JP2005351439A - Air oil lubrication structure of cylindrical roller bearing - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an air oil lubrication structure of a cylindrical roller bearing capable of securely transmitting lubricating oil adhered to a slope part to a cylindrical roller even if an inner ring is provided with a collar and has a cylindrical face to perform stable air oil lubrication. <P>SOLUTION: The inner ring 2 of the cylindrical roller bearing 1 is provided with the collar and becomes a rotation side ring. The slope part 2bb whose diameter is gradually reduced from a cylindrical face part 2ba adjacent to a raceway surface 2a on an outside diameter face of a collar part 2b of the inner ring 2 to a width face side is provided, and a nozzle member 6 provided along a clearance δ is provided in this slope part 2bb. A discharge port 8a for air oil opened by facing the slope part 2bb is provided in this nozzle member 6. An inside diameter face part 5b between a width face on a nozzle member 6 side of a holder 5 and a pocket 5a is a face having difference in radius so that a fringe part on a pocket 5a side has larger diameter than that of a fringe part on a width face side. An intersection part 2c where the slope part 2bb of the inner ring 2 and a cylindrical face part 2ba cross mutually is positioned in width of the inside diameter face part 5b having difference in radius of the holder 5. Preferably, a circumferential channel 14 is provided in the inside diameter face part 5b of the holder 5. In this case, the intersection part 2c is positioned in width of the circumferential channel 14. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to an air-oil lubrication structure for a cylindrical roller bearing used for supporting high-speed rotation of a main shaft or the like of a machine tool.

  The main spindle of machine tools tends to increase in speed in order to increase machining efficiency. For this reason, the lubrication of the bearing is also increasing in the amount of air oil lubrication in which lubricating oil is mixed with the carrier air and sprayed directly onto the inner ring rolling surface. However, in order to spray air oil directly on the inner ring rolling surface, it is necessary to overcome the wind pressure generated by the revolution of the rolling element and allow the lubricating oil to reach the raceway surface. Need to increase speed. For this reason, energy consumption increases due to an increase in the amount of air, and noise due to repeated interruption and penetration of the air flow caused by the revolution of the rolling element, that is, wind noise, is generated.

  An air-oil lubrication structure having a configuration shown in FIG. 9 has been proposed as a solution to eliminate the energy consumption and noise in such direct-spray type air-oil lubrication (for example, Patent Document 1). In the air-oil lubrication structure of the figure, a nozzle member 66 is provided on the outer diameter surface of the inner ring 62 of the cylindrical roller bearing 61 with a slope portion 62b following the raceway surface 62a of the inner ring 62, and along the slope portion 62b with a gap δ. And a circumferential groove 67 is provided on the slope portion 62b. The nozzle member 66 is provided with an air oil discharge hole 68 that opens to face the slope portion 62b.

  In the case of the air-oil lubrication structure shown in FIG. 2, air oil, which is lubricating oil mixed with the carrier air, is discharged from the discharge hole 68 of the nozzle member 66 to the circumferential groove 67 of the inner ring 62, and the inclined surface 62b of the inner ring 62 and the nozzle member From the gap δ between 66, it is guided to the inside of the bearing by the negative pressure suction action generated during the bearing operation. Further, it is guided to the raceway surface 62a inside the bearing or the inner diameter surface of the cage 65 by the surface tension of the lubricating oil adhering to the inclined surface portion 62b and the component force of the centrifugal force toward the larger diameter side of the inclined surface portion 62b. In this case, because of the circumferential groove 67 provided in the inner ring 62, an effect of spreading the air oil discharged from the discharge hole 68 over the entire circumference is obtained. For this reason, even if the discharge amount of air oil is small and the air is not uniformly discharged on the circumference, there is no oil stagnation due to the centrifugal force acting on the inner ring slope portion 62b. Lubricating oil can be supplied into the bearing.

