JP2014055657A - Planetary roller mechanism - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a planetary roller mechanism which reduces backlash without bringing about an increase of a working cost of the planetary roller mechanism.SOLUTION: A fitting hole 45 to which a pinion shaft 25 is fit according to clearance fitting is formed on a carrier member 44, and a bottom surface 45a of the fitting hole 45 abuts on the pinion shaft 25 fitted to the fitting hole 45 from one side in the axial line direction. An abutting surface 48 which abuts on the pinion shaft 25 fitted to the fitting hole 45 from the other side in the axial direction is formed opposite to the bottom surface 45a of the fitting hole 45 and the axial line direction on a carrier member 46. While the pinion shaft 25 fitted to the fitting hole 45 is held between the bottom surface 45a of the fitting hole 45 and the abutting surface 48 with respect to the axial line direction, the carrier member 44 and the carrier member 46 are fastened by a bolt 51.

Description

  The present invention relates to a planetary roller mechanism in which a planetary roller is sandwiched between a sun roller and a ring roller.

  The related art of this type of planetary roller mechanism is disclosed in Patent Document 1 below. As shown in Patent Document 1, the planetary roller mechanism is formed by incorporating a sun roller, a planetary roller, and a ring roller into an outer shell member called a carrier through a planetary shaft inserted into the planetary roller.

JP 2005-207472 A

  In the planetary roller mechanism, the components of the sun roller, planetary roller, and ring roller have high processing accuracy so that the planetary shaft can be placed in the correct position with respect to the carrier so that the carrier can be incorporated via the planetary shaft. Not only is it required, but also high assembly accuracy is required in the assembly work. However, this requires high production costs for the planetary roller mechanism.

  Therefore, as an improvement plan, if the clearance of the planetary shaft can be adjusted by providing a gap in the planetary shaft insertion hole of the planetary roller, the processing accuracy of the sun roller, planetary roller, and ring roller parts will be slightly lowered. Even if the assembly work is slightly less accurate, it can be assembled. As a result, the manufacturing cost can be reduced.

  However, as a result, a gap remains between the planetary roller and the planetary shaft even after the planetary roller mechanism is completed, and this gap becomes a backlash when the rotation direction is reversed. For a planetary roller mechanism whose rotational direction is reversed, backlash directly becomes a value error of its own operating angle, so that high operating accuracy is difficult to be obtained. As a result, the manufacturing cost can be reduced, but the operation accuracy is lowered.

  In view of the above circumstances, the present invention provides a planetary roller mechanism capable of suppressing backlash after completion while realizing a manufacturing cost reduction (a reduction in processing accuracy and a reduction in assembly work accuracy) comparable to the above-described improvement plan. With the goal.

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

  A planetary roller mechanism according to the present invention includes a ring roller, a sun roller disposed inside the ring roller, a planetary roller sandwiched between the sun roller and the ring roller, and a planetary shaft that rotatably supports the planetary roller. A planetary roller mechanism including a carrier coupled to the planetary shaft, the carrier having a fitting hole into which the planetary shaft is fitted with a clearance fit, and an axis of the planetary shaft fitted into the fitting hole. A first carrier member formed with a first abutting surface that abuts from one side in the direction, and a second abutting surface that abuts from the other side in the axial direction with respect to the planetary shaft fitted in the fitting hole. A planetary shaft that is formed opposite to the first contact surface with respect to the direction and that is fastened to the first carrier member, and that is fitted in the fitting hole. A state sandwiched between the contact surface and the second contact surface, and summarized in that the first carrier member and the second carrier member is fastened.

  In one aspect of the present invention, the first abutment surface abuts against one end surface of the planetary shaft in the axial direction from one side in the axial direction, and the second abutment surface is in the axial direction of the planetary shaft. It is preferable to abut against the other end face on the other side in the axial direction.

  In one aspect of the present invention, the planetary shaft has a flange portion, the first contact surface is in contact with the flange portion of the planetary shaft from one side in the axial direction, and the second contact surface is the planetary shaft. The first carrier member is in contact with the flange portion from the other side in the axial direction, and the flange portion of the planetary shaft is sandwiched between the first contact surface and the second contact surface with respect to the axial direction. It is preferable that the second carrier member is fastened.

  In one aspect of the present invention, rotation of one of the ring roller and the carrier is constrained, and the sun roller is formed with a first centering hole along a central axis thereof and connected to the other of the ring roller and the carrier or to the same. It is preferable that the rotating element is formed with a second centering hole along its central axis.

  According to the present invention, during the assembling of the planetary roller mechanism, the position of the planetary shaft inserted into the insertion hole of the planetary roller can be adjusted by the amount of clearance fitting with respect to the fitting hole of the carrier. This gap fitting position adjustment margin is the same as the position adjustment margin in the gap provided in the insertion hole of the planetary roller in the improvement proposal presented in the problem. In addition, the processing accuracy of the planetary roller and ring roller parts can be made slightly lower, and the assembly work can be made slightly less accurate.

