JP2008025631A - Under-race lubrication bearing - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an under-race lubrication bearing greatly improved in a supply amount of lubricating oil to respective sliding sections. <P>SOLUTION: In this under-race lubrication bearing, a retainer 4 has, at both axially longitudinal ends thereof, two annular inclined walls 6, 7 inclinedly extending from an outer ring side toward the outside of the bearing of an inner ring side, and oil supplying holes are formed at the inner ring so as to supply lubricating oil to two hollow spaces defined by the annular inclined walls 6, 7, end faces of a plurality of rolling members, and the inner ring. The annular inclined walls 6, 7 have, on hollow space side surfaces thereof, a plurality of recessed grooves 20 extending from the inner ring side to the outer ring side. It is preferable, in order to increase an amount of the lubrication oil, that the recessed grooves 20 are inclined with respect to a circumferential direction of the hollow space side surfaces of the annular inclined walls 6, 7 in such a manner that the outer ring side end position 20a is on an opposite side of the inner ring-side end position 20b with respect to the rotation direction of the retainer 4. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to an under-race lubricated bearing having an under-race lubrication structure that feeds lubricating oil to a sliding portion through an inner ring fixed to a rotating inner shaft.

  Under-lace lubricated bearings are used for high-speed rotating bearings in aircraft jet engines, machine tools, and the like because sufficient lubricating oil needs to be supplied to the sliding portions. In addition, as such an under-lace lubricated bearing, the lubricating oil is sufficiently supplied to each sliding portion such as between the cage and the rolling element, the raceway surface of the rolling element, and between the cage and the inner ring. The inventor has previously proposed the under-lace lubricated bearing described in Patent Document 1.

  As shown in FIGS. 3 and 4, this underlace lubricated bearing includes an inner ring 1, an outer ring 2, a cylindrical roller 3 as a rolling element interposed between the inner and outer rings, and a cage that holds the cylindrical roller 3. 4. The inner ring 1 is fixed to a rotating inner shaft (not shown), the outer ring 2 is fixed to the vehicle body and is stationary, and the cage 4 is located between the inner and outer rings and is slower than the inner ring 1 ( Rotating at about half the speed of the inner ring 1). The cage 4 includes a cylindrical portion 5 that is disposed near the outer ring 2 and that is parallel to the axis, and two annular inclined walls 6 and 7 that are formed at both ends of the cylindrical portion 5 in the axial direction. Yes. The two annular inclined walls 6 and 7 are formed at both end portions of the cylindrical portion 5 so as to extend while being inclined toward the bearing outer side from the outer ring 2 side toward the inner ring 1 side, and each tip end is in sliding contact with the inner ring 1. Is formed. Further, the cylindrical portion 5 of the cage 4 is formed with radial through holes at a predetermined pitch. The through holes are alternately arranged as pockets 8 that hold the cylindrical rollers 3 and those formed as radial through holes 9 that do not hold the cylindrical rollers 3.

  And the oil supply hole 12 which supplies lubricating oil to each of the two cavity parts 10 and 11 formed with both the cyclic | annular inclined walls 6 and 7, both end surfaces of the some cylindrical roller 3 as a rolling element, and the inner ring | wheel 1, 13 is formed in the inner ring 1. The oil supply holes 12 and 13 are connected to an oil supply path (not shown) provided in the shaft center of the inner shaft through an oil supply hole (not shown) formed in the inner shaft (not shown). At least one of them that communicates with each of the hollow portions 10 and 11 is provided. Further, the lubricating oil is supplied from the oil supply passage (not shown) of the inner shaft to the oil supply hole of the inner ring 1 by centrifugal action caused by the rotation of the inner shaft (not shown).

