JP5315905B2 - Cylindrical roller bearing - Google Patents

Description

  The present invention relates to a cylindrical roller bearing in which a plurality of cylindrical rollers are arranged so as to roll on a cage provided between an inner ring and an outer ring.

The cylindrical roller bearing is configured such that a plurality of cylindrical rollers can roll between a raceway surface formed at a substantially central portion of the outer peripheral surface of the inner ring and a raceway surface formed at a substantially central portion of the inner peripheral surface of the outer ring. Yes.
The cylindrical rollers are held at predetermined intervals along the circumferential direction by a cage provided between the outer ring and the inner ring. Specifically, the cage has a plurality of pockets formed by a pair of annular portions arranged opposite to each other in the axial direction and a column portion extending and connecting the pair of annular portions in the axial direction. Each cylindrical roller is held in the pocket at a predetermined interval along the circumferential direction.
As the cylindrical roller bearing, guide portions that can be slidably contacted with both axial end portions of the inner peripheral surface of the outer ring are provided on the outer peripheral side of each annular portion, and the guide portion is the inner peripheral surface of the outer ring during rotation of the bearing. A device that guides the rotation of the cage by sliding contact with is known (for example, see Patent Document 1).

JP-A-11-159535

However, since the cylindrical roller bearing device is in a state in which the cylindrical roller is sandwiched between the guide portions, the lubricant such as oil supplied onto the raceway surface of the outer ring by oil air or the like moves outward in the axial direction of the cage. This is regulated by the guide section. For this reason, there is a problem that the lubricant easily stays on the raceway surface, and the staying lubricant becomes a rolling resistance of the cylindrical roller and the bearing torque is likely to increase.
In order to prevent the lubricant from staying, it is conceivable that the outer shape of the guide portion is reduced to form a gap between the guide portion and the raceway surface, and the lubricant is allowed to escape from the gap. However, in this case, a new problem arises that the cage is likely to be eccentric due to the existence of the gap and the rotation cannot be guided well.
The present invention has been made in view of such circumstances, and can satisfactorily guide the rotation of the cage, and the bearing torque increases due to the retention of the lubricant on the raceway surface. It is an object of the present invention to provide a cylindrical roller bearing capable of preventing the above.

In order to achieve the above object, a cylindrical roller bearing of the present invention includes an inner ring having a raceway surface on an outer peripheral surface, an outer ring having a raceway surface on an inner peripheral surface, and a raceway surface of the inner ring and a raceway surface of the outer ring. A plurality of cylindrical rollers arranged so as to be able to roll, a pair of annular parts arranged apart from each other in the axial direction, and arranged at equal intervals along the circumferential direction of the annular parts to connect the annular parts to each other The cylindrical rollers are disposed in a pocket surrounded by the adjacent column portions and the pair of annular portions, thereby holding the cylindrical rollers at predetermined intervals along the circumferential direction. a retainer, the cylindrical roller bearing wherein the retainer is provided to protrude on the raceway surface of the front Kigairin the outer peripheral surface of the pillar portion, the rotation of the cage in sliding contact with the said raceways Guide for removing excess lubricant on the raceway surface Comprising a piece, the inner peripheral surface of the pillar portion, a pair of tapered surfaces are formed gradually diverging toward the axially substantially central portion, the axially substantially central portion which is the intersection of the two tapered surfaces , penetrated toward the distal end of the guide piece is characterized in that through-holes for supplying lubricant to the raceway surface from the inner peripheral surface side of the pillar portion.

According to the cylindrical roller bearing configured as described above, since the guide piece is brought into sliding contact with the raceway surface of the outer ring, the rotation of the cage can be guided well. In addition, surplus lubricant on the raceway surface can be removed by the guide piece as the cage rotates. And since the said guide piece is provided for every predetermined interval along the circumferential direction of a holder | retainer, an excess lubricant can be escaped to the axial direction both ends of an outer ring | wheel. For this reason, it is possible to prevent the bearing torque from increasing due to the excessive lubricant remaining on the raceway surface.
Furthermore, since the lubricant can be supplied to the raceway surface from the inner peripheral surface side of the cage through the through hole, the condition that the supply of the lubricant tends to be insufficient by removing the excess lubricant on the raceway surface Even underneath, the lubricant can be supplied onto the raceway surface, and insufficient supply of the lubricant can be prevented.