  In the present invention, when the planetary roller mechanism is completely assembled, the planetary shaft is sandwiched by the carrier, so that it cannot move with respect to the carrier. At this time, there is no gap between the ring roller, the sun roller, the planetary roller, and the planetary shaft, so that backlash caused by this gap can be suppressed, and the operation accuracy required for the planetary roller mechanism can be realized.

It is a figure which shows schematic structure of the traction drive mechanism provided with the planetary roller mechanism which concerns on embodiment of this invention. It is a figure which shows schematic structure of the traction drive mechanism provided with the planetary roller mechanism which concerns on embodiment of this invention. It is a figure which shows schematic structure of the traction drive mechanism provided with the planetary roller mechanism which concerns on embodiment of this invention. It is a figure which shows schematic structure of the planetary roller mechanism which concerns on embodiment of this invention. It is a figure which shows schematic structure of the planetary roller mechanism which concerns on embodiment of this invention. It is a figure which shows schematic structure of the planetary roller mechanism which concerns on embodiment of this invention. It is a figure which shows schematic structure of the planetary roller mechanism which concerns on embodiment of this invention. It is a figure which shows schematic structure of the planetary roller mechanism which concerns on embodiment of this invention. It is a figure explaining the assembly process of the planetary roller mechanism which concerns on embodiment of this invention. It is a figure explaining the assembly process of the planetary roller mechanism which concerns on embodiment of this invention. It is a figure explaining the assembly process of the planetary roller mechanism which concerns on embodiment of this invention. It is a figure explaining the assembly process of the planetary roller mechanism which concerns on embodiment of this invention. It is a figure explaining the assembly process of the planetary roller mechanism which concerns on embodiment of this invention. It is a figure explaining the assembly process of the planetary roller mechanism which concerns on embodiment of this invention. It is a figure explaining the assembly process of the planetary roller mechanism which concerns on embodiment of this invention. It is a figure explaining the assembly process of the planetary roller mechanism which concerns on embodiment of this invention. It is a figure which shows the other schematic structure of the planetary roller mechanism which concerns on embodiment of this invention.

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

  1 to 3 are diagrams showing a schematic configuration of a traction drive mechanism 10 including a planetary roller mechanism according to an embodiment of the present invention, and FIG. 1 is orthogonal to the central axis direction (axial direction) of the planetary roller mechanisms 12 and 52. FIG. 2 shows a cross-sectional view taken along the line AA in FIG. 1, and FIG. 3 shows a cross-sectional view taken along the line BB in FIG. The traction drive mechanism 10 according to the present embodiment includes two planetary roller mechanisms 12 and 52 connected in series to each other.

  The planetary roller mechanism (first planetary roller mechanism) 12 includes a ring roller (first ring roller) 22, a sun roller (first sun roller) 21 disposed on the inner side (radially inside) of the ring roller 22, and a ring roller 22. A plurality of pinion rollers (first planetary rollers) 23 that are arranged at intervals along the circumferential direction of the sun rollers 21 and the ring rollers 22 and are sandwiched in contact with each other (clamping holding). And a plurality of pinion shafts (first planetary shafts) 25 that are inserted into the insertion holes of the pinion rollers 23 and rotatably support the pinion rollers 23, and are coupled to the pinion shafts 25. And a carrier (first carrier) 24. Since the plurality of pinion shafts 25 are arranged at equal intervals (or substantially at equal intervals) with respect to the circumferential direction of the ring roller 22, the plurality of pinion rollers 23 are arranged at equal intervals with respect to the circumferential direction of the ring roller 22 ( (Alternatively, they are arranged at approximately equal intervals) The central axes (axis lines) of the sun roller 21, the ring roller 22, and the carrier 24 are coincident with each other. The rotation center axis (axis) when the pinion roller 23 rotates is parallel to the center axis of the ring roller 22.

  The planetary roller mechanism (second planetary roller mechanism) 52 is arranged on the inner side (radially inner side) of the ring roller 62 and the ring roller 62 (second ring roller) arranged opposite to the ring roller 22 in the axial direction. The sun roller (second sun roller) 61 and the ring roller 62 are arranged at intervals along the circumferential direction of the ring roller 62, and each is in contact with and sandwiched between the sun roller 61 and the ring roller 62 (holding pressure) ) Pinion rollers (second planetary rollers) 63 and a plurality of pinion shafts (the same number as the pinion rollers 63) inserted into the insertion holes of the respective pinion rollers 63 and rotatably supporting the respective pinion rollers 63 2 planetary shafts) 65 and a carrier (second carrier) 64 coupled to each pinion shaft 65. The plurality of pinion shafts 65 are arranged at equal intervals (or substantially at equal intervals) with respect to the circumferential direction of the ring roller 62, so that the plurality of pinion rollers 63 are equally spaced with respect to the circumferential direction of the ring roller 62 ( (Alternatively, they are arranged at approximately equal intervals) The central axes (axis lines) of the sun roller 61, the ring roller 62, and the carrier 64 coincide with each other, and further coincide with the central axes (axis lines) of the sun roller 21, the ring roller 22, and the carrier 24. The rotation center axis (axis line) when the pinion roller 63 rotates is parallel to the center axis of the ring roller 62. 1 to 3, the sun roller 61 of the planetary roller mechanism 52 is mechanically connected to the carrier 24 of the planetary roller mechanism 12, so that the planetary roller mechanism 12 and the planetary roller mechanism 52 are mechanically connected in series. It is connected. The ring rollers 22 and 62 are fixed to a casing (a fixed member whose rotation is fixed).

