JP2015227682A - Friction roller transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a friction roller transmission capable of solving problems including clogging of a lubricating oil passage, an increase in manufacturing cost, and an increase in pump loss by eliminating a dedicated lubricating oil passage.SOLUTION: A friction roller transmission 100 comprises: an input shaft 13; a sun roller 15; an annular roller 17; a plurality of intermediate rollers 19 rolling on and contacting a sun roller outer circumferential surface 41 and an annular roller inner circumferential surface 55; and an output shaft connected to the annular roller 17 or the intermediate rollers 19. Furthermore, the friction roller transmission 100 comprises: a plurality of roller holders 23 rotatably supporting the intermediate rollers 19 in reception hole inner circumferential surfaces 83 of support plate portions 81 via ball bearings 85, respectively; and a carrier 25 supporting the roller holders 23 between the sun roller outer circumferential surface 41 and the annular roller inner circumferential surface 55. An opening hole 27 for communicating outside with the ball bearing 85 is formed in each sun-roller side support plate portion 81 of the roller holder 23 supported by the carrier 25.

Description

  The present invention relates to a friction roller transmission.

  A traction drive is a kind of friction transmission device, and power is transmitted through an oil film formed between two surfaces having a smooth surface. Therefore, it has a feature that it can be operated with lower vibration and lower noise than a gear transmission. As a traction drive having a constant gear ratio, for example, there is a friction roller type speed reducer 200 as schematically shown in FIG. The friction roller reduction device 200 includes an input shaft 203, an output shaft 205, a sun roller 207, an annular roller 209, a plurality of intermediate rollers 211, and a loading cam device 213. The sun roller 207 has a pair of sun roller elements (first sun roller element 215 and second sun roller element 217) divided in the axial direction around the input shaft 203 with a gap interposed between the front end surfaces thereof. Deploy.

  The annular roller 209 is formed in an annular shape as a whole, and is supported and fixed to a fixed portion such as a housing (not shown) in a state of being arranged around the sun roller 207 and concentric with the sun roller 207. The intermediate roller 211 is rotatably supported by a rotation shaft 219 that is disposed in parallel with the input shaft 203. The base end portions of the rotation shafts 219 are supported and fixed to a carrier 221 coupled and fixed to the base end portion of the output shaft 205.

  The loading cam device 213 is provided on the base end surface side opposite to the front end surface of one of the first sun roller elements 215 and is supported by the input shaft 203. The loading cam device 213 rotates and drives the first sun roller element 215 toward the other second sun roller element 217 as the input shaft 203 rotates. In order to configure such a loading cam device 213, the retaining ring 222 is interposed between a retaining ring 222 that is locked in a circumferential groove formed in the intermediate portion of the input shaft 203 and the first sun roller element 215. A support ring 223, a disc spring 225, a cam ring 227, and a plurality of balls 229 are provided in order from the arrangement side.

  On the base end surface of the first sun roller element 215, driven cam surfaces 231 are provided at a plurality of locations in the circumferential direction. Further, on one side surface of the cam ring 227 facing the base end surface of the first sun roller element 215, drive side cam surfaces 233 are provided at a plurality of circumferential positions corresponding to the driven side cam surfaces 231. The driven cam surface 231 and the driving cam surface 233 have a shape in which the axial depth is deepest at the center in the circumferential direction and gradually becomes shallower toward both ends in the circumferential direction.

  In the loading cam device 213, when the input shaft 203 is stopped, the ball 229 is positioned at the deepest part of each cam surface. In this state, one first sun roller element 215 is pressed toward the other second sun roller element 217 by the elastic force of the disc spring 225. On the other hand, when the input shaft 203 rotates, each ball 229 moves to a shallow portion of the cam surface. Then, the distance between the first sun roller element 215 and the cam ring 227 is increased, and one of the first sun roller elements 215 is pressed toward the other second sun roller element 217. As a result, the one first sun roller element 215 is directed toward the other second sun roller element 217, and the elastic force of the disc spring 225 and the thrust generated by the ball 229 riding on each cam surface, It is driven to rotate while being pressed with a larger force.

