JP6398429B2 - Planetary roller traction drive - Google Patents

Description

  The present invention relates to a planetary roller traction drive.

  Conventionally, as a planetary roller type traction drive, there is one described in JP-A-9-42397 (Patent Document 1). The planetary roller traction drive includes a ring roller, a sun roller, an annular planetary roller, and a planet carrier. The planetary roller is inscribed on the inner circumferential surface of the ring roller and circumscribed on the outer circumferential surface of the sun roller. Further, the planetary shaft (drive pin) of the planetary carrier is attached to the inner diameter side of the planetary roller via a planetary roller bearing.

  In this planetary roller traction drive, for example, rotational power from a sun roller is transmitted to the planetary roller, and the planetary roller revolves while rotating on the inner peripheral surface of the fixed ring roller. . And the rotational speed of the sun roller on the input side is decelerated by outputting the rotational speed of the revolution of the ring roller.

Japanese Patent Laid-Open No. 9-42397 (FIGS. 1 and 2)

  The inventor of the present application has found that the conventional planetary roller traction drive has the following problems.

  That is, in the planetary roller type traction drive, the planetary roller performs rolling transmission while being pressed between the ring roller and the sun roller. Therefore, in this rolling transmission, there is no gap and it is difficult for backlash to exist. On the other hand, there is a gap between the inner diameter of the planetary roller and the planetary shaft. Therefore, due to this gap, backlash occurs between the planetary roller and the planetary shaft, and the positioning accuracy deteriorates due to the backlash.

  Here, as a technique for solving the problem, there is a technique in which the planetary roller bearing is disposed between the planetary roller and the planetary shaft while the planetary roller bearing is in a negative gap so that the gap is eliminated. However, in this method, when assembling the planetary roller bearing with a negative gap, it is essential to manage the negative gap with high accuracy. This is because, in order to transmit torque, it is necessary to press and assemble the annular planetary roller, so the inner diameter of the planetary roller shrinks, but in consideration of variations in the amount of shrinkage, impressions are generated on the planetary roller. It is because it is necessary to set it as the negative clearance of the range which does not carry out. Therefore, there is a problem that backlash cannot be easily reduced.

  Further, as shown in FIG. 6, that is, a schematic sectional view in the radial direction of a conventional planetary roller type traction drive, the planetary roller 223 includes a ring roller 221 and a sun roller 222, and arrows A and B in FIG. A radial pressing force indicated by is applied. Therefore, as shown in FIG. 6, the planetary roller 223 is easily deformed into an ellipse having a major radius in the revolution direction. Therefore, if a perfect circle bearing (shown by one region in FIG. 6) 225 is disposed between the planetary roller 223 and the planetary shaft (drive pin) 226, a gap is easily generated in the revolution direction. It is easy for backlash to occur.

  Therefore, an object of the present invention is to provide a planetary roller traction drive capable of reducing backlash easily and efficiently.

In order to solve the above problems, the planetary roller traction drive of the present invention is
A ring roller,
A sun roller located on the radially inner side of the ring roller;
An annular planetary roller inscribed in the inner peripheral surface of the ring roller and circumscribed in the outer peripheral surface of the sun roller;
And a planetary carrier having a rod-like elastic member having a C-shaped cross section and disposed on the inner diameter side of the planetary roller.

  In addition, by arranging a rolling bearing between the planetary roller and the rod-like elastic member, the planetary roller can freely rotate with respect to the rod-like elastic member. Further, even if a frictional force exists due to the use of an appropriate lubricant or the like, the planetary roller can be received by sliding on the outer diameter surface of the rod-like elastic member without using a rolling bearing. In addition, a bush can be appropriately disposed at any position between the planetary roller and the rod-like elastic member.

  According to the present invention, since the rod-shaped elastic member having a C-shaped cross section is arranged on the inner diameter side of the planetary roller, the inner peripheral surface of the planetary roller can be directly pressed by the rod-shaped elastic member, or it is fitted inside the planetary roller. The inner peripheral surface of the inner fitting portion (the inner fitting portion can be constituted only by a rolling bearing, or can be constituted by a rolling bearing and a bush, for example) can be pressed by a rod-like elastic member, and the inner fitting can be performed by this pressing. The portion can be expanded toward the planetary roller. Therefore, the gap between the planetary roller and the rod-like elastic member can be reduced, and backlash caused by the gap can be efficiently reduced.