  The traction drive mechanism 10 according to the present embodiment can be used as a speed change mechanism. In the example shown in FIGS. 1 to 3, since the ring rollers 22 and 62 are fixed to the casing and the rotation of the ring rollers 22 and 62 is restricted, the sun roller 21 of the planetary roller mechanism 12 and the carrier 64 of the planetary roller mechanism 52 The power can be shifted between and transmitted. At that time, in the planetary roller mechanism 12, power is shifted and transmitted between the sun roller 21 and the carrier 24, and in the planetary roller mechanism 52, power is shifted and transmitted between the sun roller 61 and the carrier 64. . When power is transmitted from the sun roller 21 to the carrier 64, the planetary roller mechanism 12 transmits the power decelerated from the sun roller 21 to the carrier 24, and the planetary roller mechanism 52 transmits the power from the sun roller 61 coupled to the carrier 24 to the carrier 64. When the power is decelerated and transmitted to the traction drive mechanism 10, the traction drive mechanism 10 functions as a speed reducing mechanism that decelerates the power input to the sun roller 21 of the planetary roller mechanism 12 and outputs it from the carrier 64 of the planetary roller mechanism 52. However, the traction drive mechanism 10 can function as a speed increasing mechanism that speeds up the power input to the carrier 64 of the planetary roller mechanism 52 and outputs it from the sun roller 21 of the planetary roller mechanism 12.

  In the planetary roller mechanism 12, as shown in FIGS. 1 and 4, each pinion shaft 25 includes a rotation support portion 25a that rotatably supports the pinion roller 23, and one side in the axial direction of the rotation support portion 25a (FIGS. 1 and 4). 4 and a flange portion 25b projecting over the entire circumference from the rotation support portion 25a to the outer peripheral side. As shown in FIGS. 1 and 5, the carrier 24 has a carrier member 44 provided on one end side in the axial direction with respect to each pinion shaft 25 (on the right side in FIGS. 1 and 5), and an axial direction with respect to each pinion shaft 25. A plurality of bolts including a carrier member 46 provided on the other end side (left side in FIGS. 1 and 5) and mechanically coupled to the sun roller 61, the carrier member 44 and the carrier member 46 being fastening members. 51 is fastened.

  As shown in FIGS. 5 and 6, a plurality of (the same number of pinion shafts 25) fitting holes 45 are formed in the carrier member 44, and the bottom surface 45 a of each fitting hole 45 is one end surface of each pinion shaft 25. A plurality of fitting holes 45 are arranged at the same interval as the pinion shaft 25 in the circumferential direction so as to be opposed to the end face of the flange portion 25b in the axial direction. Since the inner diameter of each fitting hole 45 is slightly larger than the outer diameter of each flange portion 25b, one end portion (flange portion 25b) of each pinion shaft 25 is fitted into each fitting hole 45 with a gap fit. The bottom surface (abutment surface) 45a of the fitting hole 45 abuts against the flange portion 25b of the pinion shaft 25 that is fitted into the pinion shaft 25 from one side in the axial direction (the right side in FIGS. 1 and 5). In the example shown in FIG. 6, each fitting hole 45 has a substantially elliptical shape, and the major axis direction of the ellipse coincides with (or substantially coincides with) the radial direction. The flange portion 25b of each pinion shaft 25 is also substantially elliptical, the major axis of the ellipse of each flange unit 25b is slightly smaller than the major axis of the ellipse of each fitting hole 45, and the minor axis of the ellipse of each flange unit 25b is each fitted. It is slightly smaller than the minor axis of the ellipse of the hole 45. In a state where the major axis direction of the ellipse of each flange portion 25b coincides with (or substantially coincides with) the radial direction, each flange portion 25b fits into each fitting hole 45 with a gap fit, and the bottom surface 45a of the fitting hole 45 However, it abuts from one side in the axial direction to the end surface (one side end surface in the axial direction of the pinion shaft 25) 25c of the flange portion 25b. The difference between the major axis of the ellipse of the fitting hole 45 and the major axis of the ellipse of the flange portion 25b is larger than the difference between the minor axis of the ellipse of the fitting hole 45 and the minor axis of the ellipse of the flange portion 25b. The gap with the joint hole 45 is larger in the radial direction than in the circumferential direction. Further, a mating surface 47 is formed on the carrier member 44 so as to face the carrier member 46 in the axial direction. The mating surface 47 is arranged with a circumferential position shifted with respect to each fitting hole 45 and each pinion roller 23, and is arranged at a circumferential position where the pinion roller 23 is not located.