  During the operation of the friction roller type speed reducer 200 as described above, the intermediate rollers 211 rotate about the respective rotation shafts 219 due to the axial thrust generated by the loading cam device 213, and the transmission torque varies. To be displaced in the radial direction. These intermediate rollers 211 are respectively supported by a carrier member 235 shown in FIG. The carrier 235 member has a pair of rim portions 237 arranged in concentric relations with each other as an annular shape. The rim portion 237 is connected and fixed at a plurality of equally spaced locations along the circumferential direction by column portions 239.

  The intermediate rollers 211 are rotatably supported by the roller holders 241 respectively. These roller holders 241 have a shape in which base end edges of a pair of support plate portions 243 that are parallel to each other are connected by a connecting plate portion 245.

  The end of the rotation shaft 219 of the intermediate roller 211 is rotatably supported by a ball bearing (not shown) at the tip of the support plate 243 of the roller holder 241. A swing shaft 247 shown in FIG. 14 projecting concentrically on both side surfaces of the base end portion of the roller holder 241 is inserted into a support hole 249 formed in a matching portion of the rim portion 237.

  In this friction roller type speed reducer, the intermediate roller 211 is smoothly displaced radially outward of the sun roller 207 and the annular roller 209 based on the swing displacement of the roller holder 241. Thereby, the surface pressure of a traction part is made appropriate and the transmission efficiency of the friction roller type reduction gear 200 is improved.

  By the way, during the operation of the friction roller type speed reducer, each traction portion that makes rolling contact between the outer peripheral surfaces of the intermediate roller 211 and the sun roller 207 and between the outer peripheral surface of the intermediate roller 211 and the inner peripheral surface of the annular roller 209 Torque is transmitted at. On the other hand, in the loading cam device 213, in order to increase the surface pressure of each of these traction portions, the peripheral surface of each roller is a non-cylindrical surface whose diameter changes in the axial direction. For this reason, in each traction part, a peripheral speed difference arises in the contact part of peripheral surfaces, and this causes a slip and generates heat. Under high surface pressure, this heat generation cannot be ignored, so it is necessary to cool each traction section.

  Therefore, in the friction roller type speed reducer, each traction portion is cooled by supplying lubricating oil as lubricating oil from both sides in the support direction of the carrier member 235. In this case, the lubricating oil is supplied from the carrier 221 side and the opposite housing side. The supplied lubricating oil is supplied to each traction portion through a column-portion oil passage 253 provided in the column portion 239 shown in FIG. Among these, about the inner diameter side traction portion, the lubricating oil is directly fed from the first radial direction supply path 255 provided two by two in the column portion 239. In addition, a second radial supply path is provided at a central portion in the width direction of the column portion 239 and between the first radial supply paths 255, and the outer diameter side opening 257 of the second radial supply path is provided with the annular roller 209. To the middle portion of the inner peripheral surface, the lubricant is opened so as to be supplied.

JP2013-104514A

  In the conventional friction roller type speed reducer 200, the lubricating oil is supplied from the carrier 221 side and the housing side, which are on both sides of the carrier member 235. As the oil passage in the carrier 221, there is a narrow in-carrier branch oil passage 251 not only in the column portion 239 but also in the rim portion 237. Further, a throttle 259 is provided in the middle of the in-carrier branch oil passage 251, and lubricating oil is sprayed from the throttle 259 toward the rotation shaft 219 of the intermediate roller 211.

However, since the manufacturing cost of the in-pillar oil passage 253 composed of thin and long oil passages increases, simplification of the oil passage structure is desired.
In addition, since the number of crossing portions between the oil passages increases, there are concerns about clogging of the oil passage due to burrs and foreign matters generated during drilling, and cost increase due to deburring during manufacturing.
Furthermore, since the pipe resistance increases as the oil passage becomes longer, there is a concern that pump loss increases and efficiency as a cooling unit decreases.

  SUMMARY OF THE INVENTION The present invention has been made in view of the above circumstances, and its object is to provide a friction roller type speed change mechanism that can eliminate clogging of a lubricating oil passage and an increase in manufacturing cost while suppressing pump loss without providing a special lubricating oil passage. Is to provide a machine.

