JP2010276130A - Traction drive mechanism - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To restrain the occurrence of force for inclining a roller, while restraining the occurrence of unbalance in pressing force acting on a contact part of the rollers. <P>SOLUTION: A torque cam mechanism 25 is arranged only in a ring roller 22-1 among two ring rollers 22-1 and 22-2 for changing the pressing force acting on the contact parts 27, 28-1 and 28-2 in response to transmission torque, and the movement to the other side in the axial direction is restricted by a support member 18 on the ring roller 22-2. While allowing relative displacement in the axial direction of the ring roller 22-1 to the ring roller 22-2 by engagement of mutual splines 88 and 90 respectively arranged in the ring rollers 22-1 and 22-2, relative displacement in the peripheral direction of the ring roller 22-1 to the ring roller 22-2 is restricted. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to a traction drive mechanism capable of transmitting torque by a traction force acting on a contact portion between rollers.

  In the traction drive mechanism, it is possible to transmit torque by the shear force (tangential traction force) of the oil film generated by the pressing force (normal force) acting on the contact part of the rollers through the oil film. It is. In such a traction drive mechanism, it is necessary to apply a pressing force (normal force) necessary for torque transmission to each contact portion so that excessive slip (gross slip) does not occur in each contact portion. Further, the normal force necessary for efficiently transmitting torque varies depending on the torque acting on the roller. Therefore, a traction drive mechanism has been proposed that can change the normal force applied to the contact portion in accordance with the torque of the roller (for example, Patent Documents 1 and 2 below).

  In the planetary roller mechanism of Patent Document 1, inclined surfaces that are in point contact with each other are formed on the outer peripheral surface of the two sun rollers and the outer peripheral surface of the pinion roller (planet roller), and the inclined surfaces of the two sun rollers and the pinion roller are inclined. Two torque cams are provided for applying the thrust in the axial direction to the two sun rollers so that a pressing force is applied to each contact portion with the surface. By changing the thrust that each torque cam acts on each sun roller according to the torque that acts on each sun roller, the pressing force that acts on each contact portion between the inclined surface of the two sun rollers and the inclined surface of the pinion roller is changed. I am letting.

  In the planetary roller mechanism of Patent Document 2, tapered surfaces (conical surfaces) that contact each other are formed on the inner peripheral surface of two ring rollers and the outer peripheral surface of the pinion roller, respectively, and the tapered surface of one ring roller and the pinion roller A torque cam is provided to apply a thrust force to one ring roller in one axial direction so that a pressing force is applied to the contact portion with the tapered surface. As for the other ring roller, movement to one side in the axial direction and movement in the rotational direction are restricted, and when one ring roller moves to one side in the axial direction by the thrust of the torque cam, the taper of one ring roller is reduced. The pressing force acts not only on the contact portion between the surface and the taper surface of the pinion roller but also on the contact portion between the taper surface of the other ring roller and the taper surface of the pinion roller. The pressing force applied to each contact portion between the tapered surface of the two ring rollers and the tapered surface of the pinion roller by changing the thrust applied to the one ring roller in accordance with the torque applied to the one ring roller by the torque cam. Is changing.

Japanese Patent Publication No.53-8862 Japanese Patent Laid-Open No. 51-137063

  In Patent Document 1, two torque cams are provided for each sun roller in order to change the pressing force applied to each contact portion between the inclined surface of the two sun rollers and the inclined surface of the pinion roller according to the transmission torque. However, if there is a machining error in the two torque cams, the axial thrust acting on the two sun rollers will be different from each other even if the torque acting on the two sun rollers is equal, and the pressure on the pinion roller will be different between the two sun rollers. An imbalance occurs.

  In Patent Document 2, in order to change the pressing force applied to each contact portion between the tapered surface of the two ring rollers and the tapered surface of the pinion roller according to the transmission torque, a torque cam is provided on one ring roller, The ring roller is restrained from moving in one axial direction and moving in the rotational direction. However, when a pressing force is applied to each contact portion by the thrust force of the torque cam, a phase difference occurs between the two ring rollers due to the movement of one ring roller provided with the torque cam in the rotational direction. A tilting force is generated.

  In the present invention, when the pressing force applied to the contact portion between the rollers is changed according to the torque of the roller, the pressing force of the contact portion is prevented from being unbalanced and the force to tilt the roller is suppressed. The purpose is to do.

  The traction drive mechanism according to the present invention employs the following means in order to achieve the above-described object.

  A traction drive mechanism according to the present invention is a traction drive mechanism including a planetary roller mechanism in which a pinion roller is sandwiched between a sun roller and a ring roller, and the ring roller has an inner diameter from one side to the other side in the axial direction thereof. A first ring roller whose first ring-side inclined surface gradually increases on the inner peripheral surface, and a second ring-side inclined surface whose inner diameter gradually decreases from one side to the other side in the axial direction. A second ring roller formed on the surface, and an outer diameter of the pinion roller is gradually increased from one side to the other side in the axial direction to contact the first ring-side inclined surface. A first pinion-side inclined surface, and a second pinion-side inclined surface that is in contact with the second ring-side inclined surface, the outer diameter gradually decreases from one side to the other side in the axial direction, A pressing mechanism for applying a thrust to the other side in the axial direction on the first ring roller so as to apply a pressing force to a contact portion between the first ring side inclined surface and the first pinion side inclined surface; A restraining member for restraining displacement to the other side in the axial direction, and a circumferential direction of the first ring roller relative to the second ring roller while allowing relative displacement in the axial direction of the first ring roller relative to the second ring roller And an engagement mechanism for restraining the relative displacement of the first and second embodiments.

  In one aspect of the present invention, the engagement mechanism includes a relative displacement in the axial direction of the first ring roller with respect to the second ring roller by engagement between splines provided on the first ring roller and the second ring roller, respectively. It is preferable that the relative displacement in the circumferential direction of the first ring roller with respect to the second ring roller is restricted while allowing

  The traction drive mechanism according to the present invention is a traction drive mechanism including a planetary roller mechanism in which a pinion roller is sandwiched between a sun roller and a ring roller, and the ring roller extends from one side in the axial direction to the other side. And a first ring roller having an inner peripheral surface with a first ring-side inclined surface whose inner diameter gradually increases, and is connected to the first ring roller via a connecting member, from one side to the other side in the axial direction. A second ring roller having an inner circumferential surface formed with a second ring-side inclined surface with a gradually decreasing inner diameter, and the outer diameter of the pinion roller has an outer diameter from one side to the other side in the axial direction. The first pinion-side inclined surface that gradually increases and contacts the first ring-side inclined surface and the outer diameter gradually decreases from one side to the other side in the axial direction, and the second ring-side inclined surface A second pinion-side inclined surface that is in contact with the surface, and the other of the first ring roller in the axial direction is applied to the first ring roller so as to exert a pressing force on the contact portion between the first ring-side inclined surface and the first pinion-side inclined surface. A pressing mechanism for applying a thrust to the side, and a restraining member for restraining the displacement of the second ring roller to the other side in the axial direction, and the axis of the first ring roller with respect to the second ring roller An elastically deformable portion that is elastically deformed to allow relative displacement in the direction is provided in any one of the connecting member, the connecting portion between the first ring roller and the connecting member, and the connecting portion between the second ring roller and the connecting member. It is a summary.

  In one aspect of the present invention, as the elastic deformation portion, the low rigidity portion whose rigidity against bending deformation in the radial direction is lower than the rigidity against bending deformation of the first ring roller in the axial direction is the connecting member, the first ring. It is preferable to be provided at any one of a connecting portion between the roller and the connecting member and a connecting portion between the second ring roller and the connecting member.

  In one aspect of the present invention, the pressing mechanism is a plurality of pressing members arranged at intervals from each other along the circumferential direction of the first ring roller, each of which presses the first ring roller at the circumferential position. It is preferable that a plurality of pressing members that press toward the other side in the axial direction are provided at different locations, and the elastic deformation portion is disposed at a circumferential position different from each pressing member.

  The traction drive mechanism according to the present invention is a traction drive mechanism including a planetary roller mechanism in which a pinion roller is sandwiched between a sun roller and a ring roller. The sun roller extends from one side to the other side in the axial direction. A first sun roller having a first sun-side inclined surface with a gradually decreasing outer diameter formed on the outer peripheral surface, and a second sun-side inclined surface with an outer diameter gradually increasing from one side to the other side in the axial direction A second sun roller formed on the surface, the outer diameter of the pinion roller is gradually increased from one side to the other side in the axial direction to contact the first sun side inclined surface. A pinion-side inclined surface and a second pinion-side inclined surface that gradually decreases in outer diameter from one side to the other side in the axial direction and contacts the second sun-side inclined surface are formed. A pressing mechanism that applies a thrust force to the first sun roller to the other side in the axial direction so as to apply a pressing force to a contact portion between the inclined surface and the first pinion side inclined surface; and the other side of the second sun roller in the axial direction. A restraining member for restraining the displacement of the first sun roller relative to the second sun roller, and a member for restraining the relative displacement in the circumferential direction of the first sun roller relative to the second sun roller while allowing the relative displacement in the axial direction of the first sun roller relative to the second sun roller. And having a combination mechanism.