  In the carrier member 46, each fitting hole is arranged such that the contact surface 48 is disposed opposite to the other end surface 25 d of each pinion shaft 25 (rotation support portion 25 a) fitted in each fitting hole 45 in the axial direction. It is formed to face the bottom surface 45a of 45 in the axial direction. The abutment surface 48 abuts against the other end surface 25d in the axial direction of each pinion shaft 25 from the other axial side (left side in FIGS. 1 and 5). Further, the carrier member 46 is formed with a plurality of mating surfaces 49 that project to one side (carrier member 44 side) in the axial direction with respect to the contact surface 48, and the mating surfaces formed on the carrier member 44. 47 is disposed opposite to the axial direction. The mating surface 49 is disposed with a circumferential position shifted with respect to the contact surface 48 and each pinion roller 23, and is disposed at a circumferential position where the pinion roller 23 is not positioned. Furthermore, a plurality of female screws 50 that are screw-engaged with bolts (male screws) 51 are formed on the carrier member 46 (a portion that protrudes to one side in the axial direction with respect to the contact surface 48). The plurality of female screws 50 are arranged at equal intervals (or substantially equal intervals) with respect to the circumferential direction, and are arranged at circumferential positions where the pinion roller 23 is not located.

  Each pinion shaft 25 (flange portion 25b) is fitted into each fitting hole 45 of the carrier member 44, the mating surface 47 of the carrier member 44 and the mating surface 49 of the carrier member 46 are aligned, and the bolt 51 is fixed to the female screw 50. And the pinion shaft 25 fitted in each fitting hole 45 between the bottom surface 45a of each fitting hole 45 of the carrier member 44 and the contact surface 48 of the carrier member 46 in the axial direction. The carrier member 44 and the carrier member 46 are fastened in the sandwiched state. As a result, each pinion shaft 25 is positioned with respect to the carrier 24, and each pinion shaft 25 is fixed to the carrier 24. At that time, the axial length of each pinion shaft 25 in a state where the mating surface 47 of the carrier member 44 and the mating surface 49 of the carrier member 46 are aligned (the bolt 51 is not screw-engaged with the female screw 50). The distance L1 between the one end surface 25c and the other end surface 25d in the axial direction is slightly longer than the distance L2 in the axial direction between the bottom surface 45a of each fitting hole 45 of the carrier member 44 and the contact surface 48 of the carrier member 46. Thus, the bottom surface 45a and the mating surface 47 of each fitting hole 45 of the carrier member 44, and the contact surface 48 and the mating surface 49 of the carrier member 46 are designed. Accordingly, when the pinion shaft 25 is fixed to the carrier 24 by fastening the carrier member 44 and the carrier member 46 with the bolts 51, the pinion shafts 25 (the rotation support portions 25a and the flange portions 25b) are axially moved. It is sandwiched between the carrier member 44 and the carrier member 46 by an interference fit. Therefore, the force which pinches each pinion shaft 25 between the carrier member 44 and the carrier member 46 can be increased, and each pinion shaft 25 can be reliably fixed to the carrier 24.

  In the planetary roller mechanism 52, as shown in FIGS. 1 and 7, each pinion shaft 65 includes a rotation support portion 65a that rotatably supports the pinion roller 63, and the other side in the axial direction of the rotation support portion 65a (FIGS. 1 and 7). 7 and a flange portion 65b projecting over the entire circumference from the rotation support portion 65a to the outer peripheral side. As shown in FIGS. 1 and 8, the carrier 64 is fastened by a plurality of bolts 91 in which the carrier member 84 and the carrier member 86 are fastening members, and the carrier member 84 and the carrier member 82 are fastened by a plurality of bolts 92 that are fastening members. Constructed by fastening.