The present invention has the following configuration.
(1) An input shaft, a sun roller disposed concentrically with the input shaft, an annular roller disposed concentrically with the sun roller on an outer peripheral side of the sun roller, a sun roller outer peripheral surface, and an annular roller inner peripheral surface A plurality of intermediate rollers that are rotatably supported around a rotation axis parallel to the input shaft and are in rolling contact with the outer peripheral surface of the sun roller and the inner peripheral surface of the annular roller, and an output shaft connected to the annular roller A friction roller transmission comprising:
A plurality of rollers having a pair of support plate portions covering both axial end portions of the rotation shaft of the intermediate roller, and rotatably supporting the intermediate roller via a rolling bearing on a receiving hole inner peripheral surface of the support plate portion A holder,
A carrier for supporting the plurality of roller holders between the outer peripheral surface of the sun roller and the inner peripheral surface of the annular roller;
With
A friction roller type transmission, wherein an opening hole is formed in the support plate portion on the sun roller side of the roller holder supported by the carrier to allow communication between the outside of the roller holder and the rolling bearing.
(2) The sun roller has a sun roller outer circumferential surface whose outer diameter increases toward the outside in the axial direction,
The friction roller transmission according to (1), wherein an axial position that is a maximum diameter of the outer peripheral surface of the sun roller is included in an axial range in which the opening hole of the roller holder is formed.
(3) An annular spacer is provided between the bearing end surface of the rolling bearing and the roller holder,
(1) or (2), wherein the annular spacer has a notch formed at a circumferential position facing at least an opening hole of the roller holder in a peripheral portion of a side surface facing the bearing end surface. Friction roller type transmission.

According to the friction roller transmission according to the present invention, it is possible to eliminate the clogging of the lubricating oil passage and the increase in the manufacturing cost without suppressing the pump loss without providing a special lubricating oil passage.
Further, according to the friction roller type transmission according to the present invention, the axial position where the maximum diameter of the outer surface of the sun roller is included in the axial range in which the opening hole of the roller holder is formed. The discharged lubricating oil is reliably supplied to the rolling bearing from the opening hole.
Further, according to the friction roller transmission according to the present invention, the lubricating oil that has entered the opening hole from the outside of the roller holder is once collected by the notch provided in the annular spacer and becomes an oil reservoir. Lubricating oil can be stably supplied from this oil reservoir to the rolling bearing.

It is a figure explaining embodiment of this invention, and is sectional drawing of a friction roller type transmission. It is a principal part enlarged view of the friction roller type transmission shown in FIG. It is a perspective view of the carrier which supported the some roller holder. It is an axial sectional view of a carrier in which an oil passage to a sun roller is formed. It is sectional drawing of the friction roller type transmission showing the oil supply condition to a sun roller. It is a perspective view of the roller holder in which the opening hole was formed. It is a disassembled perspective view of the roller holder shown in FIG. FIG. 3 is a perspective view of the annular spacer shown in FIG. 2. It is operation | movement explanatory drawing showing the flow of the lubricating oil from a sun roller to a rolling bearing. It is a perspective view of the annular spacer which concerns on a modification. It is operation | movement explanatory drawing showing the flow of the lubricating oil at the time of using the annular spacer shown in FIG. It is sectional drawing of the conventional friction roller type reduction gear. It is a perspective view of the conventional intermediate roller holder. FIG. 14 is an exploded perspective view of the intermediate roller holder shown in FIG. 13.

Hereinafter, embodiments according to the present invention will be described in detail with reference to the drawings.
FIG. 1 is a diagram illustrating an embodiment of the present invention, and is a cross-sectional view of a friction roller type transmission 100.
The friction roller type transmission 100 having this configuration includes an input shaft 13, a sun roller 15, an annular roller 17, an intermediate roller 19, an output shaft 21, a roller holder 23, and a carrier 25. In this configuration, an opening hole 27 (see FIG. 6) is provided in a part of the carrier 25 so that lubricating oil can be easily supplied to the intermediate roller 19.

  The friction roller transmission 100 is attached to a housing 29 that is a reduction gear case. The friction roller type transmission 100 rotationally drives the sun roller 15 by an electric motor (not shown) provided outside the housing 29 and transmits the rotation of the sun roller 15 to the annular roller 17 through a plurality of intermediate rollers 19. . The annular roller 17 and the output shaft 21 are connected by a connecting bracket 33 in a state where they are arranged concentrically with each other. Therefore, the rotation of the annular roller 17 is taken out through the output shaft 21.