The lubricating oil supplied to the hollow portions 10, 11 flows along the outer surface of the inner ring 1, between the cylindrical roller 3 and the raceway surface of the inner ring 1, and between the annular inclined walls 6, 7 in the cage 4. Lubricate between the tip and the raceway surface of the inner ring 1. The lubricating oil supplied to the cavities 10 and 11 adheres to the inner surfaces of the annular inclined walls 6 and 7 on the side of the cavities 10 and 11, and the end faces of the pockets 8 and the radial through holes 9 of the cylindrical part 5 by centrifugal force. Flows to the outer ring 2 side. Lubricating oil flows in this way, whereby lubrication between the cylindrical roller 3 and the end face of the pocket 8 of the cage 4 is performed. The space between the cylindrical roller 3 and the raceway surface of the outer ring 2 is lubricated by the lubricating oil that has flowed to the outer ring 2 side. The lubricating oil used for lubricating each sliding portion in this way is configured to be cooled and recirculated after being pushed out from the bearing portion.
JP 2001-165178 A

  As described above, in the previously proposed underlace lubricated bearing, the two hollow portions 10 formed by the two annular inclined walls 6 and 7, both end faces of the cylindrical roller 3 as a plurality of rolling elements, and the inner ring 1. , 11 is configured to supply lubricating oil from the inner shaft side through oil supply holes 12, 13 formed in the inner ring 1. The conventional under-lace lubricated bearing is configured as described above, so that the cylindrical roller 2 and the raceway surface of the inner ring 1, the annular inclined walls 6 and 7 and the raceway surface of the inner ring 1, the cylindrical roller 3 and the end face of the pocket of the retainer 4, between the cylindrical roller 3 and the raceway surface of the outer ring 2, etc., to increase the amount of lubricating oil supplied to each sliding portion, and to improve the lubrication performance is there. However, in the field of high-speed rotary bearings in aircraft jet engines, machine tools, and the like, an increase in lubricating oil supplied to the sliding portion is constantly being pursued in order to further increase the speed and extend the life.

  The present invention has been made in view of such circumstances, and an object of the present invention is to improve the above-described conventional underlace lubricated bearing so as to further increase the supply amount of lubricating oil to each sliding portion. .

  The under-lace lubricated bearing of the present invention has a cage in which rolling elements are rotatably held in a plurality of pocket portions, and the bearing outer side from the outer ring side toward the inner ring side is provided at both axial ends of the cage. Two annular inclined walls extending obliquely are formed. Further, an oil supply hole is formed in the inner ring so as to supply lubricating oil to two hollow portions formed by both the annular inclined walls, both end faces of the plurality of rolling elements, and the inner ring. A plurality of concave grooves extending from the inner ring side to the outer ring side are formed on each of the hollow portion side surfaces of both annular inclined walls.

  According to the under-lace lubricated bearing having the above configuration, the lubricating oil is supplied from the oil supply holes formed in the inner ring to the two hollow portions formed by the two annular inclined walls, the both end faces of the plurality of rolling elements, and the inner ring. Supplied. Further, the lubricating oil supplied to the cavity portion in the cage adheres to the cavity side surface of both annular inclined walls and is pumped to the outer ring side of the cylindrical portion by the centrifugal force accompanying the rotation of the cage. In this operation, since the concave groove is formed on the cavity-side surface of the annular inclined wall, the surface area of the cavity-side surface of the annular inclined wall increases, and the lubricating oil that is retained on the cavity-side surface of the annular inclined wall Increases, and the amount of lubricating oil pumped to the outer ring increases. As a result, the amount of lubricating oil supplied between the cylindrical roller and the end face of the pocket of the cage, or between the cylindrical roller and the raceway surface of the outer ring is increased, and the lubricating performance of the bearing is improved.

  Further, each of the plurality of grooves is inclined with respect to the circumferential direction of the cavity side surface of the annular inclined wall, and the position of the outer ring side end of the groove is held with respect to the position of the inner ring side end. It is preferable to incline so as to be located in the counter-rotating direction of the vessel. If it does in this way, the length of each ditch | groove can be lengthened, and the surface area of the cavity part side surface of a cyclic | annular inclined wall can further be increased. Moreover, the pump function of a ditch | groove can be improved by inclining a ditch | groove as mentioned above. As a result, the amount of lubricating oil supplied to each sliding portion is increased, and the lubricating performance of the bearing is improved.