  Further, according to the present invention, the rod-shaped elastic member having a notch and easily deformed is disposed on the inner diameter side of the planetary roller. Can be placed on the side. Further, since the rod-like elastic member having a notch and easily deformed is arranged on the inner diameter side of the planetary roller, the rod-like elastic member is arranged on the inner diameter side of the planetary roller, and then the rod-like elastic member is arranged. The outer diameter surface of the elastic member can be deformed so as to follow the shape of the inner peripheral surface with which the rod-shaped elastic member is in contact, and the outer diameter surface of the rod-shaped elastic member is closer to the inner peripheral surface. The inner peripheral surface can be pressed by the outer diameter surface of the rod-like elastic member. Therefore, the gap can be reduced easily and efficiently. Therefore, backlash can be reduced simply and efficiently, and higher positioning accuracy can be realized easily.

In one embodiment,
A rolling bearing having an outer ring fitted on the inner peripheral surface of the planetary roller, an inner ring, and a rolling element;
The rod-like elastic member is press-fitted into the inner peripheral surface of the inner ring.

  According to the above embodiment, since the rolling bearing is disposed on the inner diameter side of the planetary roller, smooth rotation of the planetary roller with respect to the rod-like elastic member can be realized with this rolling bearing. Further, the inner ring can be efficiently expanded by the rod-shaped elastic member having a C-shaped cross section that is press-fitted into the inner diameter side of the inner ring of the rolling bearing. Therefore, the bearing clearance can be reduced by the expansion of the inner ring, and the backlash can be reduced.

In one embodiment,
A plane including the central axis of the sun roller and the central axis of the planetary roller passes through the notch of the bar-shaped elastic member having the C-shaped cross section.

  According to the above embodiment, since the notch of the rod-shaped elastic member faces the radial direction of the planetary roller traction drive, the rod-shaped elastic member can be expanded more efficiently in the revolving direction of the planetary roller. Therefore, the gap in the revolution direction caused by the elliptical deformation in the revolution direction of the planetary roller based on the pressure contact of the planetary roller can be more efficiently closed by the deformation of the rod-shaped elastic member. Therefore, backlash can be effectively reduced.

In one embodiment,
The planet carrier has a carrier body having a pin insertion hole through which one end of the rod-shaped elastic member is inserted,
A stop pin press-fitted on the inner diameter side of one end of the rod-like elastic member is provided.

  According to the said embodiment, the one end part of a rod-shaped elastic member can be expanded to the inner surface side of a pin insertion hole with the stop pin press-fit by the internal diameter side of the one end part of a rod-shaped elastic member. Therefore, a large pressure can be generated on the press-fitting surfaces of the carrier body and the rod-like elastic member, and the rod-like elastic member can be hardly detached from the carrier body.

In one embodiment,
The rod-like elastic member is a spring pin.

  According to the embodiment, since the rod-like elastic member is a spring pin, a force can be reliably and stably applied to the inner peripheral side of the planetary roller using a spring action. Therefore, backlash can be reliably and effectively reduced.

  According to the present invention, backlash can be easily reduced, and higher positioning accuracy can be easily realized.

It is sectional drawing of the axial direction of the two-stage deceleration planetary mechanism of one Embodiment of this invention. It is a schematic cross section of the 1st planetary roller type traction drive of the above-mentioned two speed reduction planetary mechanism. It is a perspective view of the drive pin which consists of a C-shaped spring pin of the said 1st planetary roller type traction drive. It is a schematic cross section of the radial direction which passes the center of the ball | bowl of the angular ball bearing in a part of said 1st planetary roller traction drive. It is sectional drawing of the axial direction of the one step reduction planetary mechanism of one Embodiment of this invention. It is a schematic cross section of the radial direction of the conventional planetary roller type traction drive.

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

  FIG. 1 is a sectional view in the axial direction of a two-stage reduction planetary mechanism according to an embodiment of the present invention.

  As shown in FIG. 1, the two-stage reduction planetary mechanism includes a housing 1, a first planetary roller traction drive 2, a second planetary roller traction drive 3, and an output shaft 4. It has a cylindrical cup-shaped housing body 10 and a disk-shaped lid portion 11.

  The first planetary roller type traction drive (hereinafter simply referred to as a first drive) 2 includes a first ring roller 21, a first intermediate shaft 22 as a sun roller, a plurality of first planetary rollers 23, and a first It has a planet carrier 24 and a first double row ball bearing 25 as an example of a rolling bearing.