  The traction drive mechanism according to the present invention is a traction drive mechanism including a planetary roller mechanism in which a pinion roller is sandwiched between a sun roller and a ring roller. The sun roller extends from one side to the other side in the axial direction. A first sun roller having a first sun-side inclined surface that gradually decreases in outer diameter is connected to the first sun roller via a connecting member, and the outer diameter is increased from one side to the other side in the axial direction. A second sun roller having a gradually increasing second sun-side inclined surface formed on the outer peripheral surface, and the outer diameter of the pinion roller gradually increases from one side to the other in the axial direction. The first pinion-side inclined surface that contacts the first sun-side inclined surface, and the outer diameter of the first pinion-side inclined surface that gradually decreases from one side to the other side in the axial direction and contacts the second sun-side inclined surface A pinion side inclined surface is formed, and a thrust to the other side in the axial direction is applied to the first sun roller so as to apply a pressing force to a contact portion between the first sun side inclined surface and the first pinion side inclined surface. A pressing mechanism and a restraining member for restraining the displacement of the second sun roller to the other side in the axial direction, and elastically deforming to allow relative displacement of the first sun roller relative to the second sun roller in the axial direction The gist of the invention is that the elastically deforming portion is provided in any one of the connecting member, the connecting portion between the first sun roller and the connecting member, and the connecting portion between the second sun roller and the connecting member.

  Further, the traction drive mechanism according to the present invention is configured so that the first and second traction forces act on the contact portion between the first and second rolling surfaces of the first and second rollers and the third rolling surface of the third roller. A traction drive mechanism capable of transmitting torque between a second roller and a third roller, wherein the first rolling surface of the first roller has an outer diameter from one side to the other side in the axial direction. Is formed on the second rolling surface of the second roller, a second inclined surface having an outer diameter gradually increasing from one side to the other in the axial direction, On the third rolling surface of the third roller, the outer diameter gradually increases from one side in the axial direction to the other side, and a third inclined surface in contact with the first inclined surface and from one side in the axial direction The outer diameter gradually decreases toward the other side, and the second contact with the second inclined surface A pressing mechanism configured to apply a thrust force to the first roller in the other axial direction so as to apply a pressing force to a contact portion between the first inclined surface and the third inclined surface. A restraining member for restraining the displacement of the roller to the other side in the axial direction, and a relative displacement in the axial direction of the first roller relative to the second roller, while allowing the first roller to move in the circumferential direction of the first roller. And an engagement mechanism for restraining relative displacement.

  Further, the traction drive mechanism according to the present invention is configured so that the first and second traction forces act on the contact portion between the first and second rolling surfaces of the first and second rollers and the third rolling surface of the third roller. A traction drive mechanism capable of transmitting torque between a second roller and a third roller, wherein the first rolling surface of the first roller has an outer diameter from one side to the other side in the axial direction. Is formed on the second rolling surface of the second roller, a second inclined surface having an outer diameter gradually increasing from one side to the other in the axial direction, On the third rolling surface of the third roller, the outer diameter gradually increases from one side in the axial direction to the other side, and a third inclined surface in contact with the first inclined surface and from one side in the axial direction The outer diameter gradually decreases toward the other side, and the second contact with the second inclined surface A pressing mechanism configured to apply a thrust force to the first roller in the other axial direction so as to apply a pressing force to a contact portion between the first inclined surface and the third inclined surface. A constraining member for constraining displacement of the roller to the other side in the axial direction, the first roller and the second roller being connected via a connecting member, and the axis of the first roller relative to the second roller An elastically deformable portion that is elastically deformed to allow relative displacement in the direction is provided in any of the connecting member, the connecting portion between the first roller and the connecting member, and the connecting portion between the second roller and the connecting member. Is the gist.

  According to the present invention, when the pressing force applied to the contact portion between the rollers is changed according to the torque of the roller, it is possible to suppress the occurrence of imbalance in the pressing force of the contact portion, and to tilt the roller. Generation of force can be suppressed.

  DESCRIPTION OF EMBODIMENTS Hereinafter, embodiments for carrying out the present invention (hereinafter referred to as embodiments) will be described with reference to the drawings.

“Embodiment 1”
1 and 2 are diagrams showing a schematic configuration of the traction drive mechanism according to the first embodiment of the present invention. FIG. 1 is viewed from a direction orthogonal to the central axis (axis line) of the ring rollers 22-1 and 22-2. FIG. 2 shows a part of the AA sectional view of FIG. However, the structure of the remaining part which is not illustrated in FIG. 2 is the same structure as the illustrated part. The traction drive mechanism according to the present embodiment is arranged on a pair of ring rollers (first and second ring rollers) 22-1 and 22-2 and on the inner side (radially inside) of the ring rollers 22-1 and 22-2. The sun rollers 21 are arranged along the circumferential direction of the ring rollers 22-1 and 22-2, and the sun rollers 21 and the ring rollers 22-1 and 22-2 are in contact with and sandwiched between the sun rollers 21 and the ring rollers 22-1 and 22-2. The planetary roller mechanism 12 includes a plurality of pinion rollers (planetary rollers) 23 that are pressure-held and a carrier 24 that rotatably supports each pinion roller 23. 1 and 2 show an example in which the planetary roller mechanism 12 is a single pinion type planetary roller mechanism. The sun rollers 21, the ring rollers 22-1 and 22-2, and the carrier 24 have the same center axis (axis), and the rotation center axis (axis) when the pinion roller 23 rotates is the ring rollers 22-1 and 22. -2 is parallel to the central axis.

  The pair of ring rollers 22-1 and 22-2 are opposed to each other with a space therebetween in the axial direction, and the ring roller 22-1 is on one side in the axial direction with respect to the ring roller 22-2 (see FIG. 1). On the left). The inner peripheral surface (rolling surface) of the ring roller 22-1 has a ring-side tapered surface (inclined surface) 32− whose inner diameter gradually increases from one side in the axial direction to the other side (left side to right side in FIG. 1). 1 is formed on the inner peripheral surface (rolling surface) of the ring roller 22-2, the ring side taper surface (inclined surface) 32-2 whose inner diameter gradually decreases from one side to the other side in the axial direction. Is formed. The taper angle (inclination angle with respect to the axial direction) of the ring-side taper surface 32-1 is equal to the taper angle of the ring-side taper surface 32-2, and the maximum inner diameter of the ring-side taper surface 32-1 and The minimum value is equal to the maximum value and the minimum value of the inner diameter of the ring-side tapered surface 32-2.

  The plurality of pinion rollers 23 are arranged at intervals with respect to the circumferential direction of the ring rollers 22-1 and 22-2. An outer peripheral surface (rolling surface) of each pinion roller 23 includes a pinion side tapered surface (inclined surface) 33-1 whose outer diameter gradually increases from one side in the axial direction to the other side, and one side in the axial direction. A pinion side taper surface (inclined surface) 33-2 whose outer diameter gradually decreases toward the other side is formed at an interval in the axial direction, and the pinion side taper surface 33-1 is formed as a pinion side taper surface 33. It is arrange | positioned at the one side of the axial direction rather than -2. The taper angle (inclination angle with respect to the axial direction) of the pinion side taper surface 33-1 is equal to the taper angle of the pinion side taper surface 33-2, and the maximum value of the outer diameter of the pinion side taper surface 33-1. The minimum value is equal to the maximum value and the minimum value of the outer diameter of the pinion-side tapered surface 33-2. The magnitude of the taper angle of the pinion side taper surfaces 33-1 and 33-2 is equal to or slightly different from the magnitude of the taper angle of the ring side taper surfaces 32-1 and 32-2. Each pinion side taper surface 33-1 is in contact with the ring side taper surface 32-1, and each pinion side taper surface 33-2 is in contact with the ring side taper surface 32-2. Further, a pinion-side cylindrical surface 33-3 is formed on the outer peripheral surface of each pinion roller 23. The pinion-side cylindrical surface 33-3 is disposed between the pinion-side tapered surfaces 33-1 and 33-2 with respect to the axial direction, and is formed to project outward in the radial direction from the pinion-side tapered surfaces 33-1 and 33-2. Yes. Each pinion-side cylindrical surface 33-3 is in contact with the outer peripheral surface (sun-side cylindrical surface) 31 of the sun roller 21.