As described above, by providing the slope portion 62b and the circumferential groove 67, it is possible to stably supply lubricating oil to the raceway surface 62a without blowing air oil directly to the raceway surface 62a, and to reduce noise caused by wind noise. It becomes possible to reduce and to reduce the amount of conveyance air. Further, it is possible to prevent the bearing temperature from fluctuating due to oil retention in a small amount of air.
JP 2002-54643 A

  In the conventional air-oil lubrication structure applied to the cylindrical roller bearing shown in FIG. 9, since the inner ring 62 of the bearing 61 is hooked, the inclined surface portion 62b of the inner ring 62 is in contact with the raceway surface 62a on the outer diameter surface of the flange of the inner ring 62. It extends from the adjacent cylindrical surface portion to the width surface side. Therefore, the slope portion 62b is not directly connected to the cylindrical roller 64, and has an inflection point at the intersection of the slope portion 62b and the cylindrical surface portion, and the lubricating oil is separated from the inner ring 62 by centrifugal force at the inflection point. It is done. The separated lubricating oil may adhere to the inner diameter surface of the retainer 65 and be transmitted to the cylindrical roller 65. However, the inner diameter surface of the retainer 65 has a slope portion whose diameter increases on the outer side in the axial direction. There is a greater possibility that oil will be driven out of the cage 65.

  An object of the present invention is to provide a cylindrical roller bearing capable of performing stable air-oil lubrication even when the inner ring has a cylindrical surface with a flange and the lubricating oil adhering to the inclined surface of the inner ring is reliably transmitted to the cylindrical roller. It is to provide an air-oil lubrication structure.

The air-oil lubrication structure of the cylindrical roller bearing of the present invention has a ring-shaped cage in which a plurality of cylindrical rollers are interposed between the inner ring and the outer ring, and the plurality of cylindrical rollers are held in each pocket, The inner ring is a rotating side wheel with a flange, and an inclined surface portion having a gradually smaller diameter is provided from the cylindrical surface portion adjacent to the raceway surface on the outer diameter surface of the flange portion of the inner ring toward the width surface side, and a gap is formed in the inclined surface portion. The present invention is applied to an air oil lubrication structure of a cylindrical roller bearing in which a nozzle member is provided and an air oil discharge port is formed in the nozzle member so as to face the slope portion.
In this premise configuration, the inner diameter surface portion between the width surface on the nozzle member side of the cage and the pocket has a radius difference so that the edge on the pocket side has a larger diameter than the edge on the width surface side. The intersection portion where the inclined surface portion and the cylindrical surface portion of the inner ring intersect is positioned within the width of the inner diameter surface portion of the cage having the radius difference.

  According to this configuration, the lubricating oil discharged as air oil from the discharge port of the nozzle member is guided from the inner ring slope portion to the inner ring cylindrical surface portion and flows into the bearing. In this case, even if the lubricating oil stays at the intersection where the inner ring slope changes to the inner ring cylindrical surface part and scatters to the outer diameter side due to centrifugal force, it remains within the width surface of the inner diameter surface portion between the width surface of the cage and the pocket. Since the intersection portion is located, the lubricating oil scattered from the inner ring surface at the intersection portion is received and attached to the inner diameter surface portion of the cage. Since the inner diameter surface portion of the cage is a surface having a radius difference so that the edge on the pocket side has a larger diameter than the edge on the width surface side, the lubricating oil adhering to the inner diameter surface portion of the cage is It will flow into the pocket, ensuring adhesion to the cylindrical rollers. Therefore, stable rotation of the bearing can be obtained.

In this invention, a circumferential groove is provided in an inner diameter surface portion between the width surface on the nozzle member side of the cage and the pocket, and the inclined surface portion and the cylinder of the inner ring are within the width of the circumferential groove. You may position the intersection part which a part intersects.
When the circumferential groove is provided, the lubricating oil that has been separated from the inner ring surface and scattered on the outer diameter side at the intersection of the inner ring is received by the circumferential groove, and the rate at which the lubricating oil is received by the cage increases. Further, the received lubricating oil can be distributed over the entire circumference of the inner diameter surface portion through the circumferential groove, and the lubricating oil can be evenly supplied to each cylindrical roller.

In the present invention, a plurality of all-around grooves may be provided on the inner diameter surface of the cage, the grooves being partially formed by the circumferential grooves and surrounding the entire circumference of each pocket.
When the all-around groove surrounding the pocket is provided, the lubricating oil scattered from the retainer and received by the circumferential groove reaches the entire circumference of the pocket through the all-around groove. Therefore, the lubricating oil can be poured into the cylindrical roller from all directions, and the lubricating oil can be supplied uniformly and smoothly to each part of the cylindrical roller.