  As shown in FIG. 8, the carrier member 84 is formed with a plurality of (as many as the pinion shafts 65) fitting holes 85, and each fitting hole 85 is on one side in the axial direction (of FIGS. 1 and 8). A small-diameter hole 85b located on the right side and a large-diameter hole 85c located on the other side in the axial direction (left side in FIGS. 1 and 8) and communicating with the small-diameter hole 85b. The plurality of fitting holes 85 are arranged at the same interval as the pinion shaft 65 in the circumferential direction so that the bottom surface 85a of each large-diameter hole 85c is opposed to the one end surface 65c of the flange portion 65b of each pinion shaft 65 in the axial direction. Has been. The inner diameter of each small diameter hole 85b is slightly larger than the outer diameter of the rotation support portion 65a of each pinion shaft 65, and the inner diameter of each large diameter hole 85c is slightly larger than the outer diameter of the flange portion 65b of each pinion shaft 65. 65 rotation support portions 65a are fitted into the respective small diameter holes 85b with gap fittings, and flange portions 65b of the respective pinion shafts 65 are fitted into the respective large diameter holes 85c with gap fittings, and the flanges are fitted into the large diameter holes 85c. The bottom surface (abutment surface) 85a of the large-diameter hole 85c abuts against one end surface 65c in the axial direction of the portion 65b from one side in the axial direction (right side in FIGS. 1 and 8). Similarly to the fitting of the pinion shaft 25 and the fitting hole 45 in the planetary roller mechanism 12, the flange portion 65b and the large diameter hole 85c are substantially elliptical, and the gap between the flange portion 65b and the large diameter hole 85c It is also possible to make the gap in the direction larger than the gap in the circumferential direction. Further, the carrier member 84 is formed with a mating surface 87 facing the carrier member 86 in the axial direction, and a mating surface 97 is formed facing the carrier member 82 in the axial direction. The mating surfaces 87 and 97 are arranged with their circumferential positions shifted from the respective fitting holes 85 and the respective pinion rollers 63, and are arranged at circumferential positions where the pinion rollers 63 are not located. Furthermore, a plurality of female screws 90 that are screw-engaged with bolts (male threads) 91 are formed on the carrier member 84 (the portion where the mating surface 87 is formed). The plurality of female screws 90 are arranged at equal intervals (or substantially equal intervals) with respect to the circumferential direction, and are arranged at circumferential positions where the pinion roller 63 is not located.

  In the carrier member 86, each large-diameter hole 85c is arranged such that the contact surface 88 is opposed to the other end surface 65d of each pinion shaft 65 (flange portion 65b) fitted in each fitting hole 85 in the axial direction. Is formed so as to face the bottom surface 85a in the axial direction. The abutment surface 88 abuts against the other end face 65d in the axial direction of the flange portion 65b from the other axial side (the left side in FIGS. 1 and 8). Further, a mating surface 89 is formed on the carrier member 86, and is disposed opposite to the mating surface 87 formed on the carrier member 84 in the axial direction. The mating surface 89 is disposed with a circumferential position shifted with respect to the contact surface 88 and each pinion roller 63, and is disposed at a circumferential position where the pinion roller 63 is not positioned.

  A contact surface 98 is formed on the carrier member 82 so as to face the one end surface 65e of the rotation support portion 65a of each pinion shaft 65 in the axial direction, and one side in the axial direction (right side in FIGS. 1 and 8). To the one end face 65e of the rotation support portion 65a. Further, a mating surface 99 is formed on the carrier member 82, and is disposed opposite to the mating surface 97 formed on the carrier member 84 in the axial direction. The mating surface 99 is disposed with a circumferential position shifted with respect to the contact surface 98 and each pinion roller 63, and is disposed at a circumferential position where the pinion roller 63 is not positioned. Further, a plurality of female screws 80 that are engaged with bolts (male threads) 92 are formed on the carrier member 82 (the portion where the mating surface 99 is formed). The plurality of female screws 80 are arranged at equal intervals (or substantially at equal intervals) with respect to the circumferential direction, and are arranged at circumferential positions where the pinion rollers 63 are not located.

  The carrier member 82 and the carrier member 84 are fastened by aligning the mating surface 99 of the carrier member 82 with the mating surface 97 of the carrier member 84 and engaging the bolt 92 with the female screw 80. Further, each pinion shaft 65 is fitted into each fitting hole 85 of the carrier member 84, the mating surface 87 of the carrier member 84 and the mating surface 89 of the carrier member 86 are aligned, and the bolt 91 is engaged with the female screw 90 and the screw engagement. By combining, the flange portion 65b of each pinion shaft 65 fitted in each large diameter hole 85c is between the bottom surface 85a of each large diameter hole 85c of the carrier member 84 and the contact surface 88 of the carrier member 86 in the axial direction. In this state, the carrier member 84 and the carrier member 86 are fastened. As a result, each pinion shaft 65 is positioned with respect to the carrier 64, and each pinion shaft 65 is fixed to the carrier 64. At this time, the thickness of each flange portion 65b (in a state where the mating surface 87 of the carrier member 84 and the mating surface 89 of the carrier member 86 are matched (the bolt 91 is not screw-engaged with the female screw 90)). The length in the axial direction, the distance L1 between the one end surface 65c and the other end surface 65d in the axial direction) L3 is the distance L4 in the axial direction between the bottom surface 85a of each large-diameter hole 85c of the carrier member 84 and the contact surface 88 of the carrier member 86. The bottom surface 85a and the mating surface 87 of each large-diameter hole 85c of the carrier member 84, and the contact surface 88 and the mating surface 89 of the carrier member 86 are designed so as to be slightly longer. Thus, when the carrier member 84 and the carrier member 86 are fastened by the bolt 91, when the pinion shaft 65 is fixed to the carrier 64, the flange portion 65b of each pinion shaft 65 is tightly fitted in the axial direction so that the carrier member 84 is fitted. And the carrier member 86. Therefore, it is possible to increase the force for pinching the flange portion 65b of each pinion shaft 65 between the carrier member 84 and the carrier member 86 in the axial direction, and to securely fix each pinion shaft 65 to the carrier 64.