  Moreover, it is preferable that each of the plurality of concave grooves is formed in a curved shape that curves so as to be convex toward the outer ring side. When formed in this way, the groove can be further lengthened, so that the surface area of the cavity side surface of the annular inclined wall can be further increased, the amount of lubricating oil to each sliding portion is further increased, and the bearing The lubricating performance can be further improved.

  According to the present invention, the amount of lubricating oil supplied to each sliding portion from the inner ring side to the outer ring side is increased and the lubricating performance is improved as compared with the conventional under-lace lubricated bearing.

  Hereinafter, an underlace lubricated bearing according to an embodiment of the present invention will be described. The under-lace lubricated bearing according to the present embodiment is an improvement of the cage 4 in the conventional under-lace lubricated bearing shown in FIGS. 3 and 4. FIG. 1 shows the under-lace lubricated bearing according to the present embodiment. The principal part perspective view of the holder | retainer in a race lubrication bearing is shown. Moreover, in FIG. 2, sectional drawing in the axial direction center of the same holder | retainer is shown. 2 corresponds to the cage 4 taken along line AA in FIG. 1 and 2, the same reference numerals are used for the parts common to FIGS. 3 and 4, and in the description of the underlace lubricated bearing according to the present embodiment, the reference numerals of FIGS. 3 and 4 are used. It explains using.

  The under-lace lubricated bearing according to the present embodiment has all the configurations described in FIGS. 3 and 4, and the cavities 10 and 11 of the annular inclined walls 6 and 7 of the cage 4 in such a configuration. A plurality of grooves 20 extending from the inner ring 1 side to the outer ring 2 side are additionally formed on the side surface (see FIGS. 1 and 2). Hereinafter, the under-lace lubricated bearing according to the present embodiment will be described focusing on the difference from the conventional under-lace lubricated bearing, that is, the configuration of the cage 4.

  As shown in FIGS. 1 and 2, each groove 20 formed in a plurality of strips is inclined with respect to the circumferential direction of the cavity side surface of the annular inclined walls 6, 7, and the outer ring side end of the groove 20. The position 20a of the portion is formed so as to be inclined with respect to the position 20b of the end portion on the inner ring side so as to be positioned in the counter-rotating direction of the cage 4. Each concave groove 20 is formed in a curved shape that curves so as to be convex toward the outer ring 2 side. The concave grooves 20 are formed at equal intervals with a pitch of a predetermined dimension.

  According to the underlace lubricated bearing of the present embodiment configured as described above, lubrication is basically performed in the same manner as a conventional underlace lubricated bearing. That is, the lubricating oil is supplied to the two hollow portions 10 and 11 from the oil supply holes 12 and 13 formed in the inner ring 1, respectively. Further, the lubricating oil supplied to the cavities 10 and 11 slides between the cylindrical roller 3 and the raceway surface of the inner ring 1 and the tips of the annular inclined walls 6 and 7 of the cage 4 and the raceway of the inner ring 1. The sliding part between the surfaces is lubricated. Further, the lubricating oil supplied to the cavities 10 and 11 adheres to the surfaces of the annular inclined walls 6 and 7 on the side of the cavities 10 and 11, and the pocket 8 of the cylindrical portion 5 is caused by the centrifugal force accompanying the rotation of the cage 4. And is fed to the outer ring 2 side through the end face of the radial through hole 9. Then, lubrication between the cylindrical roller 3 and the end face of the pocket 8 of the cage 4 is performed by the lubricating oil flowing in this way.

  In the underlace lubricated bearing according to the present embodiment, since the concave groove 20 is formed on the surface of the annular inclined walls 6 and 7 on the side of the hollow portions 10 and 11, the hollow portion 10 of the annular inclined walls 6 and 7. The surface area of the surface on the 11 side increases, the lubricating oil retained on the surface of the hollow portions 10 and 11 of the annular inclined walls 6 and 7 increases, and the amount of lubricating oil pumped to the outer ring 2 side increases. As a result, the amount of lubricating oil supplied between the cylindrical roller 3 and the end face of the pocket 8 of the cage 4 or between the cylindrical roller 3 and the raceway surface of the outer ring 2 is increased, and the lubricating performance of the bearing is improved. .