  A rolling bearing unit 35 having an oil tight holding structure is installed on the inner peripheral surface 24 of the housing 29, and the input shaft 13 is rotatably supported by the bearing unit 35.

FIG. 2 is an enlarged view of a main part of the friction roller transmission 100 shown in FIG.
The sun roller 15 is disposed concentrically with the input shaft 13 and has a pair of sun roller elements (a first sun roller element 37 and a second sun roller element 39) divided into two in the axial direction. The first sun roller element 37 and the second sun roller element 39 are provided with inclined surfaces whose outer diameters gradually increase from the inner end surfaces 43, 43 on the gap side of the sun roller elements 37, 39 toward the outer end surfaces 45, 45 on the opposite side. It is formed on the outer peripheral surfaces 41, 41.

  A loading cam mechanism 47 is provided between the sun roller 15 and the output shaft 21. The sun roller 15 is a movable sun roller element in which at least one sun roller element (second sun roller element 39 in the present configuration) is movably disposed in the axial direction. As the rotational torque of the input shaft 13 increases, the loading cam mechanism 47 presses the second sun roller element 39 in the axial direction toward the first sun roller element 37 side, and the axial distance between the pair of sun roller elements is narrowed. To do.

  The cam ring 49 that constitutes the loading cam mechanism 47 is press-contacted by a loading nut 51 that is screwed and fixed to the input shaft 13, and rotates integrally with the input shaft 13 and the loading nut 51.

  The loading cam mechanism 47 includes a plurality of driven cam surfaces, driving cam surfaces, and balls 53 disposed between the cam surfaces, as in the conventional loading cam device shown in FIG. The loading cam mechanism 47 is described in detail in, for example, Japanese Patent Application Laid-Open No. 2012-197930. In addition to the above configuration, the loading cam mechanism 47 may have other configurations as long as it is a mechanism that generates thrust in the axial direction according to the rotational torque. Good.

  The annular roller 17 is formed in an annular shape as a whole, and is arranged concentrically with the sun roller 15 on the outer peripheral side of the sun roller 15 and rotates integrally with the output shaft 21.

  The intermediate roller 19 is supported between the sun roller outer peripheral surface 41 and the annular roller inner peripheral surface 55 so as to be rotatable about a rotation shaft 57 parallel to the input shaft 13. In this configuration, three intermediate rollers 19 are provided. The intermediate roller 19 is in rolling contact with the sun roller outer peripheral surface 41 and the annular roller inner peripheral surface 55.

FIG. 3 is a perspective view of the carrier 25 supporting a plurality of roller holders 23.
The intermediate roller 19 is supported by a carrier 25 supported and fixed to the housing 29 by the same number of roller holders 23 as the intermediate roller 19 so that the intermediate roller 19 can be rotated and slightly displaced in the radial direction of the carrier 25. The carrier 25 includes an annular connecting plate portion 59 and pillar portions 61 arranged at a plurality of locations (three locations in the illustrated example) that are equally spaced in the circumferential direction on one axial side surface of the connecting plate 59. Have. The column part 61 is formed on the surface of the connecting plate part 59 on the intermediate roller 19 side so as to protrude along the axial direction of the carrier 25.

  The roller holder 23 is installed between the column parts 61 adjacent to each other in the circumferential direction. The roller holder 23 is disposed so as to be swingable and displaceable about a swing support shaft 77 that is fixed by connecting each base end to one axial side surface of the connecting plate portion 59.

  The rotation shaft 57 of the intermediate roller 19 is rotatably supported by holding portions 62 provided at both axial ends of the roller holder 23 via rolling bearings (ball bearings) 85.

  The output shaft 21 is connected to the annular roller 17 by a connecting bracket 33 in a state of being arranged concentrically with each other.