  The first ring roller 21 is fitted into the cylindrical inner peripheral surface of the housing body 10. The first intermediate shaft 22 extends on the central axis of the housing body 10. The first intermediate shaft 22 is connected to the motor shaft 41 of the stepping motor 40 by a shaft coupling 90, and rotates when the stepping motor 40 is driven to rotate.

  The plurality of first planetary rollers 23 are located at intervals in the circumferential direction of the first ring roller 21. The first planetary roller 23 is inscribed in a state where surface pressure exists on the cylindrical inner peripheral surface of the first ring roller 21, and circumscribed in a state where surface pressure exists on the cylindrical outer peripheral surface of the first intermediate shaft 22. Yes.

  As shown in FIG. 1, the width of the cylindrical inner peripheral surface of the first ring roller 21 is shorter than the axial length of the first planetary roller 23, and the entire surface of the cylindrical inner peripheral surface of the first ring roller 21 is While contacting the outer peripheral surface of the first planetary roller 23, the entire outer peripheral surface of the first planetary roller 23 is not in contact with the cylindrical inner peripheral surface of the first ring roller 21. In this way, the first ring roller 21 and the first planetary roller 23 are in contact with each other with sufficient surface pressure.

  The first planet carrier 24 has a disk-shaped first carrier body 28 and a first drive pin 29, and the first carrier body 28 has a first pin insertion hole 30. One end of the first drive pin 29 in the axial direction is fitted into and fixed to the first pin insertion hole 30 of the first carrier body 28. The first carrier body 28 is fixed to the other axial end portion of the outer peripheral surface of the second intermediate shaft 52 described below.

  The first double row ball bearing 25 is disposed between the inner peripheral surface of the first planetary roller 23 and the outer diameter surface of the first drive pin 29. The first double row ball bearing 25 supports the first planetary roller 23 so as to be rotatable (rotatable) with respect to the first drive pin 29.

  The second planetary roller traction drive (hereinafter simply referred to as a second drive) 3 includes a second ring roller 51, a second intermediate shaft 52 as a sun roller, a plurality of second planetary rollers 53, and a second It has a planet carrier 54 and a second double row ball bearing 55 as an example of a rolling bearing.

  The second ring roller 51 is fitted on the cylindrical inner peripheral surface of the housing body 10. The second ring roller 51 is disposed adjacent to the first ring roller 21 and is in contact with the first ring roller 21 in the axial direction. The second intermediate shaft 52 extends on the central axis of the housing body 10. The other end surface of the second intermediate shaft 52 in the axial direction has a center hole 38, and a ball 96 is inserted into the center hole 38. A part of the ball 96 protrudes from the center hole 38. A part of the ball 96 protruding from the center hole 38 is in contact with the end surface on the other side in the axial direction of the first intermediate shaft 22. The structure in which the ball 96 is interposed between the first intermediate shaft 22 and the second intermediate shaft 52 prevents the rotation of the first intermediate shaft 22 from being directly transmitted to the second intermediate shaft 52.

  The plurality of second planetary rollers 53 are located at intervals in the circumferential direction of the second ring roller 51. The second planetary roller 53 is inscribed in a state where a surface pressure exists on the cylindrical inner peripheral surface of the second ring roller 51, and circumscribed in a state where a surface pressure exists on the cylindrical outer peripheral surface of the second intermediate shaft 52. Yes.

  As shown in FIG. 1, the width of the cylindrical inner peripheral surface of the second ring roller 51 is shorter than the axial length of the second planetary roller 53, and the entire surface of the cylindrical inner peripheral surface of the second ring roller 51 is While contacting the outer peripheral surface of the second planetary roller 53, the entire outer peripheral surface of the second planetary roller 53 is not in contact with the cylindrical inner peripheral surface of the second ring roller 51. In this way, the second ring roller 51 and the second planetary roller 53 are in contact with each other with a sufficient surface pressure.

  The second planet carrier 54 has a disk-shaped second carrier body 58 and a second drive pin 59, and the second carrier body 58 has a second pin insertion hole 60. As shown in FIG. 1, one end in the axial direction of the second drive pin 59 is fitted and fixed in a second pin insertion hole 60 of the second carrier body 58. The other end of the second carrier body 58 in the axial direction is fixed to the output shaft 4.