A second tapered surface is formed at both axial ends of the guide piece so as to incline from the pillar side toward the substantially axial center of the portion in sliding contact with the raceway surface of the guide piece. It is preferable that the total axial length of the portion in sliding contact with the track is shorter than the total axial length of the raceway surface. In this case, even if the guide piece is biased to one side in the axial direction with respect to the raceway surface while the cylindrical roller bearing is rotating, the region where the guide piece does not slide on the other side of the raceway surface, that is, the lubricant is not removed. Since the region always exists, it is possible to appropriately leave the lubricant on the raceway surface. For this reason, it is possible to avoid occurrence of insufficient supply of lubricant even under conditions where supply of lubricant is likely to be insufficient by removing excess lubricant over the entire axial length of the track surface, and the raceway surface. The lubricant remaining on at least one side in the axial direction of the roller spreads on the raceway surface due to surface tension, etc., so that an appropriate amount of lubricant is supplied to the rolling surface of the raceway surface on which the cylindrical roller rolls. can do.

In addition, a second tapered surface is formed on both ends of the guide piece in the axial direction. The second tapered surface is inclined from the pillar side toward the substantially axial center of the portion in sliding contact with the raceway surface of the guide piece. The total axial length of the portion that is in sliding contact with the raceway surface is preferably shorter than the total axial length of the cylindrical roller. In this case, a region where the lubricant is not removed always exists on at least one side in the axial direction of the rolling surface of the raceway surface on which the cylindrical roller rolls during rotation of the cylindrical roller bearing. The lubricant can be left moderately on the running surface. For this reason, it is possible to avoid the occurrence of insufficient supply of lubricant even under conditions where supply of lubricant is likely to be insufficient by removing excess lubricant over the entire axial length of the rolling surface, An appropriate amount of lubricant can be supplied to the rolling surface by the cylindrical roller extending the lubricant remaining on at least one side in the axial direction of the rolling surface by rolling.

Further, the guide piece is in line contact with the raceway surface, and a pair of side surfaces extending in the axial direction of the guide piece has a substantially central portion in a circumferential direction of a portion in sliding contact with the raceway surface of the guide piece from the pillar side. It is preferable that the 1st taper surface which inclines toward a part is formed . In this case, since the sliding contact resistance of the guide piece can be reduced, the bearing torque can be reduced as compared with the conventional cylindrical roller bearing in which the guide portion of the cage is in surface contact.
Moreover, it is preferable to have the hollow which accumulate | stores the lubricant on the said track surface in the front-end | tip part of the said guide piece. In this case, since the lubricant can be temporarily stored in the recess, the lubricant in the recess can be supplied even under conditions where the supply of the lubricant is likely to be insufficient, and the supply of lubricant is insufficient. Can be more effectively prevented.

  According to the cylindrical roller bearing of the present invention, it is possible to prevent the bearing torque from increasing due to the excess lubricant remaining on the raceway surface while guiding the rotation of the cage satisfactorily by the guide piece. . Further, since the lubricant can be supplied from the inner peripheral surface side of the cage to the raceway surface through the through hole, the condition that the supply of the lubricant is likely to be insufficient by removing the excess lubricant on the raceway surface Even underneath, the lubricant can be supplied onto the raceway surface, and insufficient supply of the lubricant can be prevented.

Next, preferred embodiments of the present invention will be described with reference to the accompanying drawings. FIG. 1 is a sectional view showing a cylindrical roller bearing of an inner ring flange type according to the first embodiment of the present invention.
In FIG. 1, a cylindrical roller bearing 1 includes an inner ring 2 fixed to a rotating shaft (not shown), an outer ring 3 fixed to a housing (not shown), and a plurality of rollers arranged between the inner ring 2 and the outer ring 3 so as to be able to roll. Cylindrical rollers 4 and cages 5 for holding the cylindrical rollers 4 at equal intervals along the circumferential direction.