  A centering hole 53 is formed in the sun roller 21 of the planetary roller mechanism 12 along the axial direction, and the center axis of the centering hole 53 coincides with the center axis of the sun roller 21. The sun roller 61 of the planetary roller mechanism 52 connected to the carrier 24 of the planetary roller mechanism 12 has a centering hole 54 formed along the axial direction, and the center axis of the centering hole 54 is the center of the sun roller 61. Coincides with the axis. Further, a centering hole 55 is formed in the carrier 64 (carrier member 84) of the planetary roller mechanism 52 along the axial direction, and the center axis of the centering hole 55 coincides with the center axis of the carrier 64. The sun roller 21 and the sun roller 61 are arranged opposite to each other in the axial direction so that the center axis of the centering hole 53 and the center axis of the centering hole 54 coincide, and the center axis of the centering hole 54 and the center axis of the centering hole 55 are The sun roller 61 and the carrier 64 (carrier member 84) are disposed opposite to each other in the axial direction so as to match. The inner diameters of the centering holes 53, 54, 55 are preferably set equal to each other.

  When assembling the planetary roller mechanism 12, as shown in FIG. 9, first, each pinion roller 23 is placed inside the ring roller 22, and each pinion roller 23 is radially outward using a jig (arrow in FIG. 9). Pull in the direction of Next, as shown in FIG. 10, the sun roller 21 is fitted inside each pinion roller 23. Next, as shown in FIG. 11, each pinion shaft 25 is inserted into a hole at the center of each pinion roller 23. At that time, there is no need for a gap (backlash) between the pinion bearing and the pinion shaft 25, and it is possible to press-fit a resin bearing for an interference fit. Next, as shown in FIG. 12, the centering hole 53 of the sun roller 21 and the centering hole 54 of the sun roller 61 connected to the carrier member 46 are centered with an outer diameter equal to the inner diameter of the centering holes 53, 54. With the shaft (jig) 56 inserted, the carrier member 44 and the carrier member 46 are fastened by the bolts 51, so that each pinion shaft 25 is fixed between the carrier member 44 and the carrier member 46 in the axial direction. To do. At that time, the shaft 56 inserted into the centering holes 53 and 54 centers the sun roller 21, the carrier 24, and the sun roller 61 to ensure the coaxiality. The misalignment caused by the centering by the shaft 56 is absorbed by the gap between the pinion shaft 25 (flange portion 25b) and the fitting hole 45. After the carrier member 44 and the carrier member 46 are fastened by the bolt 51, the shaft 56 is removed from the centering holes 53 and 54.

  When assembling the planetary roller mechanism 52, as shown in FIG. 13, first, each pinion roller 63 is placed inside the ring roller 62, and each pinion roller 63 is radially outward using a jig (arrows in FIG. 13). Pull in the direction of Next, as shown in FIG. 14, the carrier member 82 is inserted and the sun roller 61 is fitted inside each pinion roller 63. Next, as shown in FIG. 15, a centering shaft 56 having an outer diameter equal to the inner diameter of the centering holes 54, 55 is inserted into the centering hole 54 of the sun roller 61 and the centering hole 55 of the carrier member 84. In a state where the sun roller 61 and the carrier member 84 are centered to ensure the coaxiality, the carrier member 82 and the carrier member 84 are fastened by the bolt 92, and each pinion shaft 65 is fitted to each fitting hole 85 and each pinion roller 63. Insert into the center hole. At that time, the positional shift caused by the centering by the shaft 56 is absorbed by the gap between the pinion shaft 65 and the fitting hole 85. Therefore, there is no need for a gap (backlash) between the pinion bearing and the pinion shaft 65, and it is possible to press-fit a resin bearing for an interference fit. Next, as shown in FIG. 16, the flange member 65 b of each pinion shaft 65 is sandwiched between the carrier member 84 and the carrier member 86 in the axial direction by fastening the carrier member 84 and the carrier member 86 with bolts 91. Secure with. After the carrier member 84 and the carrier member 86 are fastened by the bolt 91, the shaft 56 is removed from the centering holes 54 and 55.