  A shaft of a rotary device (not shown), for example, a shaft of a plate making scanner of a printing machine, is coupled to the outer end portion of the output shaft 4. The output shaft 4 extends on the central axis of the housing body 10. The other end surface of the output shaft 4 in the axial direction has a center hole 39, and a ball 97 is inserted into the center hole 39. A part of the ball 97 protrudes from the center hole 39. A part of the ball 97 protruding from the center hole 39 is in contact with the other end surface of the second intermediate shaft 52 in the axial direction. The structure in which the ball 97 is interposed between the second intermediate shaft 52 and the output shaft 4 prevents the rotation of the second intermediate shaft 52 from being directly transmitted to the output shaft 4.

  The second double row ball bearing 55 is disposed between the second planetary roller 53 and the outer diameter surface of the second drive pin 59. The second double row ball bearing 55 supports the second planetary roller 53 so as to be rotatable (rotatable) with respect to the second drive pin 59.

  As shown in FIG. 1, a ball bearing 75 is arranged between the inner peripheral surface of the disc portion 70 of the cylindrical cup-shaped housing body 10 and the output shaft 4. The output shaft 4 is rotatably supported by the ball bearing 75 with respect to the housing body 10. The outer diameter end portion of the disc-shaped lid portion 11 of the housing 1 is fastened and fixed to the end surface of the housing main body 10 on the opposite side to the disc portion 70 side in the axial direction by fastening bolts 98.

  Further, when tightening with the tightening bolt 98, the first ring roller 21 and the second ring roller 51 are pivoted by the disc-shaped lid portion 11 of the housing 1 and the disc portion 70 of the housing body 10. Tightened by pinching in the direction. In this way, the first ring roller 21 and the second ring roller 51 are positioned in the axial direction, and the first ring roller 21 and the second ring roller 51 are prevented from rotating relative to the housing 1. .

  FIG. 2 is a schematic cross-sectional view of the first drive 2 showing the first drive 2 in detail. The second drive 3 is the same as the first drive 2. The description of the second drive 3 is omitted from the description of the first drive 2.

  As shown in FIG. 2, the inner peripheral surface of the first planetary roller 23 has a circumferential groove at the center in the axial direction, and a positioning stop ring 77 is fitted into the circumferential groove. The double row ball bearing 25 is fitted on the inner peripheral surface of the first planetary roller 23. The double row ball bearing 25 is in contact with the inner peripheral surface of the first planetary roller 23. The double row ball bearing 25 includes a pair of angular ball bearings 80 and 81. One angular ball bearing 80 has an outer ring 82, an inner ring 83, and a plurality of balls 84, while the other angular ball bearing 81 has an outer ring 86, an inner ring 87, and a plurality of balls 88. The pair of angular ball bearings 80, 81 are fitted and inserted into the inner peripheral surface of the first planetary roller 23 so as to come into contact with the positioning retaining ring 77.

  The drive pin 29 of the first drive 2 is a spring pin having a C-shaped cross section shown in the perspective view of FIG. The spring pin having a C-shaped cross section constitutes a rod-shaped elastic member having a C-shaped cross section and having elasticity. The material of the spring pin may be any material of a spring pin specified by JIS (Japanese Industrial Standard). The drive pin 29 is press-fitted to the inner diameter side of the inner ring 83 of one angular ball bearing 80 and is also press-fitted to the inner diameter side of the inner ring 87 of the other angular ball bearing 81. The drive pin 29 presses the inner ring 83 and the inner ring 87 outward in the radial direction. The drive pin 29 causes the inner ring 83 and the inner ring 87 to expand outward in the radial direction. The expansion of the inner ring 83 eliminates the bearing clearance of one angular ball bearing 80, and the expansion of the inner ring 87 eliminates the bearing clearance of the other angular ball bearing 81.

  As shown in FIG. 2, the first drive 2 includes a stop pin 79, and the stop pin 79 is one side in the axial direction of the drive pin 29 inserted through the first pin insertion hole 30 of the first carrier body 28. It is press-fitted into the inner diameter side of the end portion. In this way, the outer diameter surface of the end portion on one side in the axial direction of the drive pin 29 is expanded toward the inner peripheral surface side of the first pin insertion hole 30, and the end on the one side in the axial direction of the drive pin 29. A large pressure is generated between the outer diameter surface of the first portion and the inner peripheral surface of the first pin insertion hole 30.

  FIG. 4 is a schematic cross-sectional view in the radial direction passing through the center of the ball 84 of the angular ball bearing 80 in a part of the first drive 2. In FIG. 4, the elliptical deformation in the circumferential direction (revolution direction) of the first planetary roller 23 generated based on the pressure contact force indicated by arrows A and B in FIG. 4 is exaggerated.