  The torque cam mechanism 25 is arranged along the circumferential direction of the ring roller 22-1 and a ring-shaped cam disk 29 disposed opposite to the ring roller 22-1 with respect to the axial direction. A plurality of cylindrical cam rollers 30 sandwiched between the roller 22-1 and the cam disk 29. The cam disk 29 is disposed on one side in the axial direction with respect to the ring roller 22-1 and is fixed to the support member 18. As shown in FIGS. 1 and 3, a plurality of cam surfaces 22-1b are formed on the side surface of the ring roller 22-1 on one side in the axial direction so as to be spaced from each other in the circumferential direction. -1b faces the cam disk 29. Here, FIG. 3 shows the ring roller 22-1 and the cam disk 29 developed in the circumferential direction. A plurality of cam surfaces 29b are formed on the side surface of the cam disk 29 on the other side in the axial direction so as to be spaced from each other in the circumferential direction, and each cam surface 29b faces each cam surface 22-1b. ing. Each cam roller 30 is interposed between the cam surfaces 22-1b and 29b in the axial direction. That is, the plurality of cam rollers 30 are arranged at intervals with respect to the circumferential direction of the ring roller 22-1.

  In the present embodiment, the ring roller 22-1 is provided with a spline 88 formed with teeth and grooves extending along (or substantially along) the axial direction, and the ring roller 22-2 has an axial direction ( Splines 90 are provided with teeth and grooves extending (almost along). The teeth of the spline 88 are fitted into the groove of the spline 90 (the teeth of the spline 90 are fitted into the groove of the spline 88), so that the ring roller 22-2 is rotated in the circumferential direction (rotating direction). The relative movement is restricted, and the ring roller 22-1 and the ring roller 22-2 are engaged with each other in the circumferential direction (rotation direction). However, since the teeth of the spline 88 can move in the axial direction along the groove of the spline 90 (the teeth of the spline 90 can move in the axial direction along the groove of the spline 88), the ring roller 22-2 ( The axial movement of the ring roller 22-1 (ring-side tapered surface 32-1) relative to the ring-side tapered surface 32-2) is allowed. In this manner, the engagement between the splines 88 and 90 allows the relative displacement in the axial direction of the ring roller 22-1 with respect to the ring roller 22-2 and allows the ring roller 22-2 to move around the ring roller 22-2. The relative displacement in the direction is constrained. The ring roller 22-2 is supported by the support member 18 via the bearing 19. The movement (displacement) of the ring roller 22-2 toward the other side (the right side in FIG. 1) in the axial direction is restricted by the support member 18, but the circumferential direction (rotation direction) of the ring roller 22-2 with respect to the support member 18 Relative movement (displacement) is allowed by the bearing 19.

  When a phase difference occurs between the ring roller 22-1 and the cam disk 29 due to the torque acting on the ring roller 22-1, each cam roller 30 rolls along the cam surfaces 22-1b and 29b, so that the cam The relative rotation of the ring roller 22-1 with respect to the disk 29 is suppressed. At the same time, each cam roller 30 presses the ring roller 22-1 toward the other side in the axial direction at a different position in the circumferential direction, so that thrust on the other side in the axial direction acts on the ring roller 22-1. . When the ring roller 22-1 moves to the other side in the axial direction (the direction in which the outer diameter of the pinion side taper surface 33-1 increases) by this thrust, the ring side taper surface 32-1 of the ring roller 22-1 moves to each pinion. A force is generated to press the pinion side tapered surface 33-1 of the roller 23 inward in the radial direction. Accordingly, the pressing force is applied to the contact portion 28-1 between each pinion-side tapered surface 33-1 and the ring-side tapered surface 32-1, and the contact portion 27 between each pinion-side cylindrical surface 33-3 and the sun-side cylindrical surface 31. Act. Further, when each pinion roller 23 moves to the other side in the axial direction, the ring roller 22-2 receives a reaction force from the support member 18 toward the one side in the axial direction, so that the ring-side taper of the ring roller 22-2. The surface 32-2 generates a force that presses the pinion-side tapered surface 33-2 of each pinion roller 23 radially inward. Accordingly, the pressing force is applied to the contact portion 28-2 between each pinion-side tapered surface 33-2 and the ring-side tapered surface 32-2, and the contact portion 27 between each pinion-side cylindrical surface 33-3 and the sun-side cylindrical surface 31. Act. In this way, each cam roller 30 presses the ring roller 22-1 to the other side in the axial direction at different positions in the circumferential direction, thereby causing the ring rollers 22-1 and 22-2 to move toward the pinion roller 23 side. A pressing force can be applied. The thrust to the other side in the axial direction acting on the ring roller 22-1 changes according to the phase difference between the ring roller 22-1 and the cam disk 29 (torque acting on the ring roller 22-1). The phase difference (torque acting on the ring roller 22-1) increases with an increase. Therefore, the pressing force (normal force) acting on each contact portion 27, 28-1, and 28-2 changes according to the torque acting on the ring roller 22-1, and the torque acting on the ring roller 22-1. Increase with respect to increase. The ring roller 22-1 is supported while being movable in the axial direction, and each pinion roller 23 is supported by the carrier 24 in a state where slight radial movement and axial movement are allowed.

  In the traction drive mechanism (planetary roller mechanism 12), torque is generated by the shear force (tangential traction force) of the oil film generated by the pressing force (normal force) acting on the contact portion between the rollers via the oil film. It is possible to communicate. When torque transmission is performed, it is necessary to apply a pressing force (normal force) necessary for torque transmission to each contact portion so that excessive slip (gross slip) does not occur at each contact portion. In the present embodiment, it is possible to apply a pressing force (normal force) to the contact portions 27, 28-1, and 28-2 by the torque cam mechanism 25 that applies a thrust in the axial direction to the ring roller 22-1. It becomes. Thereby, a traction force can be generated at the contact portions 27, 28-1, and 28-2, and between the sun roller 21 and each pinion roller 23, and between each pinion roller 23 and the ring rollers 22-1 and 22-2. Torque can be transmitted between the two. Further, the torque cam mechanism 25 can change the normal force applied to the contact portions 27, 28-1, and 28-2 in accordance with the transmission torque.

  The planetary roller mechanism 12 can be used as a speed change mechanism. For example, by fixing the cam disk 29 and the ring roller 22-2 to the casing (using the support member 18 as a casing) and restraining the rotation of the ring rollers 22-1 and 22-2, the sun roller 21 and the carrier 24 The power can be shifted between the two and transmitted. In this case, when power is transmitted from the sun roller 21 to the carrier 24, the planetary roller mechanism 12 functions as a speed reducing mechanism that decelerates and transmits power from the sun roller 21 to the carrier 24. On the other hand, when the power is transmitted from the carrier 24 to the sun roller 21, the planetary roller mechanism 12 functions as a speed increasing mechanism that accelerates and transmits the power from the carrier 24 to the sun roller 21. Further, by fixing the carrier 24 to the casing and restraining its rotation, the power can be changed and transmitted between the sun roller 21 and the ring rollers 22-1 and 22-2. Further, by fixing the sun roller 21 to the casing and restraining its rotation, the power can be changed and transmitted between the carrier 24 and the ring rollers 22-1 and 22-2. When restraining the rotation of the carrier 24 or the sun roller 21, the support member 18 rotates. As described above, the planetary roller mechanism 12 transmits torque between the remaining two by restricting rotation of any one of the carrier 24, the sun roller 21, and the ring rollers 22-1 and 22-2. Is possible.

  Here, as shown in FIG. 4, in order to change the pressing force applied to the contact portions 27, 28-1, and 28-2 according to the transmission torque, the two torque cam mechanisms 25 are connected to the ring rollers 22-1. , 22-2 is considered. In the configuration shown in FIG. 4, when there are machining errors in the two torque cam mechanisms 25, such as when machining errors occur in the cam surfaces 22-1b, 22-2b, and 29b, the two ring rollers 22-1. , 22-2 even if the torque acting on the two ring rollers 22-1 and 22-2 is equal, the axial thrust acting on the two ring rollers 22-1 and 22-2 is unbalanced and the pushing force acting on the contact portions 28-1 and 28-2 is generated. An imbalance occurs in the pressure.

  Further, as shown in FIG. 5, in order to change the pressing force applied to each contact portion 27, 28-1, 28-2 according to the transmission torque, a torque cam mechanism 25 is provided on the ring roller 22-1, and the ring Consider a case where the roller 22-2 is fixed to the support member 18 to restrain the movement in the axial direction and the rotational direction. In the configuration shown in FIG. 5, when the pressing force is applied to the contact portions 27, 28-1, and 28-2 according to the torque that the torque cam mechanism 25 acts on the ring roller 22-1, the ring roller 22-1 is applied. Moves in the rotational direction with respect to the cam disk 29 (support member 18), so that a phase difference occurs between the two ring rollers 22-1 and 22-2, and thus a force for tilting the pinion roller 23 is generated.