  In assembling the planetary roller mechanism 12, it is important to position the center of each pinion roller 23. In the planetary roller mechanism 12, each pinion roller 23 and the sun roller 21 are press-fitted inside the ring roller 22 for assembly, but the press-fitting allowance varies depending on the processing accuracy of each roller diameter. In order to make the position equal for all products, machining with extremely high accuracy is required, resulting in an increase in machining cost. Further, in order to assemble so that the intervals between the plurality of pinion rollers 23 are constant, processing with extremely high accuracy is required. In assembling the planetary roller mechanism 12, the input / output coaxiality between the sun roller 21 that is an input rotating element to which power is input and the carrier 24 that is an output rotating element to which power is output is also important. In particular, when the carrier 24 is connected to the sun roller 61 of the planetary roller mechanism 52, the sun roller 61 is press-fitted and restrained in the radial direction, and eccentric rotation is impossible. Is required. If ideal high-accuracy machining is possible, it is possible to position the center of each pinion roller 23 and achieve input / output coaxiality. However, in order to reduce machining costs, there is a gap between the bearings of each pinion roller 23. By providing (back) or providing a gap (back) in the input / output shaft key or the like, it becomes possible to absorb errors in the processing accuracy of each roller diameter and the assembly accuracy of the rollers. However, in that case, backlash occurs due to the gaps provided in the bearings of the pinion rollers 23 and the keys of the input / output shafts. That is, the center positioning and input / output coaxiality of each pinion roller 23 and the backlash are in a trade-off relationship. Similarly, in assembling the planetary roller mechanism 52, the center of each pinion roller 63 is positioned, and the sun roller 61 that is an input rotation element to which power is input and the carrier 64 that is an output rotation element to which power is output are input. The output coaxiality is important, and these and the backlash are in a contradictory relationship.

  On the other hand, in this embodiment, errors in processing accuracy of each roller diameter and assembly accuracy of the rollers in the planetary roller mechanism 12 are absorbed by the gaps between the pinion shafts 25 (flange portions 25b) and the fitting holes 45. Meanwhile, each pinion shaft 25 can be fixed to the carrier 24 by being sandwiched between the carrier member 44 and the carrier member 46 in the axial direction. Therefore, it is not necessary to provide a gap (backlash) between the pinion bearing and the pinion shaft 25 in order to absorb errors in processing accuracy of each roller diameter and roller assembly accuracy, and backlash caused by the pinion bearing clearance. Can be reduced. Further, when the planetary roller mechanism 12 is assembled, a centering hole 53 formed along the central axis of the sun roller 21 and a centering hole 54 formed along the central axis of the sun roller 61 connected to the carrier 24. By inserting the shaft 56 in the planetary roller mechanism 12, the sun roller 21, which is a rotating element to which power is input / output in the planetary roller mechanism 12, and the carrier 24 are centered to secure the input / output coaxiality. It can be fixed to the carrier 24. Therefore, the input / output coaxiality between the sun roller 21 and the carrier 24 can be ensured and the backlash can be reduced without increasing the processing cost of the planetary roller mechanism 12.

  Further, in the present embodiment, each pinion shaft 65 (flange portion) is absorbed while the error in the processing accuracy of each roller diameter and the roller assembly accuracy in the planetary roller mechanism 52 is absorbed by the gap between the pinion shaft 65 and the fitting hole 85. 65b) can be sandwiched between the carrier member 84 and the carrier member 86 in the axial direction and fixed to the carrier 64. Therefore, no gap (backlash) is required between the pinion bearing and the pinion shaft 65, and backlash caused by the gap of the pinion bearing can be reduced. Further, when the planetary roller mechanism 52 is assembled, the shaft 56 is inserted into the centering hole 54 formed along the center axis of the sun roller 61 and the centering hole 55 formed along the center axis of the carrier 64. As a result, the sun roller 61, which is a rotating element to which power is input / output in the planetary roller mechanism 52, and the carrier 64 are centered to secure input / output coaxiality, and each pinion shaft 65 is fixed to the carrier 64. Can do. Therefore, the input / output coaxiality between the sun roller 61 and the carrier 64 can be ensured and the backlash can be reduced without increasing the processing cost of the planetary roller mechanism 52. Thus, in this embodiment, since the position of the movable part called the pinion shafts (planetary shafts) 25 and 65 can be adjusted, it is possible to achieve two effects of ease of assembly and reduction of backlash. Even if a technique capable of adjusting the position of a non-movable part is known, it is not easy to derive the effect of the present embodiment therefrom.

  In the present embodiment, for example, as shown in FIG. 17, in the planetary roller mechanism 12, bolt holes 57 are formed along the axial direction in the carrier member 44, the pinion shaft 25 (rotation support portion 25 a and flange portion 25 b), and the carrier member 46. It is also possible to fasten the carrier member 44 and the carrier member 46 through the bolt 51 in the bolt through hole 57. The inner diameter of the bolt through hole 57 is set slightly larger than the outer diameter of the bolt 51, and the gap between the bolt 51 and the bolt through hole 57 is set larger than the gap between the pinion shaft 25 (flange portion 25 b) and the fitting hole 45. . According to the configuration example shown in FIG. 17, the pinion shaft 25 can be reliably sandwiched between the carrier member 44 and the carrier member 46 in the axial direction. Similarly, in the planetary roller mechanism 52, bolt through holes are formed in the carrier member 82, the pinion shaft 65 (the rotation support portion 65 a and the flange portion 65 b), and the carrier member 86 along the axial direction. It is also possible to fasten the carrier members 82, 84, 86 through bolts.