The inner ring 2 forms a raceway surface 2a on which the cylindrical roller 4 rolls at the axially central portion of the outer peripheral surface, and flanges 2b projecting to the outer ring 3 side are formed on both sides of the raceway surface 2a in the axial direction. It is integrally formed.
The outer ring 3 forms a raceway surface 3a on which the cylindrical roller 4 rolls in the axial center portion of the inner peripheral surface, and tapered surfaces that gradually increase in diameter toward the outside in the axial direction at both end portions in the axial direction of the raceway surface 3a. 3b is formed.
Oil air P as a lubricant is supplied from an inner peripheral surface of the cage 5 and an outer peripheral surface of the inner ring 2 by an injection nozzle (not shown). The oil air P supplied to the inside of the cylindrical roller bearing 1 contains oil particles, and the oil particles adhere to the inside of the cylindrical roller bearing 1, particularly the inner peripheral surface of the cage 5, the outer peripheral surface of the cylindrical roller 4 and the inner ring 2. To do. The adhered oil particles become agglomerated oil O, and this oil O is the rolling contact surface of the raceway surface 2a of the cylindrical roller 4 and the inner ring 2, the raceway surface 3a of the cylindrical roller 4 and the outer ring 3, the cylindrical roller 4 and the flange 2b. Or it moves to the sliding contact surface of the cylindrical roller 4 and the cage | basket 5, and lubricates these rolling contact surfaces and sliding contact surfaces.

  FIG. 2 is a perspective view showing a part of the cage 5. The cage 5 is made of PEEK (polyetheretherketone) resin, and a pair of annular portions 5a that are spaced apart in the axial direction, and at equal intervals along the circumferential direction of the annular portion 5a. In a pocket 5c that is provided with a plurality of pillars 5b that are arranged to connect the annular parts 5a and a guide piece 6 that guides the rotation of the cage 5, and is surrounded by the adjacent pillars 5b and the pair of annular parts 5a In addition, each cylindrical roller 4 is disposed, and the cylindrical rollers 4 are held at predetermined intervals along the circumferential direction.

The guide piece 6 is formed on the outer peripheral surface of all the pillar portions 5b so as to protrude toward the raceway surface 3a of the outer ring 3, and a sliding contact portion 6a that is slidably contacted with the raceway surface 3a is provided at a tip portion thereof. The sliding contact portion 6a is formed in a flat shape, and the corner portion in the circumferential direction is in line contact with the track surface 3a formed in an arc shape over the entire length in the axial direction.
In addition, the guide piece 6 is formed with a first tapered surface 6b inclined on the pair of side surfaces extending in the axial direction from the column portion 5b side toward the substantially central portion in the circumferential direction of the sliding contact portion 6a (see FIG. 3). ).

  Further, as shown in FIG. 1, the guide piece 6 is formed so that the axial total length L1 of the base end portion thereof is the same as the axial total length L3 of the raceway surface 3a of the outer ring 3 and both axial end portions. A second tapered surface 6c is formed so as to incline from the column portion 5b side toward the approximate center in the axial direction of the sliding contact portion 6a. As a result, the axial total length L2 of the sliding contact portion 6a, which is the tip of the guide piece 6, is formed shorter than the total axial length L3 of the raceway surface 3a, and is less than or equal to the total axial length L3 of the raceway surface 3a (this embodiment). Is the same as the axial length L4 of the cylindrical roller 4 in the same manner as the axial length L3 of the raceway surface 3a).

  A pair of tapered surfaces 5d that gradually increase in diameter toward the substantially central portion in the axial direction are formed on the inner peripheral surface of each column portion 5b, and at the substantially central portion in the axial direction that is the intersection of both tapered surfaces 5d. Is formed with a through hole 7 penetrating toward a substantially central portion in the axial direction of the sliding contact portion 6a.

  With the above configuration, since the sliding contact portion 6a of the guide piece 6 is in sliding contact with the raceway surface 3a during the rotation of the cylindrical roller bearing 1, the rotation of the cage 5 can be well guided. Further, as the cage 5 rotates in the direction of the arrow X in FIG. 3 with respect to the raceway surface 3a, the excess oil Ob (shaded portion in FIG. 3) of the oil O on the raceway surface 3a is slidably contacted. 6a can be scraped off and removed, and excess oil Ob can be released to both ends of the outer ring 3 in the axial direction. For this reason, it is possible to prevent the excess oil Ob from staying on the raceway surface 3a while leaving an appropriate amount of oil Oa (the non-hatched portion in FIG. 3) with a thin and uniform thickness on the entire raceway surface 3a. Therefore, it is possible to prevent the bearing torque from increasing due to the surplus oil Ob remaining on the raceway surface 3a.