  As shown in FIG. 4, each first drive pin 29 includes a plane including the central axis P <b> 1 of the first intermediate shaft 22 as a sun roller and the central axis P <b> 2 of the first planetary roller 23 surrounding the first drive pin 29. P3 passes through the notch 48 of the first drive pin 29 made of a spring pin having a C-shaped cross section.

  In the above configuration, in the two-stage reduction planetary mechanism, when the stepping motor 40 is driven to rotate, the first intermediate shaft 22 as the sun roller rotates through the shaft coupling 90. Then, as described above, the rotational power of the first intermediate shaft 22 is not transmitted to the second intermediate shaft 52 by the balls 96, but is transmitted to the first planetary roller 23 circumscribing the first intermediate shaft 22. Then, the first planetary roller 23 rotates at a reduced speed around the first drive pin 29. Then, since the first planetary roller 23 circumscribes the cylindrical outer peripheral surface of the first ring roller 21 that is stationary with respect to the housing 1, the rotation of the first intermediate shaft 22 together with the first drive pin 29 is caused by its rotation. Revolve around. Then, since the first drive pin 29 is fixed to the first carrier body 28 and the first carrier body 28 is fixed to the second intermediate shaft 52, the revolution power of the first drive pin 29 is the first It is transmitted to the second intermediate shaft 52 via the carrier body 28, and the revolution speed of the first planetary roller 23 is output as the rotation speed of the second intermediate shaft 52. In this way, the second intermediate shaft 52 rotates at a reduced speed with respect to the first intermediate shaft 22.

  Next, as described above, the rotational power of the second intermediate shaft 52 that rotates at a reduced speed relative to the rotation of the first intermediate shaft 22 is not transmitted to the output shaft 4 by the balls 97, but circumscribes the second intermediate shaft 52. It is transmitted to the second planetary roller 53. Then, the second planetary roller 53 rotates at a reduced speed around the second drive pin 59. Then, since the second planetary roller 53 circumscribes the cylindrical outer peripheral surface of the second ring roller 51 that is stationary with respect to the housing 1, the rotation of the second intermediate shaft 52 together with the second drive pin 59 is caused by its rotation. Revolve around. Then, since the second pin 59 is fixed to the second carrier body 58 and the second carrier body 58 is fixed to the output shaft 4, the revolving power of the second drive pin 59 causes the second carrier body 58 to move. The revolution speed of the second planetary roller 53 is output as the rotation speed of the output shaft 4. In this way, the output shaft 4 rotates at a reduced speed with respect to the second intermediate shaft 52. In this way, the rotating device coupled to the output shaft 4 is decelerated in two stages with respect to the rotation of the stepping motor 40 and rotates.

  According to the above-described embodiment, the inner peripheral surfaces of the angular ball bearings 80 and 81 as inner fitting portions fitted inside the planetary rollers 23 and 53 are pressed by the drive pins 29 and 59 formed of spring pins having a C-shaped cross section. The inner fitting portion can be expanded toward the planetary rollers 23 and 53 by this pressing. Therefore, the gap between the planetary rollers 23 and 53 and the drive pins 29 and 59 can be reduced, and the backlash caused by the gap can be efficiently reduced.

  Further, according to the above-described embodiment, the drive pins 29 and 59 formed of the spring pins having a C-shaped cross section having the notches 48 are disposed on the inner diameter side of the planetary rollers 23 and 53. The drive pins 29 and 59 can be easily arranged on the inner diameter side of the angular ball bearings 80 and 81. Further, since the angular ball bearings 80 and 81 are disposed on the inner diameter side of the drive pins 29 and 59 which are formed of spring pins having a notch 48 and are easily deformed and having a C-shaped cross section. 59 is disposed on the inner diameter side of the angular ball bearings 80, 81, and the outer diameter surfaces of the drive pins 29, 59 are arranged on the inner peripheral surfaces of the angular ball bearings 80, 81 with which the drive pins 29, 59 are in contact. The outer peripheral surface of the drive pins 29, 59 can be deformed so as to follow the shape, and the inner peripheral surface of the drive pins 29, 59 is closer to the inner peripheral surface thereof. The surface can be pressed. Therefore, the gap can be reduced easily and efficiently. Therefore, backlash can be reduced simply and efficiently, and higher positioning accuracy can be realized easily.