FIG. 4 is an axial sectional view of the carrier 25 in which an oil passage to the sun roller 15 is formed.
Inside the connecting plate portion 59 and the column portion 61 constituting the carrier 25, a lubricating oil supply path is provided. These supply paths are respectively an axial supply path 65 formed in the column portion 61 of the carrier 25, an inner diameter direction supply path 67, 67 and an outer diameter direction supply path 69 formed in the radial direction through the axial supply path 65. It consists of. The axial direction supply path 65 communicates the respective rear end portions with the intermediate portions of the inner diameter direction supply paths 67 and 67 and opens the base end portion to the distal end surface 71 of the column portion 61. The inner diameter direction supply paths 67 and 67 block the radially outer end of the carrier 25 by press-fitting stop plugs 73 and 73, respectively.

  FIG. 5 is a cross-sectional view of the friction roller type transmission 100 showing the state of oil supply to the sun roller 15. Unlike FIG. 1 shown at the cross-sectional position including the rotation axis of the intermediate roller 19, FIG. 5 shows the cross-sectional position including the column part 61.

  The axial supply path 65 opened in the tip surface 71 of the column part 61 is communicated with a main supply path 75 formed in the housing 29. The main supply path 75 is connected to an oil supply source such as an oil feed pump (not shown). During operation of the apparatus incorporating the friction roller transmission 100, lubrication from the oil supply source is performed on the axial supply path 65, the inner diameter direction supply paths 67 and 67, and the outer diameter direction supply path 69 via the main supply path 75. The oil can be sent.

  In the friction roller type transmission 100, when lubricating oil is supplied to the axial supply path 65 provided inside the column portion 61, the supplied lubricating oil is supplied to the inner diameter direction supply paths 67 and 67 and the outer diameter direction supply path. 69. The lubricating oil sent to the inner diameter direction supply paths 67, 67 is supplied to the sun roller outer peripheral surface 41 of the sun roller 15 (arrow 63 in the figure). The lubricating oil sent to the outer diameter direction supply path 69 is supplied to the inner peripheral surface 55 of the annular roller.

Next, the configuration of the roller holder 23 will be described.
As shown in FIG. 2, the carrier 25 supports the plurality of roller holders 23 between the sun roller outer peripheral surface 41 and the annular roller inner peripheral surface 55. Further, as shown in FIG. 3, the roller holders 23 are respectively installed at portions between the column portions 61 adjacent to each other in the circumferential direction of the carrier 25. Each roller holder 23 is freely swingable about a swing support shaft 77 having a base end portion coupled and fixed to one axial side surface of the connecting plate portion 59.

6 is a perspective view of the roller holder 23 in which the opening hole 27 is formed, and FIG. 7 is an exploded perspective view of the roller holder 23 shown in FIG.
The roller holder 23 has a pair of support plate portions 81 that cover both axial end portions of the rotation shaft 57 of the intermediate roller 19, and a ball bearing 85 is provided on a receiving hole inner peripheral surface 83 of the support plate portion 81 shown in FIG. 7. The intermediate roller 19 is rotatably supported. The support plate 81 (see FIG. 3) on the sun roller 15 side of the roller holder 23 is formed with an opening hole 27 through which the outside and the ball bearing 85 are passed.

  An annular spacer 79 is provided between the bearing end surface 87 of the ball bearing 85 and the roller holder 23. FIG. 8 is a perspective view of the annular spacer 79 shown in FIG. The annular spacer 79 has a notch 89 formed at a circumferential position facing at least the opening hole 27 of the roller holder 23 on the side surface facing the bearing end surface 87. The annular spacer 79 is fixed with respect to the rotation direction on the inner peripheral surface of the support plate portion 81 of the roller holder 23.

Next, the operation of the friction roller transmission 100 having the above configuration will be described.
FIG. 9 is an operation explanatory view showing the flow of lubricating oil from the sun roller 15 to the ball bearing 85.

  The sun roller 15 has an outer peripheral surface whose outer diameter increases toward the outer side in the axial direction. The axial position that is the maximum diameter of the outer circumferential surface of the sun roller is included in the axial range in which the opening hole 27 of the roller holder 23 is formed.

  The notched portion 89 of this configuration extends from the outer peripheral position of the annular spacer 79 to the annular gap 95 between the inner ring 91 and the outer ring 93 of the rolling bearing in the radial direction.