  On the other hand, in this embodiment, in order to change the pressing force applied to each contact part 27, 28-1, 28-2 according to the transmission torque, of the two ring rollers 22-1, 22-2. The torque cam mechanism 25 is provided only on the ring roller 22-1 and the movement of the ring roller 22-2 to the other side in the axial direction is restricted by the support member 18 without providing the torque cam mechanism 25. As a result, it is possible to suppress the occurrence of unbalance in the axial thrust acting on the two ring rollers 22-1 and 22-2 due to the processing error of the torque cam mechanism 25, and the contact portions 28-1, It is possible to suppress the occurrence of imbalance in the pressing force acting on 28-2. Further, the ring rollers 22-1 and 22-2 are engaged with each other by the splines 88 and 90, and the ring roller 22-2 is allowed to be displaced relative to the ring roller 22-2 in the axial direction while the ring roller 22-2 is engaged. The circumferential displacement of the ring roller 22-1 with respect to 22-2 is restrained. As a result, when the torque cam mechanism 25 applies a pressing force to the contact portions 27, 28-1, 28-2 according to the torque acting on the ring roller 22-1, the two ring rollers 22-1, 22-22. 2 can be prevented from generating a phase difference, and the force to tilt the pinion roller 23 can be suppressed. As a result, the movement of the pinion roller 23 can be stabilized.

  In this embodiment, when the support member 18 restrains the movement of the ring roller 22-2 in the other axial direction while allowing the relative displacement of the ring roller 22-2 in the circumferential direction with respect to the support member 18, It is also possible to support the roller 22-2 on the support member 18 without using the bearing 19. In this case, a film made of a low friction material can be formed on the contact surface of the ring roller 22-2 with the support member 18 or the contact surface of the support member 18 with the ring roller 22-2. As the low friction material here, for example, DLC (diamond-like carbon), ceramic such as chromium nitride, PTFE, or the like can be used.

“Embodiment 2”
FIG. 6 is a diagram showing a schematic configuration of the traction drive mechanism according to the second embodiment of the present invention, and shows a cross-sectional view seen from a direction orthogonal to the central axes (axis lines) of the sun rollers 21-1 and 21-2. In the following description of the second embodiment, the same or corresponding components as those in the first embodiment are denoted by the same reference numerals, and the components that are not described are the same as those in the first embodiment.

  In the present embodiment, a pair of sun rollers (first and second sun rollers) 21-1 and 21-2 are disposed opposite to each other in the axial direction thereof, and the sun roller 21-1 is more than the sun roller 21-2. It arrange | positions at the one side (left side of FIG. 6) of an axial direction. On the outer peripheral surface (rolling surface) of the sun roller 21-1, a sun-side tapered surface (inclined surface) 31-1 whose outer diameter gradually decreases from one side in the axial direction to the other side (left side to right side in FIG. 6). A sun-side tapered surface (inclined surface) 31-2 whose outer diameter gradually increases from one side in the axial direction to the other side is formed on the outer peripheral surface (rolling surface) of the sun roller 21-2. Has been. The taper angle (inclination angle with respect to the axial direction) of the sun-side taper surface 31-1 is equal to the taper angle of the sun-side taper surface 31-2 and the maximum outer diameter of the sun-side taper surface 31-1. The minimum value is equal to the maximum value and the minimum value of the outer diameter of the sun-side tapered surface 31-2. And the magnitude | size of the taper angle of the sun side taper surfaces 31-1 and 31-2 is equal to or slightly different from the magnitude | size of the taper angle of the pinion side taper surfaces 33-1 and 33-2. The sun side taper surface 31-1 is in contact with each pinion side taper surface 33-1, and the sun side taper surface 31-2 is in contact with each pinion side taper surface 33-2. Each pinion-side cylindrical surface 33-3 is in contact with the inner peripheral surface (ring-side cylindrical surface) 32 of the ring roller 22.

  In the torque cam mechanism 25, the cam disk 29 fixed to the support member 18 is disposed opposite to the sun roller 21-1 with respect to the axial direction, and is disposed on one side in the axial direction with respect to the sun roller 21-1. A plurality of cam surfaces 21-1 b are formed on the side surface of the sun roller 21-1 with respect to one side in the axial direction at intervals with respect to the circumferential direction, and each cam surface 21-1 b corresponds to each cam surface of the cam disk 29. 29b, respectively. Each cam roller 30 is disposed between the cam surfaces 21-1b and 29-1b in the axial direction. That is, the plurality of cam rollers 30 are arranged at intervals with respect to the circumferential direction of the sun roller 21-1.

  In the present embodiment, the sun roller 21-1 is provided with a spline 88 formed with teeth and grooves extending along (or substantially along) the axial direction, and the teeth and grooves extending along (or substantially along) the axial direction. Is formed on the sun roller 21-2. The teeth of the spline 88 are fitted into the grooves of the spline 90 (the teeth of the spline 90 are fitted into the grooves of the spline 88), whereby the relative displacement in the circumferential direction (rotation direction) of the sun roller 21-1 with respect to the sun roller 21-2. The sun roller 21-1 and the sun roller 21-2 are engaged with each other in the circumferential direction (rotation direction). However, since the teeth of the spline 88 can move in the axial direction along the groove of the spline 90 (the teeth of the spline 90 can move in the axial direction along the groove of the spline 88), the sun roller 21-2 (Sun Relative displacement in the axial direction of the sun roller 21-1 (sun-side taper surface 31-1) with respect to the side taper surface 31-2) is allowed. The sun roller 21-2 is supported by the support member 18 via the bearing 19. The displacement of the sun roller 21-2 toward the other side in the axial direction (the right side in FIG. 6) is restrained by the support member 18, but the circumferential displacement (rotation direction) of the sun roller 21-2 relative to the support member 18 is a bearing. 19 is permitted.

  When a phase difference is generated between the sun roller 21-1 and the cam disk 29 due to the torque acting on the sun roller 21-1, each cam roller 30 rolls along the cam surfaces 21-1b and 29b, thereby causing the cam disk 29 to rotate. The relative rotation of the sun roller 21-1 is suppressed. At the same time, each cam roller 30 presses the sun roller 21-1 to the other side in the axial direction at different positions in the circumferential direction, so that thrust to the other side in the axial direction acts on the sun roller 21-1. When the sun roller 21-1 moves to the other side in the axial direction by this thrust force, the sun-side tapered surface 31-1 of the sun roller 21-1 presses the pinion-side tapered surface 33-1 of each pinion roller 23 outward in the radial direction. appear. Accordingly, the pressing force is applied to the contact portion 27-1 between the sun-side tapered surface 31-1 and each pinion-side tapered surface 33-1 and the contact portion 28 between each pinion-side cylindrical surface 33-3 and the ring-side cylindrical surface 32. Act. Further, when each pinion roller 23 moves to the other side in the axial direction, the sun roller 21-2 receives a reaction force from the support member 18 toward the one side in the axial direction, whereby the sun-side tapered surface 31 of the sun roller 21-2. -2 generates a force that presses the pinion-side tapered surface 33-2 of each pinion roller 23 radially outward. Thus, the pressing force is applied to the contact portion 27-2 between the sun-side tapered surface 31-2 and each pinion-side tapered surface 33-2 and the contact portion 28 between each pinion-side cylindrical surface 33-3 and the ring-side cylindrical surface 32. Act. The pressing force acting on each contact portion 27-1, 27-2, 28 changes according to the torque acting on the sun roller 21-1, and increases with an increase in the torque acting on the sun roller 21-1. The sun roller 21-1 is supported so as to be movable in the axial direction.

  Also in the present embodiment described above, it is possible to suppress the occurrence of unbalance in the axial thrust acting on the two sun rollers 21-1 and 21-2 and to act on the contact portions 27-1 and 27-2. It is possible to suppress the occurrence of imbalance in the pressing force. Furthermore, it is possible to suppress the occurrence of a phase difference between the two sun rollers 21-1 and 21-2, and it is possible to suppress the generation of a force that tilts the pinion roller 23.

  In the present embodiment, similarly to the first embodiment, the sun roller 21-2 can be supported by the support member 18 without using the bearing 19. In this case, a film made of a low friction material can be formed on the contact surface of the sun roller 21-2 with the support member 18 or the contact surface of the support member 18 with the sun roller 21-2.

“Embodiment 3”
FIG. 7 is a diagram showing a schematic configuration of a traction drive mechanism according to Embodiment 3 of the present invention, and shows a cross-sectional view seen from a direction orthogonal to the central axes (axis lines) of the rollers 121-1 and 121-2. In the following description of the third embodiment, the same or corresponding components as those of the first and second embodiments are denoted by the same reference numerals, and the description of the components that are not described is the same as that of the first and second embodiments.