  Further, the oil O supplied by oil-air lubrication from between the inner peripheral surface of the column portion 5b and the inner peripheral surface of the inner ring 2 is caused by centrifugal force accompanying rotation of the cage 5 along the tapered surface 5d. Is guided to the substantially central portion in the axial direction of the inner peripheral surface, and flows into the inside from the lower portion of the through hole 7 (see arrow A in FIG. 1). Further, the oil O flows radially outward in the through hole 7 by the centrifugal force, and is supplied to the raceway surface 3a of the outer ring 3 from the sliding contact portion 6a at the upper end portion of the through hole 7 (see arrow B in FIG. 1). ). For this reason, it is possible to avoid a shortage of supply of the oil O even under conditions where the supply of the oil O tends to be short by removing the excess oil Ob over the entire axial length of the raceway surface 3a.

  Furthermore, since the axial total length L2 of the sliding contact portion 6a is shorter than the axial total length L3 of the raceway surface 3a, the sliding contact portion 6a is axially oriented with respect to the raceway surface 3a during the rotation of the cylindrical roller bearing 1. Even if it is biased to either side, there is always a region (L3-L2, L4-L2) where the sliding contact portion 6a does not slide, that is, a region where oil O is not removed, on the other side of the raceway surface 3a. Become. Therefore, an appropriate amount of oil Oa can remain on the raceway surface 3a, and the supply of oil O is likely to be insufficient by removing excess oil Ob over the entire axial length of the raceway surface 3a. However, it is possible to avoid the shortage of oil O supply. Further, the oil O remaining on at least one side in the axial direction of the raceway surface 3a spreads on the raceway surface 3a due to surface tension or the like, so that the rolling surface in the raceway surface 3a on which the cylindrical roller 4 rolls, An appropriate amount of oil O can be supplied.

Moreover, since the axial total length L2 of the sliding contact part 6a is formed shorter than the axial total length L4 of the cylindrical roller 4, of the raceway surface 3a on which the cylindrical roller 4 rolls while the cylindrical roller bearing 1 rotates. Since there is always a region where the oil O is not removed on at least one side in the axial direction of the rolling surface, an appropriate amount of oil Oa can remain on the rolling surface 3a. For this reason, it is possible to avoid insufficient supply of the appropriate amount of oil Oa even under conditions where supply of the appropriate amount of oil Oa is likely to be insufficient by removing excess oil Ob over the entire axial length of the rolling surface. At the same time, the cylindrical roller 4 stretches the oil O remaining on at least one side in the axial direction of the rolling surface, so that an appropriate amount of oil O can be supplied to the rolling surface.
Further, since the entire axial length of the sliding contact portion 6a is in line contact with the raceway surface 3a, the sliding contact resistance of the sliding contact portion 6a can be reduced, and the conventional cylindrical roller in which the guide portion of the cage is in surface contact. The bearing torque can be reduced compared to the bearing.

4 and 5 show a cylindrical roller bearing 1 according to the second embodiment. 4 is a perspective view of a main part showing the cage 5, and FIG. 5 is a cross-sectional view taken along the line BB of FIG.
4 and 5, the second embodiment is different from the first embodiment in that a recess 6 d for temporarily storing oil O is provided in the sliding contact portion 6 a of the guide piece 6. The recesses 6 d are formed at two locations on both sides in the axial direction with respect to the through hole 7.
According to the present embodiment, the oil O stored in the recess 6d can be supplied to the raceway surface 3a even under a condition where the supply of the appropriate amount of oil Oa is likely to be insufficient during the rotation of the cylindrical roller bearing 1. Further, it is possible to prevent a shortage of supply of an appropriate amount of oil Oa.

Although the present invention has the above is not limited to the embodiments, for example, in each of the above embodiments it is sliding a draft in the piece 6 to the outer ring raceway surface 3a of the inner ring flanged type cylindrical roller bearing 1 It is also possible to make the outer ring raceway contact with the outer ring raceway surface of the cylindrical roller bearing with the outer ring collar. In the above embodiments, the sliding contact portion 6a of the guide piece 6 is brought into line contact with the track surface 3a, but it is also possible to make surface contact.