  According to the friction roller type transmission 100 having the above configuration, the lubricating oil is supplied to the traction surface of the sun roller 15 from the inner diameter direction supply paths 67 and 67 of the carrier 25 as shown in FIG. This lubricating oil is supplied directly from the carrier 25 to the sun roller 15 without passing through a special lubricating oil path for cooling the ball bearing 85 that supports the intermediate roller 19.

  As shown in FIG. 9, the lubricating oil supplied to the sun roller 15 cools the traction surface of the sun roller 15, and then part of the lubricating oil flows along the maximum diameter side of the sun roller 15 that rotates at a high speed. The lubricating oil (see arrow 63) that has flowed to the maximum diameter side with a high peripheral speed finally moves to the maximum diameter portion of the sun roller 15 and is released from the maximum diameter portion in the tangential direction of the element outer peripheral surface by centrifugal force. The That is, the lubricating oil is discharged from the outer peripheral surface of the maximum diameter portion of the sun roller 15 toward the outer peripheral portion in the radial direction.

  A part of the lubricating oil discharged to the peripheral portion is collected in the opening hole 27 formed in the support plate portion 81 of the roller holder 23 and supplied to the inside of the roller holder 23 from the opening hole 27. In this configuration, since the axial position where the maximum diameter of the outer surface of the sun roller is included is included in the axial range where the opening hole 27 is formed, the lubricating oil released by the centrifugal force from the sun roller 15 is reliably supplied to the opening hole 27. To be supplied.

  The lubricating oil supplied to the opening hole 27 passes through the receiving hole inner peripheral surface 83 of the support plate 81 and is guided to the ball bearing 85. Accordingly, the lubricating oil is supplied from the sun roller 15 rotating at a high speed to the opening hole 27 of the roller holder 23 without passing through a special lubricating oil passage, and then smoothed by the inertial force, centrifugal force, capillary action, etc. of the lubricating oil. Thus, the target ball bearing 85 is reached.

  Specifically, in the friction roller type transmission 100 of the present configuration, the lubricating oil that has flowed to the outer diameter side of the sun roller 15 matches the locus in the tangential direction from the axial position where the maximum diameter of the outer peripheral surface of the sun roller is reached. Released in an annular shape. As described above, the annular lubricating oil supply range includes the position of the opening hole 27 formed in the support plate portion 81 of the roller holder 23, and the lubricating oil can be reliably supplied to the opening hole 27. .

  Further, in the friction roller type transmission 100 having the above-described configuration, a notch 89 is provided in an annular spacer 79 installed between the roller holder 23 and the intermediate roller 19. The notch 89 has a groove shape that does not penetrate to the inner diameter side, so that the supplied lubricating oil forms an oil reservoir. As a result, a predetermined amount of lubricating oil can be held in the opening hole 27, and the lubricating oil can be constantly supplied into the ball bearing 85 stably. In other words, it is possible to stably supply the ball bearing 85 to the ball bearing 85 by a capillary phenomenon or the like from the oil pool of the lubricating oil once collected in the notch 89. The lubricating oil supplied to the inside of the ball bearing 85 enters the inner roller rolling surface from an annular gap 95 formed between the outer ring 93 and the inner ring 91 and spreads over the entire bearing.

  Further, the notch 89 of the annular spacer 79 reaches the annular gap 95 between the inner ring 91 and the outer ring 93 of the ball bearing 85. As a result, the lubricating oil enters the opening hole 27 from the outside of the roller holder 23, flows into the notch 89, and is reliably introduced into the ball bearing 85 through the annular gap 95. Thus, the notch 89 forms an oil passage for guiding and smoothly introducing the lubricating oil between the opening hole 27 and the inside of the ball bearing 85.

  The annular spacer 79 is rotationally restricted and fixed to the inner peripheral surface (receiving hole inner peripheral surface 83) of the support plate portion 81 of the roller holder 23. For this reason, the notch part 89 and the opening hole 27 can always be maintained in a state in which the phases coincide with each other. Therefore, the rotational position of the annular spacer 79 is not shifted even during operation of the transmission, and the lubricating oil collected in the opening hole 27 can be stably supplied to the inside of the ball bearing 85.