  The pair of rollers (first and second rollers) 121-1 and 121-2 are opposed to each other with a space therebetween in the axial direction, and the roller 121-1 is one of the axial direction than the roller 121-2. It is arranged on the side (left side in FIG. 7). On the outer peripheral surface (rolling surface) of the roller 121-1, a tapered surface (inclined surface) 131-1 is formed 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. 7). The outer surface (rolling surface) of the roller 121-2 is formed with a tapered surface (inclined surface) 131-2 whose outer diameter gradually increases from one side to the other side in the axial direction. The taper angles (inclination angles with respect to the axial direction) of the taper surfaces 131-1 and 131-2 are equal to each other, and the maximum value and the minimum value of the outer diameters of the taper surfaces 131-1 and 131-2 are equal to each other.

  The rotation center axis (axis) of the roller (third roller) 123 is parallel to the rotation center axes (axis) of the rollers 121-1 and 121-2. The outer peripheral surface (rolling surface) of the roller 123 has a tapered surface (inclined surface) 133-1 whose outer diameter gradually increases from one side in the axial direction to the other side, and an outer surface from one side in the axial direction to the other side. A taper surface (inclined surface) 133-2 having a gradually decreasing diameter is formed at an interval in the axial direction, and the taper surface 133-1 is located on one side in the axial direction with respect to the taper surface 133-2. Has been placed. The taper angles 133-1 and 133-2 have the same taper angle (inclination angle with respect to the axial direction), and the taper surfaces 133-1 and 133-2 have the same maximum and minimum outer diameters. The taper angle of the taper surfaces 133-1 and 133-2 is equal to or slightly different from the taper angle of the taper surfaces 131-1 and 131-2. The tapered surface 133-1 is in contact with the tapered surface 131-1, and the tapered surface 133-2 is in contact with the tapered surface 131-2.

  In the torque cam mechanism 25, the cam disk 29 fixed to the support member 18 is disposed to face the roller 121-1 with a space in the axial direction, and is disposed on one side in the axial direction with respect to the roller 121-1. A plurality of cam surfaces 121-1b are formed at intervals in the circumferential direction on the side surface of the roller 121-1 with respect to one side in the axial direction, and each cam surface 121-1b is each cam surface of the cam disk 29. 29b, respectively. Each cam roller 30 is disposed so as to be sandwiched between these cam surfaces 121-1b and 29-1b in the axial direction.

  In this embodiment, a spline 88 formed with teeth and grooves extending along (or substantially along) the axial direction is provided on the roller 121-1, and the teeth and grooves extending along (or substantially along) the axial direction. Is formed on the roller 121-2. When the teeth of the spline 88 are fitted in the grooves of the spline 90, relative displacement in the circumferential direction (rotation direction) of the roller 121-1 with respect to the roller 121-2 is restrained, and the roller 121-1 and the roller 121-2 are rotated. Engage with respect to direction (direction of rotation). However, since the teeth of the spline 88 can move in the axial direction along the groove of the spline 90, the axial direction of the roller 121-1 (tapered surface 131-1) with respect to the roller 121-2 (tapered surface 131-2). Relative displacement is allowed. The roller 121-2 is supported by the support member 18 via the bearing 19. Although the displacement of the roller 121-2 toward the other side in the axial direction is restricted by the support member 18, the relative displacement in the circumferential direction (rotation direction) of the roller 121-2 with respect to the support member 18 is allowed by the bearing 19. .

  When a phase difference is generated between the roller 121-1 and the cam disk 29 due to the torque acting on the roller 121-1, each cam roller 30 rolls along the cam surfaces 121-1b and 29b, so that the cam disk 29 The relative rotation of the roller 121-1 relative to the roller 121-1 is suppressed, and a thrust to the other side in the axial direction acts on the roller 121-1. When the roller 121-1 moves to the other side in the axial direction by this thrust, a force is generated in which the tapered surface 131-1 of the roller 121-1 presses the tapered surface 133-1 of the roller 123. As a result, a pressing force acts on the contact portion 127-1 between the tapered surface 131-1 and the tapered surface 133-1. Further, when the roller 123 moves to the other side in the axial direction, the roller 121-2 receives a reaction force from the support member 18 to the one side in the axial direction, so that the tapered surface 131-2 of the roller 121-2 becomes a roller. The force which presses the taper surface 133-2 of 123 generate | occur | produces. As a result, a pressing force acts on the contact portion 127-2 between the tapered surface 131-2 and the tapered surface 133-2. The pressing force acting on each of the contact portions 127-1 and 127-2 changes according to the torque acting on the roller 121-1 and increases with the increase in the torque acting on the roller 121-1. The rollers 121-1 and 123 are supported so as to be movable in the axial direction.

  Also in the present embodiment described above, it is possible to suppress the occurrence of unbalance in the axial thrust acting on the two rollers 121-1 and 121-2, and to act on the contact portions 127-1 and 127-2. It is possible to suppress the occurrence of imbalance in the pressing force. Furthermore, it is possible to suppress the occurrence of a phase difference between the two rollers 121-1 and 121-2, and it is possible to suppress the generation of a force that tilts the roller 123.

  Also in this embodiment, as in the first and second embodiments, the roller 121-2 can be supported by the support member 18 without the bearing 19 interposed therebetween. In that case, the film | membrane by a low friction material can also be formed in the contact surface with the support member 18 in the roller 121-2, or the contact surface with the roller 121-2 in the support member 18.

“Embodiment 4”
FIG. 8 is a diagram showing a schematic configuration of a traction drive mechanism according to Embodiment 4 of the present invention, and shows a cross-sectional view seen from a direction orthogonal to the central axis (axis line) of the ring roller 22. In the following description of the fourth embodiment, the same or corresponding components as those of the first to third embodiments are denoted by the same reference numerals, and the description thereof is omitted as in the first to third embodiments.

  In the present embodiment, the ring roller 22 includes a first ring roller 22-1 having a ring-side tapered surface 32-1 formed on the inner peripheral surface, and a first ring roller 22-1 having a ring-side tapered surface 32-2 formed on the inner peripheral surface. The first ring roller 22-1 and the second ring roller 22-2 are connected via an annular connecting member 20. The ring rollers 22-1 and 22-2 (ring-side tapered surfaces 32-1 and 32-2) are radially inward from the connecting member 20 toward the pinion roller 23 (pinion-side tapered surfaces 33-1 and 33-2). Protruding to A groove is formed in the outer circumferential portion of the ring roller 22 (connecting member 20) along the circumferential direction, so that the coupling member 20 is provided with a low-rigidity portion (elastically deforming portion) 26 along the circumferential direction. Yes. The thickness in the radial direction of the low-rigidity portion 26 is thinner than the thickness in the axial direction of the ring rollers 22-1 and 22-2, and the rigidity (bending stiffness) against bending deformation in the radial direction of the low-rigidity portion 26 is It is lower than the rigidity against bending deformation in the axial direction of the rollers 22-1 and 22-2 (bending rigidity). Therefore, the low-rigidity part 26 is more easily elastically deformed (bending deformation) than the ring rollers 22-1 and 22-2. As shown in FIG. 9, the low-rigidity portion 26 is elastically deformed by bending in the radial direction, so that the ring roller 22-1 (ring-side tapered surface 32-2) with respect to the ring roller 22-2 (ring-side tapered surface 32-2) is obtained. A relative displacement in the axial direction of 1) is allowed. However, even if the low-rigidity portion 26 is elastically deformed, the relative displacement in the circumferential direction (rotation direction) of the ring roller 22-1 with respect to the ring roller 22-2 is constrained by the connecting member 20. In FIG. 9, in order to make it easy to understand the deformation of the ring rollers 22-1 and 22-2 and the connecting member 20, the displacement amount of the ring rollers 22-1 and 22-2 and the connecting member 20 is increased. It is shown.

  Each cam roller 30 presses the ring roller 22-1 toward the other side in the axial direction at different locations in the circumferential direction in accordance with the torque acting on the ring roller 22-1 so that the ring roller 22-1 has an axis line. When a thrust to the other side of the direction is applied, a pressing force is applied to the contact portions 27 and 28-1. At that time, due to elastic deformation of the low-rigidity portion 26, movement of the ring roller 22-1 to the other side in the axial direction with respect to the ring roller 22-2 is allowed. Further, the ring roller 22-2 receives a reaction force from the support member 18 toward the one side in the axial direction, so that a pressing force acts on the contact portions 27 and 28-2. The pressing force acting on each contact portion 27, 28-1, 28-2 increases with an increase in torque acting on the ring roller 22-1.