  Further, according to the above embodiment, the double row ball bearings 25 and 55 are arranged on the inner diameter side of the planetary rollers 23 and 53, so that the double row ball bearings 25 and 55 use the planetary rollers 23 and 59 to drive pins 29 and 59. 53 smooth rotations can be realized. Further, the inner rings 83, 87 can be efficiently expanded by the drive pins 29, 59 having a C-shaped cross section that are press-fitted into the inner diameter sides of the inner rings 83, 87 of the double row ball bearings 25, 55. Therefore, the bearing clearance can be reduced by the expansion of the inner rings 83 and 87, and the backlash can be reduced.

  Further, according to the above embodiment, the plane P3 including the central axis P1 of the intermediate shafts 22 and 52 as the sun rollers and the central axes P2 of the planetary rollers 23 and 53 surrounding the drive pins 29 and 59 has a C-shaped cross section. Passing through the notches 48 of the drive pins 29 and 59, each of which is a spring pin. Therefore, since the notches 48 of the drive pins 29 and 59 are oriented in the radial direction of the traction drives 2 and 3, the drive pins 29 and 59 can be expanded more efficiently in the revolving direction of the planetary rollers 23 and 53. . Therefore, the revolution-direction gap generated due to the elliptical deformation in the revolution direction of the planetary rollers 23, 53 based on the pressure contact of the planetary rollers 23, 53 is more efficiently closed by the deformation of the planetary rollers 23, 53. be able to. Therefore, backlash can be effectively reduced.

  Further, according to the embodiment, the end portions of the drive pins 29 and 59 are inserted into the pin insertion holes 30 by the stop pins 79 press-fitted into the inner diameter side of the end portions on one side in the axial direction of the drive pins 29 and 59. , 60 can be expanded to the inner surface side. Accordingly, a large pressure can be generated on the press-fitting surfaces of the carrier main bodies 28 and 58 and the drive pins 29 and 59, and the drive pins 29 and 59 can be hardly detached from the carrier main bodies 28 and 58.

  Further, according to the embodiment, since the drive pins 29 and 59 are spring pins having a C-shaped cross section, they are reliably and stably applied to the inner peripheral side of the planetary rollers 23 and 53 by using a spring action. Power can be granted. Therefore, backlash can be reliably and effectively reduced.

  In the above embodiment, the plane P3 including the central axis P1 of the intermediate shafts 22 and 52 as the sun rollers and the central axes P2 of the planetary rollers 23 and 53 surrounding the drive pins 29 and 59 is a spring having a C-shaped cross section. It passed through the notch 48 of the drive pins 29 and 59 consisting of pins. Further, the notches 48 of the drive pins 29 and 59 face the intermediate shafts 22 and 52 as sun rollers and do not face the ring rollers 21 and 51. However, in the present invention, with respect to the drive pin composed of all C-shaped spring pins, the plane including the center axis of the sun roller and the center axis of the planetary roller surrounding the drive pin passes through the notch of the drive pin. Furthermore, the notch of the drive pin made of at least one C-shaped spring pin does not have to face the ring roller side and the sun roller side. The present invention also relates to a drive pin comprising at least one C-shaped spring pin, and a plane including the central axis of the sun roller and the central axis of the planetary roller surrounding the drive pin passes through the notch of the drive pin. You don't have to.

  Moreover, in the said embodiment, the ring rollers 21 and 51 are fixed with respect to the housing 1, the fixing speed of the ring roller 21 is set to 0, the rotational speed of the intermediate shafts 22 and 52 as sun rollers is set as the input rotational speed, The revolution speed of the planetary carriers 24 and 54 is set as the output rotation speed, and the rotation speed of the intermediate shafts 22 and 52 is reduced. However, in the present invention, one of the three elements of the rotational speed of the ring roller, the rotational speed of the sun roller, and the rotational speed of the planet carrier (revolution speed of the planetary roller) is stationary (speed 0), one Is the input rotation speed, and one is the output rotation speed. The stationary (fixed) may be any of the above three elements, the input may be any of the above three elements, and the output may be any of the above three elements.

  In the above-described embodiment, the driving pin 29, 59 formed of a C-shaped spring pin is driven by press-fitting the stop pin 79 into the inner diameter side of one end in the axial direction on the carrier body 28, 58 side. The end portions of the pins 29 and 59 are expanded toward the inner surfaces of the pin insertion holes 30 and 60. However, in the present invention, the stop pin does not have to exist on the inner diameter side of the end portion on the carrier main body side in the axial direction of the drive pin formed of the C-shaped spring pin.