  Further, a groove (not shown) connected to the opening hole 27 along the axial direction may be formed on the outer peripheral surface 97 of the support plate 81 of the roller holder 23. In that case, the lubricating oil supplied from the sun roller 15 is collected in the groove portion and introduced into the opening hole 27 from the groove portion, whereby the amount of lubricating oil supplied to the ball bearing 85 can be increased.

Next, a modification of the annular spacer will be described.
FIG. 10 is a perspective view of an annular spacer 99 as a modification, and FIG. 11 is an operation explanatory view showing the flow of lubricating oil when the annular spacer 99 shown in FIG. 10 is used.
The annular spacer 99 of this modification has the same configuration as the annular spacer 79 described above except that an annular thin portion 101 is further formed on the outer peripheral edge portion on the bearing end surface side.

  In the friction roller type transmission 100, the opening hole 27 formed in the roller holder 23 and the notch 89 formed in the annular spacer 79 need to be assembled with the same phase. Further, in the case where the rolling bearing is not preloaded by the roller holder 23, the annular spacer 79 has an outer diameter between the outer diameter of the annular spacer 79 and an inner diameter of the inner peripheral surface 83 of the receiving hole so that it does not rotate during operation. Rotation is restricted by press-fitting, bonding, and pin fixing.

  Therefore, if the annular spacer 99 provided with the annular thin portion 101 is used at the outer peripheral edge portion, the spacer-side notch 89 and the roller holder side opening hole 27 are formed by the annular thin portion 101 as shown in FIG. Even if it is an arbitrary relative rotation angle θ, it communicates. By using such an annular spacer 99, the roller holder 23 does not need to match the phase of the notch 89 of the annular spacer 99 and the opening hole 27 during assembly.

  According to the friction roller type transmission 100 of each configuration example described above, clogging of the lubricating oil passage and increase in manufacturing cost can be eliminated while suppressing pump loss without providing a special lubricating oil passage.

  The present invention is not limited to the above-described embodiments, and the configurations of the embodiments may be combined with each other, or may be modified or applied by those skilled in the art based on the description of the specification and well-known techniques. The invention is intended and is within the scope of seeking protection.

DESCRIPTION OF SYMBOLS 13 Input shaft 15 Sun roller 17 Annular roller 19 Intermediate roller 21 Output shaft 23 Roller holder 25 Carrier 27 Opening hole 41 Sun roller outer peripheral surface 55 Annular roller inner peripheral surface 57 Autorotation shaft 79 Annular spacer 81 Support plate part 83 Receiving hole inner peripheral surface 85 Rolling bearing (Ball bearing)
87 Bearing end face 89 Notch 100 Friction roller type transmission

Claims (3)

Between the input shaft, the sun roller disposed concentrically with the input shaft, the annular roller disposed concentrically with the sun roller on the outer peripheral side of the sun roller, and the sun roller outer peripheral surface and the annular roller inner peripheral surface, A plurality of intermediate rollers that are rotatably supported around a rotation axis parallel to the input shaft, and that are in rolling contact with the outer peripheral surface of the sun roller and the inner peripheral surface of the annular roller; and an output shaft connected to the annular roller. A friction roller type transmission comprising:
A plurality of rollers having a pair of support plate portions covering both axial end portions of the rotation shaft of the intermediate roller, and rotatably supporting the intermediate roller via a rolling bearing on a receiving hole inner peripheral surface of the support plate portion A holder,
A carrier for supporting the plurality of roller holders between the outer peripheral surface of the sun roller and the inner peripheral surface of the annular roller;
With
A friction roller type transmission, wherein an opening hole is formed in the support plate portion on the sun roller side of the roller holder supported by the carrier to allow communication between the outside of the roller holder and the rolling bearing. The sun roller has a sun roller outer peripheral surface whose outer diameter increases toward the outside in the axial direction,
2. The friction roller transmission according to claim 1, wherein an axial position that is a maximum diameter of the outer peripheral surface of the sun roller is included in an axial range in which the opening hole of the roller holder is formed. An annular spacer is provided between a bearing end surface of the rolling bearing and the roller holder,
The notch part is formed in the circumferential position where the said annular spacer faces the opening hole of the said roller holder at least of the peripheral part of the side surface which faces the said bearing end surface, The Claim 1 or Claim 2 characterized by the above-mentioned. Friction roller type transmission.

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