  Even in the present embodiment described above, it is possible to suppress the occurrence of unbalance in the axial thrust acting on the two ring rollers 22-1 and 22-2 due to the processing error of the torque cam mechanism 25, and the contact It is possible to suppress the occurrence of imbalance in the pressing force acting on the portions 28-1 and 28-2. Furthermore, when the torque cam mechanism 25 applies a pressing force to the contact portions 27, 28-1, and 28-2 in accordance with the torque acting on the ring roller 22-1, the low-rigidity portion (elastic deformation portion) 26 By restraining the relative displacement in the circumferential direction of the ring roller 22-1 with respect to the ring roller 22-2 while allowing the relative displacement in the axial direction of the ring roller 22-1 with respect to the ring roller 22-2 by elastic deformation, It is possible to suppress the occurrence of a phase difference between the ring rollers 22-1 and 22-2, and it is possible to suppress the generation of a force that tilts the pinion roller 23.

  When the ring roller 22-1 is easily bent and elastically deformed by the thrust force of the torque cam mechanism 25, the ring roller 22-1 is displaced in the axial direction depending on whether it is pressed by the cam roller 30 or not. The amount will be different. Since the pressing force acting on the contact portion 28-1 changes according to the amount of displacement of the ring roller 22-1 in the axial direction, the amount of displacement of the ring roller 22-1 in the axial direction differs depending on the circumferential position. As the ring rollers 22-1 and 22-2 and the carrier 24 rotate relative to each other, the pressing force acting on the contact portion 28-1 varies. This variation in pressing force causes variation in transmission torque and vibration of the ring roller 22-1.

  On the other hand, in the present embodiment, the bending rigidity in the radial direction of the low-rigidity portion 26 is made lower than the bending rigidity in the axial direction of the ring roller 22-1 so as to be lower than that of the ring roller 22-1. It is possible to suppress the amount of displacement of the ring roller 22-1 in the axial direction from varying according to the position in the circumferential direction by easily elastically deforming. Therefore, it is possible to suppress fluctuations in the pressing force acting on the contact portion 28-1 due to the relative rotation between the ring rollers 22-1 and 22-2 and the carrier 24.

  In this embodiment, for example, as shown in FIG. 10, a low-rigidity portion (elastic deformation portion) whose rigidity against bending deformation in the radial direction is lower than rigidity against bending deformation in the axial direction of the ring rollers 22-1 and 22-2. 26) can also be provided along the circumferential direction at the connecting portion between the ring roller 22-1 and the connecting member 20, or at the connecting portion between the ring roller 22-2 and the connecting member 20. For example, as shown in FIG. 11, the thickness of the entire connecting member 20 in the radial direction is made thinner than the thickness of the ring rollers 22-1 and 22-2 in the axial direction so that the entire connecting member 20 is a low-rigidity portion ( Elastic deformation part) 26. 10 and 11, when the torque cam mechanism 25 applies a pressing force to each contact portion 27, 28-1, 28-2 according to the torque acting on the ring roller 22-1, the ring roller While the relative displacement in the circumferential direction of the ring roller 22-1 with respect to 22-2 is constrained, the relative displacement in the axial direction of the ring roller 22-1 with respect to the ring roller 22-2 can be allowed by elastic deformation of the low rigidity portion 26. it can. Furthermore, it can suppress that the displacement amount to the axial direction of the ring roller 22-1 changes according to a circumferential direction position.

  In the present embodiment, for example, as shown in FIGS. 12 and 13, by forming a plurality of grooves on the side surface of the ring roller 22 in the circumferential direction, the axis of the ring roller 22-1 with respect to the ring roller 22-2. An elastically deformable portion (low-rigidity portion) 26 that is elastically deformed to allow relative displacement in the direction is connected to a connecting portion between the ring roller 22-1 and the connecting member 20, or a connecting portion between the ring roller 22-2 and the connecting member 20. In addition, a plurality of portions may be provided partially in the circumferential direction. Here, FIG. 13 shows the ring roller 22 and the cam disk 29 developed along the circumferential direction. The rigidity with respect to the bending deformation in the axial direction of each elastic deformation portion 26 is lower than the rigidity with respect to the bending deformation in the axial direction of the ring rollers 22-1 and 22-2. Each elastic deformation part 26 is arrange | positioned in the position which shifted | deviated from the cam surface 22-1b (cam roller 30) regarding the circumferential direction, and is arrange | positioned in the position between the cam surfaces 22-1b (between the cam rollers 30) regarding the circumferential direction. . That is, the elastic deformation portion 26 is disposed at a circumferential position different from each cam roller 30. 12 and 13, the amount of displacement in the axial direction of the portion of the ring roller 22-1 that is not pressed by the cam roller 30 can be increased by elastic deformation (bending deformation) of the elastic deformation portion 26. Therefore, it is possible to suppress the amount of displacement of the ring roller 22-1 in the axial direction from being different depending on the circumferential position.

“Embodiment 5”
FIG. 14 is a diagram showing a schematic configuration of a traction drive mechanism according to Embodiment 5 of the present invention, and shows a cross-sectional view seen from a direction orthogonal to the central axis (axis line) of the sun roller 21. In the following description of the fifth embodiment, the same or corresponding components as those in the first to fourth embodiments are denoted by the same reference numerals, and the description thereof is omitted as in the first to fourth embodiments.

  In this embodiment, the sun roller 21 includes a first sun roller 21-1 having a sun-side tapered surface 31-1 formed on the outer peripheral surface and a second sun roller 21- having a sun-side tapered surface 31-2 formed on the outer peripheral surface. 2, and the first sun roller 21-1 and the second sun roller 21-2 are connected via a cylindrical connecting member 20. The sun rollers 21-1 and 21-2 (sun-side tapered surfaces 31-1 and 31-2) are radially outward from the connecting member 20 toward the pinion roller 23 (pinion-side tapered surfaces 33-1 and 33-2). It protrudes. The thickness in the radial direction of the low-rigidity portion (elastically deforming portion) 26 provided along the circumferential direction on the connecting member 20 is thinner than the thickness in the axial direction of the sun rollers 21-1 and 21-2. The rigidity against bending deformation in the radial direction of the sun rollers 21-1, 21-2 is lower than the rigidity against bending deformation in the axial direction of the sun rollers 21-1, 21-2. When the low-rigidity portion 26 is bent and elastically deformed in the radial direction, relative displacement in the axial direction of the sun roller 21-1 (sun-side tapered surface 31-1) with respect to the sun roller 21-2 (sun-side tapered surface 31-2) is caused. Permissible. However, even if the low-rigidity portion 26 is elastically deformed, the relative displacement in the circumferential direction (rotational direction) of the sun roller 21-1 with respect to the sun roller 21-2 is constrained by the connecting member 20.

  In response to the torque acting on the sun roller 21-1, each cam roller 30 presses the sun roller 21-1 to the other side in the axial direction at a different position in the circumferential direction, thereby causing the sun roller 21-1 to have the other in the axial direction. When thrust to the side acts, a pressing force acts on the contact portions 27-1 and 28. At that time, due to the elastic deformation of the low-rigidity portion 26, movement of the sun roller 21-1 to the other side in the axial direction of the sun roller 21-2 is allowed. Further, the sun roller 21-2 receives a reaction force from the support member 18 toward the one side in the axial direction, so that a pressing force acts on the contact portions 27-2 and 28. The pressing force acting on each contact portion 27-1, 27-2, 28 increases with an increase in torque acting on the sun roller 21-1.

  Also in the present embodiment described above, it is possible to suppress the occurrence of unbalance in the axial thrust acting on the two sun rollers 21-1 and 21-2 and to act on the contact portions 27-1 and 27-2. It is possible to suppress the occurrence of imbalance in the pressing force. And it can suppress that a phase difference arises in two sun rollers 21-1, 21-2, and can suppress that the force which inclines the pinion roller 23 arises. Furthermore, by making the low-rigidity portion 26 elastically deform more easily than the sun roller 21-1, it is possible to suppress the amount of displacement of the sun roller 21-1 in the axial direction from varying according to the circumferential position. It can suppress that the pressing force which acts on the contact part 27-1 with the relative rotation of the sun rollers 21-1, 21-2 and the carrier 24 is fluctuated.

  Also in this embodiment, for example, as shown in FIG. 15, a low-rigidity portion (elastic deformation portion) 26 whose bending rigidity in the radial direction is lower than the bending rigidity in the axial direction of the sun rollers 21-1 and 21-2 is It can also be provided along the circumferential direction at the connecting portion between 21-1 and the connecting member 20 or at the connecting portion between the sun roller 21-2 and the connecting member 20. For example, as shown in FIG. 16, the thickness of the entire connecting member 20 in the radial direction is made thinner than the thickness of the sun rollers 21-1 and 21-2 in the axial direction to (Deformation part) 26 can also be used.