In this invention, the inner diameter surface portion between the width surface and the pocket on the nozzle member side of the cage extends from the edge of the cylindrical surface portion to the pocket side edge from the cylindrical surface portion located on the width surface side. The side may be a tapered surface having a large diameter.
Even if there is a cylindrical surface portion adjacent to the width surface of the cage, if there is a tapered surface on the pocket side, and there is an intersection portion of the inner ring on this tapered surface, the lubricating oil separated at the intersection portion from the inner ring is removed from the tapered surface. Can be received and poured into the pocket. In addition, if there is a cylindrical surface portion adjacent to the width surface of the cage, a large space is obtained between the vicinity of the width surface of the cage and the outer surface of the inner ring, and the nozzle member must be inserted deep into the cage pocket. Becomes easy.

The air-oil lubrication structure of the cylindrical roller bearing according to the present invention is provided with a slope portion that gradually decreases in diameter from the cylindrical surface portion adjacent to the raceway surface on the outer diameter surface of the flange portion of the inner ring toward the width surface side, and follows this slope portion with a gap. In an air-oil lubrication structure in which a nozzle member is provided and an air-oil discharge port is provided in the nozzle member so as to face the slope portion, the inner diameter surface between the width surface on the nozzle member side of the cage and the pocket The portion is a surface having a radius difference so that the edge on the pocket side has a larger diameter than the edge on the width surface side, and an intersection point where the inclined surface portion and the cylindrical surface portion of the inner ring intersect with each other is Because it is positioned within the width of the inner diameter surface portion having the radius difference, even if the inner ring has a flange and a cylindrical surface portion, the lubricating oil adhering to the inclined surface of the inner ring is reliably transmitted to the cylindrical roller, and stable air oil Lubricate It is possible.
When a circumferential groove is provided in the inner diameter surface portion of the cage, and the intersection portion of the inner ring is positioned within the width of the circumferential groove, the lubricating oil separated at the intersection portion from the inner ring surface is It can be received by the circumferential groove and can be more reliably supplied to the cylindrical roller.

  A first embodiment of the present invention will be described with reference to FIGS. The cylindrical roller bearing 1 has a plurality of cylindrical rollers 4 interposed between raceway surfaces 2a and 3a of an inner ring 2 which is a rotating side wheel and an outer ring 3 which is a fixed side ring. Each cylindrical roller 4 is held in each pocket 5 a provided at a plurality of locations in the circumferential direction of the ring-shaped cage 5. The inner ring 2 has flange portions 2b on both sides, and the outer ring 3 has no flanges.

A slope portion 2bb following the raceway surface 2a is provided on the outer diameter surface of the flange portion 2b of the inner ring 2, and a nozzle member 6 is provided along the slope portion 2ba with a gap δ. The inclined surface portion 2bb extends from the cylindrical surface portion 2ba adjacent to the raceway surface 2a on the outer diameter surface of the flange portion 2b of the inner ring 2 to gradually decrease in diameter toward the width surface side. In this embodiment, the slope 2bb has a portion that is adjacent to the cylindrical surface 2ba a steeper surface than other portions. A circumferential groove side wall surface 2bc having a slope that is steeper than the slope portion 2bb is provided on the outer ring surface side of the inner ring 2 with respect to the slope portion 2bb. A circumferential groove 7 having a V-shaped cross section is formed by the circumferential groove side wall surface 2bc and the chamfered portion 11a on the outer diameter side of the inner ring spacer 11 adjacent to the inner ring 2. The circumferential groove 7 extends in the circumferential direction and is formed in an annular shape.
In this embodiment, the cross-sectional shape of the inner ring 2 is bilaterally symmetrical, and the cylindrical surface portion 2ba is also formed on the outer diameter surface of the flange portion 2b opposite to the nozzle member 6 side with the raceway surface 2a interposed therebetween. , A slope portion 2bb and a circumferential groove side wall surface 2bc are provided.

  As shown in an enlarged view in FIG. 2, the cage 5 has an inner diameter surface portion 5b between the width surface on the nozzle member 6 side and the pocket 5a, and the edge on the pocket 5a side has a larger diameter than the edge on the width surface side. The surface has a radius difference. The inner diameter surface portion 5b having this radius difference is provided between the cylindrical surface portion 5ba adjacent to the pocket 5a, the width surface adjacent peripheral surface portion 5bb adjacent to the cage width surface, and the cylindrical surface portion 5ba and the width surface adjacent peripheral surface portion 5bb. It is constituted by the inner surface of the circumferential groove 14. The pocket-side cylindrical surface portion 5ba has a larger diameter than the width surface adjacent peripheral surface portion 5bb, thereby giving the radius difference. The width surface adjacent peripheral surface portion 5bb may be a cylindrical surface or an inclined surface or a curved surface having a large diameter on the width surface side or the pocket side. In the illustrated example, the width surface adjacent peripheral surface portion 5bb is a cylindrical surface, and the edge on the width surface side is a surface that becomes a chamfered portion. The circumferential groove 14 is a groove having a V-shaped cross section.