  In the above embodiment, the case where the sun roller 61 of the planetary roller mechanism 52 is connected to the carrier 24 of the planetary roller mechanism 12 and the rotation of the ring rollers 22 and 62 is restrained has been described. However, in the present embodiment, the carrier 24 and the ring roller 62 are fixed to the casing to restrain the rotation, and the ring roller 22 and the sun roller 61 are mechanically connected, so that power is transmitted between the sun roller 21 and the carrier 64. It is also possible to transmit at a reduced speed (for example, to reduce the power transmitted from the sun roller 21 to the carrier 64). In this case, the planetary roller mechanism 12 transmits power between the sun roller 21 and the ring roller 22 with a speed change, and the planetary roller mechanism 52 transmits power between the sun roller 61 and the carrier 64 with a speed change. The Further, in the present embodiment, the ring roller 22 and the carrier 64 are fixed to the casing to restrain the rotation, and the carrier 24 and the sun roller 61 are mechanically connected to thereby generate power between the sun roller 21 and the ring roller 62. It is also possible to transmit at a reduced speed (for example, to transmit the power from the sun roller 21 to the ring roller 62 at a reduced speed). In that case, in the planetary roller mechanism 12, the power is shifted and transmitted between the sun roller 21 and the carrier 24, and in the planetary roller mechanism 52, the power is shifted and transmitted between the sun roller 61 and the ring roller 62. The centering hole 55 is formed along the central axis of a rotating element mechanically connected to the ring roller 62. Further, in the present embodiment, the carriers 24 and 64 are fixed to the casing to restrain the rotation, and the ring roller 22 and the sun roller 61 are mechanically connected to shift the power between the sun roller 21 and the ring roller 62. It is also possible to transmit the power (for example, the power is decelerated and transmitted from the sun roller 21 to the ring roller 62). In that case, the planetary roller mechanism 12 transmits the power by shifting between the sun roller 21 and the ring roller 22, and the planetary roller mechanism 52 transmits the power by shifting between the sun roller 61 and the ring roller 62. The centering hole 55 is formed along the central axis of the rotating element mechanically connected to the ring roller 62. In the present embodiment, the planetary roller mechanism 52 may be omitted, and the planetary roller mechanism 52 may be omitted, and the planetary roller mechanism 12 may be omitted, or the planetary roller mechanism 12 may be omitted. It is also possible to configure only the mechanism 52.

  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.

  10 Traction drive mechanism, 12, 52 Planetary roller mechanism, 21, 61 Sun roller, 22, 62 Ring roller, 23, 63 Pinion roller, 24, 64 Carrier, 25, 65 Pinion shaft, 25a, 65a Rotation support part, 25b, 65b Flange, 44, 46, 82, 84, 86 Carrier member, 45 85 fitting hole, 45a, 85a bottom surface, 47, 49, 87, 89, 97, 99 mating surface, 48, 88, 98 contact surface, 50 , 80, 90 Female thread, 51, 91, 92 bolt, 53, 54, 55 Centering hole, 57 Bolt through hole, 85b Small diameter hole, 85c Large diameter hole.

Claims (4)

A ring roller,
A sun roller located inside the ring roller;
A planetary roller sandwiched between a sun roller and a ring roller;
A planetary shaft that rotatably supports the planetary roller;
A carrier coupled with a planetary shaft;
A planetary roller mechanism comprising:
Career
A first carrier member formed with a fitting hole into which the planetary shaft is fitted with a gap fit, and a first abutting surface that comes into contact with the planetary shaft fitted into the fitting hole from one side in the axial direction;
A second contact surface that contacts the planetary shaft fitted in the fitting hole from the other side in the axial direction is formed to face the first contact surface in the axial direction, and is fastened to the first carrier member. A second carrier member;
Including
The first carrier member and the second carrier member are fastened in a state where the planetary shaft fitted in the fitting hole is sandwiched between the first contact surface and the second contact surface in the axial direction. Planetary roller mechanism. The planetary roller mechanism according to claim 1,
The first abutting surface abuts from one side in the axial direction against one end surface of the planetary shaft in the axial direction,
The second contact surface is a planetary roller mechanism that contacts the other end surface of the planetary shaft in the axial direction from the other side in the axial direction. The planetary roller mechanism according to claim 1,
The planetary shaft has a flange part,
The first contact surface contacts the flange portion of the planetary shaft from one side in the axial direction,
The second contact surface contacts the flange portion of the planetary shaft from the other side in the axial direction,
A planetary roller mechanism in which the first carrier member and the second carrier member are fastened in a state where the flange portion of the planetary shaft is sandwiched between the first contact surface and the second contact surface in the axial direction. The planetary roller mechanism according to any one of claims 1 to 3,
The rotation of one of the ring roller and the carrier is restricted,
A first centering hole is formed in the sun roller along its central axis,
A planetary roller mechanism in which a second centering hole is formed along the central axis of the other one of the ring roller and the carrier, or the rotating element connected thereto.

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