  Also in this embodiment, for example, as shown in FIG. 17, by forming a plurality of grooves on the side surface of the sun roller 21 in the circumferential direction, the relative displacement in the axial direction of the sun roller 21-1 with respect to the sun roller 21-2 is reduced. An elastically deformable portion (low-rigidity portion) 26 that is elastically deformed to allow is partially applied to a connecting portion between the sun roller 21-1 and the connecting member 20 or a connecting portion between the sun roller 21-2 and the connecting member 20 in the circumferential direction. A plurality of them can be provided. The rigidity of each elastic deformation portion 26 with respect to the bending deformation in the axial direction is lower than the rigidity with respect to the bending deformation of the sun rollers 21-1 and 21-2 in the axial direction. Each elastic deformation part 26 is arrange | positioned in the position which shifted | deviated from the cam surface 21-1b (cam roller 30) regarding the circumferential direction, and is arrange | positioned in the circumferential direction position different from each cam roller 30.

“Embodiment 6”
FIG. 18 is a diagram showing a schematic configuration of a traction drive mechanism according to Embodiment 6 of the present invention, and shows a cross-sectional view seen from a direction orthogonal to the central axes (axis lines) of the rollers 121-1 and 121-2. In the following description of the sixth embodiment, the same or corresponding components as those of the first to fifth embodiments are denoted by the same reference numerals, and the description thereof is omitted as in the first to fifth embodiments.

  In the present embodiment, the roller 121 includes a first roller 121-1 having a tapered surface 131-1 formed on the outer peripheral surface and a second roller 121-2 having a tapered surface 131-2 formed on the outer peripheral surface. The first roller 121-1 and the second roller 121-2 are connected via a cylindrical connecting member 20. The rollers 121-1 and 121-2 (tapered surfaces 131-1 and 131-2) protrude radially outward from the connecting member 20 toward the roller 123 (tapered surfaces 133-1 and 133-2). The thickness in the radial direction of the low-rigidity portion (elastically deformable portion) 26 provided along the circumferential direction in the connecting member 20 is thinner than the thickness in the axial direction of the rollers 121-1 and 121-2, and the low-rigidity portion 26. The rigidity against bending deformation in the radial direction is lower than the rigidity against bending deformation in the axial direction of the rollers 121-1 and 121-2. Since the low-rigidity portion 26 is bent in the radial direction and elastically deformed, relative displacement in the axial direction of the roller 121-1 (taper surface 131-2) with respect to the roller 121-2 (taper surface 131-2) is allowed. However, even if the low-rigidity portion 26 is elastically deformed, the relative displacement in the circumferential direction (rotational direction) of the roller 121-1 with respect to the roller 121-2 is constrained by the connecting member 20.

  Depending on the torque acting on the roller 121-1, each cam roller 30 presses the roller 121-1 toward the other side in the axial direction at different positions in the circumferential direction, thereby causing the roller 121-1 to move in the other axial direction. When thrust to the side acts, a pressing force acts on the contact portion 127-1. At that time, due to the elastic deformation of the low-rigidity portion 26, movement of the roller 121-1 to the other side in the axial direction relative to the roller 121-2 is allowed. Further, the roller 121-2 receives a reaction force from the support member 18 toward the one side in the axial direction, whereby a pressing force acts on the contact portion 127-2. The pressing force acting on each contact portion 127-1 and 127-2 increases with an increase in torque acting on the roller 121-1.

  Also in the present embodiment described above, it is possible to suppress the occurrence of unbalance in the axial thrust acting on the two rollers 121-1 and 121-2, and to act on the contact portions 127-1 and 127-2. It is possible to suppress the occurrence of imbalance in the pressing force. And it can suppress that a phase difference arises in two rollers 121-1, 121-2, and can suppress that the force which inclines roller 123 arises. Further, it is possible to suppress the amount of displacement of the roller 121-1 in the axial direction from being changed according to the circumferential position, and the contact portion 127-1 is moved along with the rotation of the rollers 121-1 and 121-2. It is possible to suppress fluctuations in the applied pressing force.

  Also in this embodiment, for example, as shown in FIG. 19, a low-rigidity portion (elastic deformation portion) 26 whose bending rigidity in the radial direction is lower than the bending rigidity in the axial direction of the rollers 121-1 and 121-2 is It can also be provided along the circumferential direction at the connecting portion between 121-1 and the connecting member 20, or at the connecting portion between the roller 121-2 and the connecting member 20. For example, as shown in FIG. 20, the thickness of the entire connecting member 20 in the radial direction is made thinner than the thickness of the rollers 121-1 and 121-2 in the axial direction so that the entire connecting member 20 is made of a low rigidity portion (elasticity). (Deformation part) 26 can also be used.

  Also in this embodiment, for example, as shown in FIG. 21, by forming a plurality of grooves on the side surface of the roller 121 in the circumferential direction, the relative displacement in the axial direction of the roller 121-1 with respect to the roller 121-2 is reduced. An elastically deformable portion (low-rigidity portion) 26 that elastically deforms to allow is partially applied to the connecting portion between the roller 121-1 and the connecting member 20 or the connecting portion between the roller 121-2 and the connecting member 20 in the circumferential direction. A plurality of them can be provided. The rigidity with respect to the bending deformation in the axial direction of each elastic deformation portion 26 is lower than the rigidity with respect to the bending deformation in the axial direction of the rollers 121-1 and 121-2. Each elastic deformation part 26 is arrange | positioned in the position which shifted | deviated from the cam surface 121-1b (cam roller 30) regarding the circumferential direction, and is arrange | positioned in the circumferential direction position different from each cam roller 30.

  As mentioned above, although the form for implementing this invention was demonstrated, this invention is not limited to such embodiment at all, and it can implement with a various form in the range which does not deviate from the summary of this invention. Of course.

It is a figure which shows schematic structure of the traction drive mechanism which concerns on Embodiment 1. FIG. It is a figure which shows schematic structure of the traction drive mechanism which concerns on Embodiment 1. FIG. It is a figure which shows schematic structure of the traction drive mechanism which concerns on Embodiment 1. FIG. It is a figure which shows schematic structure at the time of providing two torque cam mechanisms for every ring roller. It is a figure which shows schematic structure at the time of providing a torque cam mechanism in one ring roller, and restraining the movement of the other ring roller in the axial direction and rotation direction. It is a figure which shows schematic structure of the traction drive mechanism which concerns on Embodiment 2. FIG. It is a figure which shows schematic structure of the traction drive mechanism which concerns on Embodiment 3. FIG. It is a figure which shows schematic structure of the traction drive mechanism which concerns on Embodiment 4. FIG. It is a figure explaining a deformation | transformation of a ring roller. FIG. 10 is a diagram showing another schematic configuration of the traction drive mechanism according to the fourth embodiment. FIG. 10 is a diagram showing another schematic configuration of the traction drive mechanism according to the fourth embodiment. FIG. 10 is a diagram showing another schematic configuration of the traction drive mechanism according to the fourth embodiment. FIG. 10 is a diagram showing another schematic configuration of the traction drive mechanism according to the fourth embodiment. It is a figure which shows schematic structure of the traction drive mechanism which concerns on Embodiment 5. FIG. FIG. 10 is a diagram showing another schematic configuration of the traction drive mechanism according to the fifth embodiment. FIG. 10 is a diagram showing another schematic configuration of the traction drive mechanism according to the fifth embodiment. FIG. 10 is a diagram showing another schematic configuration of the traction drive mechanism according to the fifth embodiment. It is a figure which shows schematic structure of the traction drive mechanism which concerns on Embodiment 6. FIG. FIG. 10 is a diagram illustrating another schematic configuration of the traction drive mechanism according to the sixth embodiment. FIG. 10 is a diagram illustrating another schematic configuration of the traction drive mechanism according to the sixth embodiment. FIG. 10 is a diagram illustrating another schematic configuration of the traction drive mechanism according to the sixth embodiment.

  DESCRIPTION OF SYMBOLS 1 Planetary roller mechanism, 18 Support member, 19 Bearing, 20 Connecting member, 21, 21-1, 21-2 Sun roller, 22, 22-1, 22-2 Ring roller, 23 Pinion roller, 24 Carrier, 25 Torque cam mechanism, 26 Low rigidity portion (elastic deformation portion), 27, 27-1, 27-2, 28, 28-1, 28-2, 127-1, 127-2 Contact portion, 29 cam disc, 30 cam roller, 31-1 31-2 Sun side taper surface, 32-1, 32-2 Ring side taper surface, 33-1, 33-2 Pinion side taper surface, 88, 90 spline, 121, 121-1, 121-2, 123 roller 131-1, 131-2, 133-1, 133-2 taper surface.