  The intersection 2c where the inclined surface 2bb and the cylindrical surface 2ba of the inner ring 2 intersect is located within the groove width of the circumferential groove 14, and therefore is located within the width of the inner diameter surface portion 5b having the radius difference. doing.

  In this embodiment, the cross-sectional shape of the cage 5 is also bilaterally symmetric, and the circumferential groove 14 is also provided in the inner diameter surface portion 5b opposite to the nozzle member 6 side across the pocket 5a. . Further, an axial groove 15 extending in the axial direction and connected to the left and right circumferential grooves 14 is provided on the inner diameter surface of the column portion 5c between the adjacent pockets 5a and 5a of the cage 5. The left and right circumferential grooves 14 and the axial grooves 15 constitute a plurality of all-around grooves 16 surrounding the entire periphery of each pocket 5a.

  The tip 6 a of the nozzle member 6 is positioned between the inner diameter surface of the cage 5 and the outer diameter surface of the inner ring 2. The nozzle member 6 is a ring-shaped member, and is provided adjacent to the cylindrical roller bearing 1 in the axial direction, and has an annular flange 6a extending in the axial direction from the inner diameter portion of the side surface. The flange-shaped portion 6 a has an inner diameter surface formed on an inclined surface having the same angle as that of the inclined surface portion 2 bb of the inner ring 2, extends to a position directly below the cage 5, and the tip thereof becomes the tip portion 6 aa of the nozzle member 6. The clearance δ between the flange 6a of the nozzle member 6 and the inclined surface 2bb of the inner ring 2 is in consideration of the fitting between the inner ring 2 and the shaft and the temperature rise of the inner ring 2 and expansion due to centrifugal force. It is set to a dimension as small as possible (for example, a range of 0.15 to 0.65 mm) as long as it does not touch the surface.

  The nozzle member 6 is provided with a discharge hole 8 facing the slope portion 2bb and having a discharge port 8a opened. Specifically, the discharge port 8 a faces the vicinity of the circumferential groove 7. The discharge holes 8 are provided at one place or a plurality of places in the circumferential direction of the nozzle member 6. The discharge hole 8 directs the discharge direction of the discharge port 8a toward the circumferential groove 7 so that the discharged air oil can be directly blown onto the circumferential groove 7, and the discharge direction is a predetermined inclination angle with respect to the bearing axis. Is provided to have.

  The nozzle member 6 is attached to a housing 9 to which the outer ring 3 of the cylindrical roller bearing 1 is attached. The nozzle member 6 may be attached to the housing 9 through the outer ring spacer 10 or directly. The example of FIG. 1 is an example attached through an outer ring spacer 10, and a nozzle member 6 is provided in a fitted state in an annular notch recess 10 a formed in the inner diameter part of one side surface of the outer ring spacer 10. . The inner diameter surface outside the bearing of the nozzle member 6 is close enough not to contact the inner ring spacer 11.

  In the discharge hole 8 of the nozzle member 6, the vicinity 8b of the discharge port 8a is formed as a narrowed hole having a smaller diameter than the general part. The inlet of the discharge hole 8 communicates with an air oil supply path 13 provided from the housing 9 to the nozzle member 6. The air oil supply path 13 has an air oil supply port (not shown) in the housing 9 and a housing portion outlet 13 b on the inner surface of the housing 9. The housing portion outlet 13b communicates with an annular communication groove 13c provided on the outer diameter surface of the outer ring spacer 10, and each discharge of the nozzle member 6 is performed from the communication groove 13c through an individual path 13d that penetrates in the radial direction. It communicates with the hole 8. The air oil supply port of the air oil supply path 13 is connected to an air oil supply source (not shown) in which lubricating oil is mixed with compressed carrier air.