  In the above embodiment, the angular ball bearings 80 and 81 are arranged in two rows between the planetary rollers 23 and 53 and the drive pins 29 and 59 formed of C-shaped spring pins. However, in the present invention, the rolling bearings may be arranged in one row or three or more rows between the planetary roller and the drive pin formed of a C-shaped spring pin. In the present invention, the at least one bearing disposed between the planetary roller and the drive pin formed of a C-shaped spring pin is not an angular ball bearing but may be a deep groove ball bearing. A ball bearing other than the bearing may be used. In the present invention, at least one bearing disposed between the planetary roller and the drive pin formed of a C-shaped spring pin is not a ball bearing but a roller bearing (a cylindrical roller bearing, a tapered roller bearing, a convex surface ( Spherical surface roller bearings, needle roller bearings, etc.), and any rolling bearing other than ball bearings and roller bearings.

  In the above embodiment, the drive pins 29 and 59 formed of C-shaped spring pins are indirectly attached to the inner peripheral surfaces of the planetary rollers 23 and 53 via the double row ball bearings 25 and 55. Then, you may attach directly the drive pin which consists of a C-shaped spring pin to the internal peripheral surface of a planetary roller. This is because, by using an appropriate lubricant, even if there is a frictional force, the planetary roller can be received by sliding on the outer diameter surface of the drive pin composed of a C-shaped spring pin.

  Moreover, in the said embodiment, the bush did not exist between the planetary rollers 23 and 53 and the drive pins 29 and 59 which consist of C-shaped spring pins. However, in the present invention, an annular bush may exist between the planetary roller and the drive pin formed of a C-shaped spring pin.

  In the above embodiment, the width of the cylindrical inner peripheral surface of the ring rollers 21 and 51 is shorter than the axial length of the planetary rollers 23 and 53. In the present invention, the width of the cylindrical inner peripheral surface of the ring roller is It may be the same as the axial length of the planetary roller, or may be longer than the axial length of the planetary roller.

  In the above embodiment, the rotational power of the stepping motor 40 is input. However, the rotational power of a DC motor, an AC motor, a switched reluctance motor, or an ultrasonic motor may be input, or other than that. The rotational power generated by the rotational power drive device may be input. Further, in the above embodiment, the output shaft 4 is coupled to the shaft of the plate making scanner of the printing press. However, in the present invention, the output shaft may be coupled to the rotating shaft of any machine.

  Moreover, in the said embodiment, as shown in FIG. 3, the slit of the drive pins 29 and 59 which consist of a C-shaped spring pin was linear. However, in the present invention, the slit of the drive pin formed of a spring pin having a C-shaped cross section may have a shape other than a straight shape such as a wave shape.

  In the above embodiment, the rotational speed of the output shaft 4 is reduced in two stages with respect to the rotational speed of the first intermediate shaft 22 on the input side using the two traction drives 2 and 3. Using the planetary roller type traction drive of the invention, the rotational speed of the output shaft may be increased in two stages with respect to the rotational speed of the input shaft. Further, using three or more traction drives of the present invention, the rotational speed of the output shaft may be reduced or increased in three or more stages with respect to the rotational speed of the input shaft. In addition, using only one traction drive, the rotational speed of the output shaft may be increased in one step with respect to the rotational speed of the input shaft, and only one traction drive is used as follows. Thus, the rotational speed of the input shaft may be reduced in one step with respect to the rotational speed of the output shaft.

  FIG. 5 is a sectional view in the axial direction of the one-stage reduction planetary mechanism according to the embodiment of the present invention.

  In comparison with the two-stage reduction planetary mechanism shown in FIG. 1, this one-stage reduction planetary mechanism is configured so that the carrier body 128 of the planetary roller type traction drive 102 is connected to the second intermediate shaft (sun roller) of the second planetary roller type traction drive. 1 is different from the two-stage reduction planetary mechanism shown in FIG. 1 in that it is fixed to the outer peripheral surface of the output shaft 104 instead of being fixed to the outer peripheral surface.