Further, in each of the above-described embodiments, the guide piece 6 has the guide piece 6 in order to make the axial total length L2 of the sliding contact portion 6a shorter than the axial total length L3 of the raceway surface 3a and the axial total length L4 of the cylindrical roller 4. 6 are tapered surfaces (second tapered surface 6c), but the axial total length L1 of the base end of the guide piece 6 is shorter than the axial total length L3 of the track surface 3a. It may be a vertical plane.
Moreover, in each said embodiment, although the axial direction full length L2 of the sliding contact part 6a of the guide piece 6 was formed shorter than the axial direction full length L3 of the track surface 3a and the axial direction full length L4 of the cylindrical roller 4, for example, When the lubrication conditions are not severe, the axial total length L2 of the sliding contact portion 6a of the guide piece 6 is not less than the axial total length L3 of the raceway surface 3a and / or the axial total length L4 of the cylindrical roller 4. May be.
Moreover, in each said embodiment, although the guide piece 6 is formed in all the pillar parts 5b of the holder | retainer 5, it is also possible to form only in the one part pillar part 5b. In short, the guide pieces 6 may be formed at predetermined intervals in the circumferential direction of the cage 5, preferably at equal intervals.
In each of the above embodiments, the oil O as the lubricant is supplied by the oil air P. However, the oil O may be supplied by other means such as oil mist.

It is sectional drawing which shows the cylindrical roller bearing which concerns on the 1st Embodiment of this invention. It is a principal part perspective view which shows the holder | retainer in the said cylindrical roller bearing. It is AA sectional drawing of FIG. It is a principal part perspective view which shows the holder | retainer in the cylindrical roller bearing which concerns on the 2nd Embodiment of this invention. It is BB sectional drawing of FIG.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Cylindrical roller bearing 2 Inner ring 2a Raceway surface 3 Outer ring 3a Raceway surface 4 Cylindrical roller 5 Cage 6 Guide piece 6d Depression 7 Through-hole O Oil (lubricant)
Ob surplus oil (surplus lubricant)

Claims (5)

An inner ring having a raceway surface on the outer peripheral surface;
An outer ring having a raceway surface on the inner peripheral surface;
A plurality of cylindrical rollers arranged to roll between the raceway surface of the inner ring and the raceway surface of the outer ring;
The adjacent pillars having a pair of annular parts spaced apart in the axial direction and a plurality of pillar parts arranged at equal intervals along the circumferential direction of the annular part to connect the annular parts to each other In a cylindrical roller bearing comprising a cage that holds the cylindrical roller at a predetermined interval along the circumferential direction by disposing the cylindrical roller in a pocket surrounded by a part and a pair of the annular parts ,
Said retainer is provided to protrude on the raceway surface of the front Kigairin the outer peripheral surface of the pillar portion, in sliding contact with the said raceways with guiding the rotation of the cage, surplus lubricating on the raceway surface A guide piece for removing the agent,
A pair of tapered surfaces that gradually increase in diameter toward the substantially central portion in the axial direction are formed on the inner peripheral surface of the column portion,
A substantially central portion in the axial direction, which is an intersection of both the tapered surfaces, is penetrated toward the tip of the guide piece , and is used to supply lubricant from the inner peripheral surface side of the column portion to the raceway surface. A cylindrical roller bearing, wherein a hole is formed. Second tapered surfaces are formed on both ends of the guide piece in the axial direction so as to be inclined from the column side toward the substantially axial center of the portion in sliding contact with the raceway surface of the guide piece.
The cylindrical roller bearing according to claim 1, wherein an axial total length of a portion of the guide piece in sliding contact with the raceway surface is shorter than an axial total length of the raceway surface. Second tapered surfaces are formed on both ends of the guide piece in the axial direction so as to be inclined from the column side toward the substantially axial center of the portion in sliding contact with the raceway surface of the guide piece.
It said track surface and axial length of the sliding contact portion, a cylindrical roller bearing according to a short claim 1 than the axial length of the cylindrical rollers of the guide piece. The guide piece is in line contact with the raceway surface ;
A pair of side surfaces extending in the axial direction of the guide piece is formed with a first tapered surface that is inclined from the column portion side toward a substantially central portion in a circumferential direction of a portion that is in sliding contact with the raceway surface of the guide piece. Item 4. The cylindrical roller bearing according to Items 1 to 3.   The cylindrical roller bearing according to any one of claims 1 to 4, further comprising a recess for storing a lubricant on the raceway surface at a tip portion of the guide piece.

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