Claims (9)

A traction drive mechanism comprising a planetary roller mechanism in which a pinion roller is sandwiched between a sun roller and a ring roller,
The ring roller includes a first ring roller having an inner peripheral surface formed with a first ring-side inclined surface whose inner diameter gradually increases from one side to the other side in the axial direction, and from one side to the other side in the axial direction. A second ring roller having a second ring-side inclined surface having an inner diameter that gradually decreases and formed on the inner peripheral surface,
On the outer peripheral surface of the pinion roller, an outer diameter gradually increases from one side to the other side in the axial direction, and a first pinion-side inclined surface that comes into contact with the first ring-side inclined surface, and one side in the axial direction. An outer diameter gradually decreases toward the other side, and a second pinion-side inclined surface that contacts the second ring-side inclined surface is formed,
A pressing mechanism that applies thrust to the first ring roller to the other side in the axial direction so as to apply a pressing force to the contact portion between the first ring-side inclined surface and the first pinion-side inclined surface;
A restraining member for restraining the displacement of the second ring roller to the other side in the axial direction;
An engagement mechanism for restraining the relative displacement in the circumferential direction of the first ring roller relative to the second ring roller while allowing the relative displacement in the axial direction of the first ring roller relative to the second ring roller;
A traction drive mechanism. The traction drive mechanism according to claim 1,
The engaging mechanism allows the second ring roller to be displaced relative to the second ring roller in the axial direction by allowing the splines provided on the first ring roller and the second ring roller to engage with each other. A traction drive mechanism that restrains the relative displacement of the first ring roller in the circumferential direction with respect to the ring roller. A traction drive mechanism comprising a planetary roller mechanism in which a pinion roller is sandwiched between a sun roller and a ring roller,
The ring roller includes a first ring roller having an inner circumferential surface formed with a first ring-side inclined surface whose inner diameter gradually increases from one side to the other side in the axial direction, and a first ring roller via a connecting member. A second ring roller that is connected and has a second ring-side inclined surface formed on the inner peripheral surface, the inner diameter of which gradually decreases from one side to the other side in the axial direction,
On the outer peripheral surface of the pinion roller, an outer diameter gradually increases from one side to the other side in the axial direction, and a first pinion-side inclined surface that comes into contact with the first ring-side inclined surface, and one side in the axial direction. An outer diameter gradually decreases toward the other side, and a second pinion-side inclined surface that contacts the second ring-side inclined surface is formed,
A pressing mechanism that applies thrust to the first ring roller to the other side in the axial direction so as to apply a pressing force to the contact portion between the first ring-side inclined surface and the first pinion-side inclined surface;
A restraining member for restraining the displacement of the second ring roller to the other side in the axial direction;
Have
An elastically deformable portion that is elastically deformed to allow relative displacement of the first ring roller in the axial direction relative to the second ring roller is coupled to the coupling member, the coupling portion between the first ring roller and the coupling member, and the second ring roller. A traction drive mechanism provided at one of the connecting portions with the member. The traction drive mechanism according to claim 3,
As the elastic deformation portion, a low-rigidity portion whose rigidity against bending deformation in the radial direction is lower than rigidity against bending deformation in the axial direction of the first ring roller is connected to the connecting member, the first ring roller and the connecting member. A traction drive mechanism provided in any of the portion and the connecting portion between the second ring roller and the connecting member. The traction drive mechanism according to claim 3,
The pressing mechanism is a plurality of pressing members arranged at intervals from each other along the circumferential direction of the first ring roller, each of which pushes the first ring roller in the axial direction at different positions in the circumferential direction. Having a plurality of pressing members for pressing to the other side;
The elastic deformation portion is a traction drive mechanism arranged at a circumferential position different from each pressing member. A traction drive mechanism comprising a planetary roller mechanism in which a pinion roller is sandwiched between a sun roller and a ring roller,
The sun roller has a first sun roller formed on the outer peripheral surface with a first sun-side inclined surface whose outer diameter gradually decreases from one side to the other side in the axial direction, and an outer diameter from one side to the other side in the axial direction. A second sun roller on the outer peripheral surface of which the second sun-side inclined surface is gradually increased,
On the outer peripheral surface of the pinion roller, the outer diameter gradually increases from one side to the other side in the axial direction, and a first pinion-side inclined surface that contacts the first sun-side inclined surface, and one side in the axial direction. The outer diameter gradually decreases toward the other side, and a second pinion-side inclined surface that contacts the second sun-side inclined surface is formed,
A pressing mechanism that applies a thrust to the first sun roller to the other side in the axial direction so as to apply a pressing force to the contact portion between the first sun-side inclined surface and the first pinion-side inclined surface;
A restraining member for restraining the displacement of the second sun roller to the other side in the axial direction;
An engagement mechanism for restraining the relative displacement in the circumferential direction of the first sun roller relative to the second sun roller while allowing the relative displacement in the axial direction of the first sun roller relative to the second sun roller;
A traction drive mechanism. A traction drive mechanism comprising a planetary roller mechanism in which a pinion roller is sandwiched between a sun roller and a ring roller,
The sun roller is connected to the first sun roller via a first sun roller having a first sun side inclined surface formed on the outer peripheral surface, the outer diameter of which gradually decreases from one side to the other side in the axial direction, and a connecting member, A second sun roller having a second sun-side inclined surface with an outer diameter gradually increasing from one side to the other side in the axial direction formed on the outer peripheral surface,
On the outer peripheral surface of the pinion roller, the outer diameter gradually increases from one side to the other side in the axial direction, and a first pinion-side inclined surface that contacts the first sun-side inclined surface, and one side in the axial direction. The outer diameter gradually decreases toward the other side, and a second pinion-side inclined surface that contacts the second sun-side inclined surface is formed,
A pressing mechanism that applies a thrust to the first sun roller to the other side in the axial direction so as to apply a pressing force to the contact portion between the first sun-side inclined surface and the first pinion-side inclined surface;
A restraining member for restraining the displacement of the second sun roller to the other side in the axial direction;
Have
The elastically deforming portion that elastically deforms to allow relative displacement of the first sun roller relative to the second sun roller to the axial direction includes a connecting member, a connecting portion between the first sun roller and the connecting member, and a connection between the second sun roller and the connecting member. A traction drive mechanism provided in one of the parts. Due to the traction force acting on the contact portion between the first and second rolling surfaces of the first and second rollers and the third rolling surface of the third roller, between the first and second rollers and the third roller. A traction drive mechanism capable of transmitting torque,
The first rolling surface of the first roller is formed with a first inclined surface whose outer diameter gradually decreases from one side to the other side in the axial direction,
On the second rolling surface of the second roller, a second inclined surface having an outer diameter gradually increasing from one side to the other side in the axial direction is formed,
On the third rolling surface of the third roller, the outer diameter gradually increases from one side in the axial direction to the other side, and a third inclined surface in contact with the first inclined surface and from one side in the axial direction The outer diameter gradually decreases toward the other side, and a fourth inclined surface that contacts the second inclined surface is formed,
A pressing mechanism that applies a thrust force to the first roller on the other side so as to apply a pressing force to the contact portion between the first inclined surface and the third inclined surface;
A restraining member for restraining the displacement of the second roller to the other side in the axial direction;
An engagement mechanism for restraining the relative displacement in the circumferential direction of the first roller relative to the second roller while allowing the relative displacement in the axial direction of the first roller relative to the second roller;
A traction drive mechanism. Due to the traction force acting on the contact portion between the first and second rolling surfaces of the first and second rollers and the third rolling surface of the third roller, between the first and second rollers and the third roller. A traction drive mechanism capable of transmitting torque,
The first rolling surface of the first roller is formed with a first inclined surface whose outer diameter gradually decreases from one side to the other side in the axial direction,
On the second rolling surface of the second roller, a second inclined surface having an outer diameter gradually increasing from one side to the other side in the axial direction is formed,
On the third rolling surface of the third roller, the outer diameter gradually increases from one side in the axial direction to the other side, and a third inclined surface in contact with the first inclined surface and from one side in the axial direction The outer diameter gradually decreases toward the other side, and a fourth inclined surface that contacts the second inclined surface is formed,
A pressing mechanism that applies a thrust force to the first roller on the other side so as to apply a pressing force to the contact portion between the first inclined surface and the third inclined surface;
A restraining member for restraining the displacement of the second roller to the other side in the axial direction;
Have
The first roller and the second roller are connected via a connecting member,
An elastically deformable portion that elastically deforms to allow relative displacement of the first roller relative to the second roller in the axial direction includes a connecting member, a connecting portion between the first roller and the connecting member, and a connection between the second roller and the connecting member. A traction drive mechanism provided in one of the parts.

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