  In this one-stage reduction planetary mechanism, when the intermediate shaft 122 as a sun roller that receives the rotational power of the input shaft 141 via the shaft coupling 190 rotates, the rotational power of the intermediate shaft 122 is transmitted to the output shaft 104 by the ball 196. On the other hand, the power non-transmission structure by the ball 196 is the same as the structure described in the two-stage reduction planetary mechanism, but is transmitted to the planetary roller 123 circumscribing the intermediate shaft 122. Then, the planetary roller 123 decelerates and rotates around the drive pin 129 formed of a spring pin having a C-shaped cross section. Then, the planetary roller 123 circumscribes the cylindrical outer peripheral surface of the ring roller 121 that is stationary with respect to the housing 101, and revolves around the intermediate shaft 122 together with the drive pin 129 by its rotation. Then, since the drive pin 129 is fixed to the carrier main body 128 and the carrier main body 128 is fixed to the output shaft 104, the revolving power of the drive pin 129 is transmitted to the output shaft 104 via the carrier main body 128, The revolution speed of the planetary roller 123 is output as the rotation speed of the output shaft 104. In this way, the output shaft 104 rotates at a reduced speed with respect to the intermediate shaft 122 in one step.

  In the above-described embodiment and modification, all of the rod-shaped elastic members having elasticity with a C-shaped cross section are spring pins with a C-shaped cross section. However, in the present invention, at least one of the rod-shaped elastic members having elasticity with a C-shaped section may be made of a material having elasticity other than the material used for the spring pin. At least one of the rod-shaped elastic members may be made of rubber, elastomer or the like. In the present invention, at least one of the rod-like elastic members having a C-shaped cross section and elasticity may be made of any material having known elasticity. In addition, the planetary roller traction drive of the present invention includes a printing machine feed mechanism, a labeler, an automation device, a lifting device and other devices that require positioning, a crushing machine, a crusher, a high-speed cutter, a jack, a stirrer, a cam drive, Needless to say, it may be used for any machine such as a crank drive. In addition, it is needless to say that a new embodiment can be constructed by combining two or more configurations among all the configurations described in the above-described embodiments and modifications.

DESCRIPTION OF SYMBOLS 1 Housing 2 1st planetary roller type traction drive 3 2nd planetary roller type traction drive 4 Output shaft 21 1st ring roller 22 1st intermediate shaft 23 1st planetary roller 24 1st planetary carrier 25 1st double row ball bearing 28 1st 1 carrier body 29 first drive pin 30 first pin insertion hole 48 notch of drive pin made of C-shaped spring pin 51 second ring roller 52 second intermediate shaft 53 second planetary roller 54 second planetary carrier 55 second compound Row ball bearing 58 Second carrier body 59 Second drive pin 60 Second pin insertion hole 79 Stop pin 80 First angular ball bearing 81 Second angular ball bearing 82 Outer ring of first angular ball bearing 83 Inner ring of first angular ball bearing 84 Ball of first angular ball bearing 86 Outer ring of second angular ball bearing 87 Second angular ball Inner ring 88 Ball of second angular ball bearing 90 Joint P1 Center axis of first intermediate shaft P2 Center axis of first drive pin P3 Center axis P1 of first intermediate shaft 22 as a sun roller, and first drive pin 29 A plane including the central axis P2 of the first planetary roller 23 surrounding the first planetary roller 23 A planetary roller traction drive 104 An output shaft 121 A ring roller 122 An intermediate shaft 123 A planetary roller 128 A carrier body 129 A drive pin 141 An input shaft

Claims (4)

A ring roller,
A sun roller located on the radially inner side of the ring roller;
An annular planetary roller inscribed in the inner peripheral surface of the ring roller and circumscribed in the outer peripheral surface of the sun roller;
E Bei a planet carrier having a rod-shaped elastic member having elastic that will be placed on the inner diameter side of the planetary rollers,
The rod-like elastic member has a notch along the axial direction of the central axis of the planetary roller on the outer peripheral surface of the rod-like elastic member, and a cross section perpendicular to the axial direction of the central axis of the planetary roller is C-shaped. ,
A rolling bearing having an outer ring fitted on the inner peripheral surface of the planetary roller, an inner ring, and a rolling element;
The planetary roller type traction drive , wherein the rod-like elastic member is press-fitted into an inner peripheral surface of the inner ring . The planetary roller traction drive according to claim 1 ,
A planetary roller type traction drive characterized in that a plane including the central axis of the sun roller and the central axis of the planetary roller passes through the notch of the bar-shaped elastic member having a C-shaped cross section. The planetary roller traction drive according to claim 1 or 2 ,
The planet carrier has a carrier body having a pin insertion hole through which one end of the rod-shaped elastic member is inserted,
A planetary roller traction drive comprising a stop pin press-fitted into an inner diameter side of one end of the rod-like elastic member. In the planetary roller traction drive according to claim 1乃Itaru 3,
A planetary roller traction drive characterized in that the rod-like elastic member is a spring pin.

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