  Further, according to the underlace lubricated bearing according to the present embodiment, each of the plurality of grooves 20 is inclined with respect to the circumferential direction of the cavity side surface of the annular inclined walls 6 and 7, and the grooves The position 20a of the outer ring side end portion 20 is inclined with respect to the position 20b of the inner ring side end portion so as to be positioned in the counter-rotating direction of the cage 4. With respect to such a configuration, the concave groove 20 is formed at right angles to the circumferential direction of the cavity side surface of the annular inclined walls 6 and 7, that is, the position 20a of the outer ring side end and the position 20b of the inner ring side end. Can also be formed at the same angle in the rotation direction of the cage 4. However, as compared with the case of forming in this way, in the case of the present embodiment, the length of each concave groove 20 can be increased, and the surface area of the surface of the annular inclined walls 6, 7 on the cavity 10, 11 side is increased. It can be further increased. Moreover, the pump function by the concave groove 20 can also be improved by inclining as in the present embodiment. As a result, the amount of lubricating oil supplied to each sliding portion is increased, and the lubricating performance of the bearing is improved.

  Further, the plurality of grooves 20 can be formed so as not to protrude in either the outer ring 2 side or the inner ring 1 side, but compared to the grooves formed in this way, As in the embodiment, in the case where each is formed in a curved shape so as to be convex toward the outer ring 2, the concave groove 20 can be made longer. Thereby, the surface area of the cavity 10, 11 side surface of the annular inclined walls 6, 7 can be further increased. As a result, the amount of lubricating oil to each sliding portion can be further increased, and the lubricating performance of the bearing can be further improved.

  In the present embodiment, the underlace lubricated bearing using the cylindrical roller as the rolling element has been described. However, the rolling element may be a spherical cone and a headed cone including a cylindrical body. That is, the under-lace lubricated bearing may be any of a ball bearing, a roller bearing, and a tapered roller bearing.

It is a principal part perspective view of the holder | retainer in the under-lace lubrication bearing which concerns on embodiment of this invention. It is sectional drawing in the axial direction center part of the holder | retainer. It is sectional drawing of the conventional under race lubricated bearing. It is AA sectional drawing in FIG.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 1 ... Inner ring, 2 ... Outer ring, 3 ... Cylindrical roller (as rolling element), 4 ... Retainer, 6, 7 ... Annular wall, 8 ... Pocket, 10, 11 ... Cavity part (inside retainer), 12 , 13 ... Oil supply hole, 20 ... Groove, 20a ... Position of the outer ring side end of the groove, 20b ... Position of the inner ring side end of the groove.

Claims (3)

  Two annular slopes that have a cage that rotatably holds rolling elements in a plurality of pockets, and that extend from the outer ring side toward the outer side of the bearing at both ends in the axial direction. A wall is formed, and an oil supply hole is formed in the inner ring so that lubricating oil is supplied to two hollow portions formed by both the annular inclined walls, both end faces of the plurality of rolling elements, and the inner ring. In the race lubricated bearing, an under-lace lubricated bearing is characterized in that a plurality of concave grooves extending from the inner ring side to the outer ring side are formed on each of the hollow portion side surfaces of the annular inclined walls.   Each of the plurality of grooves is inclined with respect to the circumferential direction of the cavity side surface of the annular inclined wall, and the position of the outer ring side end of the groove is relative to the position of the inner ring side end of the cage. 2. The under-lace lubricated bearing according to claim 1, wherein the bearing is inclined so as to be positioned in the counter-rotating direction.   The under-lace lubricated bearing according to claim 1, wherein each of the plurality of concave grooves is formed in a curved shape that curves so as to be convex toward the outer ring side.

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