The operation of the air oil lubrication structure having the above configuration will be described. The air oil supplied to the air oil supply path 13 is injected to the side wall surface 2bc of the circumferential groove 7 on the outer diameter surface of the boundary between the inner ring 2 and the inner ring spacer 11 through the discharge hole 8 of the nozzle member 6. The air oil injected to the side wall surface 2bc of the circumferential groove 7 contributes to the lubrication of the cylindrical roller bearing 1 in the following form.
(1) The lubricating oil adhering to the side wall surface 2bc of the circumferential groove 7 is guided from the inner ring slope portion 2bb to the inner ring cylindrical surface portion 2ba by the surface tension and the component force to the large diameter side caused by the centrifugal force, and is bearing. 1 flows into the interior.

(2) Even if the lubricating oil stays at the intersection 2c changing from the inner ring slope part 2bb to the inner ring cylindrical surface part 2ba and scatters to the outer diameter side by centrifugal force, the width surface and the pocket 5a on the nozzle member 6 side of the cage 5 Since the intersection portion 2b is located within the width surface of the inner diameter surface portion 5b between them, the lubricating oil scattered from the inner ring 2 adheres to the inner diameter surface portion 5b of the cage 5. Further, the inner circumferential surface portion 5b is provided with a circumferential groove 14, and the intersection portion 2b is located within the groove width of the circumferential groove 14, so that the lubricating oil scattered at the intersection portion 2b It is received in the groove 14 and escapes to the outside of the cage width are avoided.
The inner diameter surface portion 5b of the cage 5 has a radius difference so that the edge on the pocket 5a side has a larger diameter than the edge on the width surface side. The centrifugal force generated by the rotation of the cage 5 flows toward the pocket 5a and is reliably supplied to the cylindrical roller 4.

(3) Further, the lubricating oil received in the circumferential groove 14 can flow through the circumferential groove 14 and spread over the entire circumference, so that the lubricating oil can be evenly supplied to each cylindrical roller 4.
Further, the inner diameter surface portion 5b of the cage 5 is provided with a plurality of all-around grooves 16 partially formed by the circumferential grooves 14 and surrounding the entire circumference of each pocket 5a. Lubricating oil can be poured into the cylindrical roller 4 from any direction via the peripheral groove 16.

  (5) Even when the supply air becomes small and the flow becomes nonuniform on the circumferential groove 7, the negative generated in the gap δ between the inner ring inclined surface portion 2 bb and the annular flange portion 6 a of the nozzle member 6. Air oil flows into the bearing due to the pressure suction action and centrifugal force.

  Thus, according to the air oil lubrication structure of the above configuration, even if the inner ring 2 has the flange portion 2b and the cylindrical surface portion 2ba, the lubricating oil adhering to the inclined surface portion 2bb is reliably transmitted to the cylindrical roller 4, Stable air-oil lubrication can be performed. Further, since air oil is supplied into the bearing without directly injecting air oil onto the raceway surface 2a of the inner ring 2, noise due to wind noise can be reduced.

In addition, the axial groove 15 provided on the inner diameter surface of the column portion 5c in the cage 5 is formed from an intermediate portion of the axial groove 15 as shown in the cross-sectional views and the rear view in FIGS. Further, branch grooves 17 branching toward the cylindrical roller retaining claw 18 protruding from the outer diameter side may be added to the edges of the pocket 5a facing in the circumferential direction.
When this branch groove 17 is added, the lubricating oil adhering to the inner diameter surface portion 5b of the cage 5 can be made to flow toward the cylindrical roller retaining claw 18. Since the lubricating oil adhering to the outer periphery of the cylindrical roller 4 may be scraped off by the cylindrical roller retaining claw 18, the lubricating oil is supplied to this portion from the branch groove 17. Insufficient lubrication is resolved.

  Moreover, in each said embodiment, although the circumferential groove 14 was provided in a part of the width direction of the said internal surface part 5b of the holder | retainer 5, without providing this circumferential groove 14, for example as shown in FIG. The entire inner diameter surface portion 5b may be a tapered surface. The inner diameter surface portion 5b may be formed in an arcuate cross section as shown in FIG.

  Further, as shown in FIG. 7, the inner diameter surface portion 5b includes a cylindrical surface portion 5bc located on the width surface side, and a tapered surface 5bd extending from the edge of the cylindrical surface portion 5bc to the edge portion on the pocket side and having a large diameter on the pocket side. It is good also as a surface. Thus, even if there is a cylindrical surface portion 5bc adjacent to the width surface of the cage 5, if there is a tapered surface 5bd on the pocket side and the intersection portion 2c of the inner ring 2 is on the tapered surface 5bd, the surface of the inner ring 2 The lubricating oil separated at the intersection 2c can be received by the tapered surface 5bd and poured into the pocket 5a. Further, if there is a cylindrical surface 5bc adjacent to the width surface of the cage 5, a large space is obtained between the vicinity of the width surface of the cage 5 and the outer diameter surface of the inner ring 2, and the nozzle member 6 is connected to the pocket 5 a of the cage 5. It becomes easy to insert to a deep position to the side.

  In the above-described embodiments, the slope portion 2bb of the inner ring 2 has a portion that is adjacent to the cylindrical surface portion 2ba that is steeper than the other portions. The slope portion 2bb is shown in FIG. Thus, the entire surface may be a substantially uniform tapered surface. Moreover, you may provide the circumferential groove 7 formed between the inner ring | wheel 2 and the inner ring | wheel spacer 11 in each said embodiment in the middle of the slope part 2bb, as shown to FIG. 8 (B).

It is sectional drawing which shows the air oil lubrication structure of the cylindrical roller bearing concerning one Embodiment of this invention. It is a principal part expanded sectional view of the air oil lubrication structure. (A) is a fragmentary sectional view of the retainer in the air oil lubrication structure, and (B) is a back view of the retainer. (A) is a fragmentary sectional view which shows the other example of the holder | retainer, (B) is a back view of the holder | retainer. It is a partial expanded sectional view of the air oil lubrication structure concerning other embodiments of this invention. It is a partial expanded sectional view of the air oil lubrication structure concerning other embodiment of this invention. It is a partial expanded sectional view of the air oil lubrication structure concerning other embodiment of this invention. (A), (B) is an expanded sectional view of the slope part of the inner ring in the air oil lubrication structure concerning further another embodiment of this invention, respectively. It is sectional drawing of a prior art example.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 ... Cylindrical roller bearing 2 ... Inner ring | wheel 2a ... Raceway surface 2b ... Collar surface 2ba ... Cylindrical surface part 2bb ... Slope part 2c ... Intersection part 4 ... Outer ring 4 ... Cylindrical roller 5 ... Cage 5a ... Pocket 5b ... Inner diameter surface part 5ba ... Cylindrical Surface portion 5bb ... Width surface adjacent peripheral surface portion 6 ... Nozzle member 8a ... Discharge port 14 ... Circumferential groove 16 ... All-around groove δ ... Clearance

Claims (4)

A plurality of cylindrical rollers are interposed between the inner ring and the outer ring, and a ring-shaped cage that holds the plurality of cylindrical rollers in each pocket is provided. There is an inclined surface portion that gradually decreases in diameter from the cylindrical surface portion adjacent to the raceway surface on the outer diameter surface of the flange portion of the inner ring to the width surface side, and a nozzle member is provided along the inclined surface portion with a gap. In the air-oil lubrication structure of the cylindrical roller bearing provided with the air-oil discharge port that opens facing the slope portion,
An inner diameter surface portion between the width surface on the nozzle member side of the cage and the pocket is a surface having a radius difference so that an edge portion on the pocket side has a larger diameter than an edge portion on the width surface side, and the inner ring An air oil lubrication structure for a cylindrical roller bearing, wherein an intersection portion where the inclined surface portion and the cylindrical surface portion of the retainer are located within a width of an inner diameter surface portion of the cage having the radius difference.   In Claim 1, a circumferential groove is provided in an inner diameter surface portion between the width surface on the nozzle member side of the cage and the pocket, and the inclined surface portion of the inner ring is disposed within the width of the circumferential groove. An air-oil lubrication structure for a cylindrical roller bearing in which an intersection where the cylinder intersects is located.   The air oil for a cylindrical roller bearing according to claim 1 or 2, wherein a plurality of circumferential grooves are provided on the inner diameter surface of the cage by the circumferential grooves and surrounding the entire circumference of each pocket. Lubrication structure.   2. The inner diameter surface portion between the width surface on the nozzle member side of the cage and the pocket according to claim 1 extends from the cylindrical surface portion positioned on the width surface side to the edge portion on the pocket side from the edge of the cylindrical surface portion. Air-oil lubrication structure for cylindrical roller bearings with a tapered surface with a large diameter on the pocket side.

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