JP2009103282A - Roller bearing - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To make seizing difficult when running out of an oil film between a roller end face and a flange. <P>SOLUTION: An undercutting part 11 is formed on a flange 10 sequentially from the side edge 13 of a raceway face 12 of a bearing ring 1 to the recessed grinding relief and a sliding member 15 is firmly fixed in the whirl stopping condition by injection moulding a sliding member 15 to its undercutting part 11. Its sliding member 15 contacts a roller end face 21 prior to a flange 10, and the rolling end face 21 and the sliding member 15 are solely contacting in the condition of no skew or the like by producing the elastic compression deformation until when the rolling end face 21 contacts the flange 10 according to the suppress strength received from this rolling end face 21, so that the rolling end face 21 may come in sliding contacts with both the sliding member 15 and the flange 10 when the skew or the like occurs. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a roller bearing having a flanged ring.

  The collar ring with a collar is formed by integrally forming a collar protruding from the raceway surface on both sides or one side of the raceway surface, and radially and axially from the side edge of the raceway surface between the raceway surface and the collar. Has a recessed grinding relief. The roller rolling on the raceway surface is guided by sliding contact between the roller end surface and the collar. For this reason, lubrication between the end surfaces of the collars is achieved. In general machinery, especially bearings used in places where the amount of lubricating oil is limited, and bearings that require performance so that seizure does not occur immediately even if the lubrication device fails, an oil film is formed between the roller end face and the collar. By making it difficult to cut, a device for improving seizure resistance has been devised.

As shown in FIG. 4 which shows an axial cross section in the vicinity of the collar of the conventional example, by forming a wedge space in which the guide clearance between the roller end surface 41 and the collar 42 increases toward the roller center axis side, the roller end surface 41 and the collar 42 are formed. It is widely practiced to make it easy for oil to enter between them.
Further, the roughness of the sliding contact surface 43 of the roller end surface 41 and the collar 42 is improved, the intersection P1 between the roller end surface 41 and the chamfered portion 44, and the intersection P2 of the sliding contact surface 43 of the collar 42 and the grinding clearance 45. The seizure resistance is improved by adjusting the positional relationship (see Patent Document 1 and Patent Document 2).

Japanese Patent Laid-Open No. 2002-181053 (abstract, paragraphs 0002 and 0003) JP 2006-90516 A

  However, in the conventional example as described above, although an oil film can be easily formed between the roller end face and the collar, there is a limit to the amount of lubricating oil supplied, an abnormality occurs in the lubricating oil supply, If the axial load applied to the roller is large and the rollers are skewed, the oil film may be cut, and there is a risk of seizing between the roller end face and the collar at an early stage.

  Accordingly, an object of the present invention is to make it difficult for seizure to occur when an oil film break occurs between the roller end face and the collar.

In order to solve the above-described problems, the present invention provides a roller bearing having a race ring integrally formed with a collar, wherein the collar includes a portion of a thin portion facing the axial direction on the end face of the roller in the radial direction and a circumference around the center axis of the bearing. It is formed over the entire circumference of the direction, and a sliding member is fixed to the shank, and the collar and the sliding member are formed as a sliding surface with the roller end surface.
Specifically, if a brim portion facing the axial direction is formed on the end surface of the roller in a radial direction partially over the entire circumference in the circumferential direction around the bearing central axis, and a sliding member is fixed to the bristle portion. The roller end surface and the collar can be guided over the entire circumference, and the sliding member is interposed between the roller end surface and the raceway ring while avoiding an increase in the guide clearance, and the collar and the sliding member are inserted into the roller end surface. It can be set as the sliding surface which carries out sliding contact.
If the roller end surface is in sliding contact with the collar partly in the radial direction and over the entire circumference, the roller can be guided firmly with the collar. At the same time, if the roller end surface is in sliding contact with the sliding member, even if an oil film breakage occurs between the roller end surface and the collar, the contact surface pressure between the roller end surface and the collar is prevented from increasing, and the sliding member Sliding contact is obtained. As the sliding contact of the sliding member is obtained, seizure between the roller end face and the collar is less likely to occur.
Therefore, according to the present invention, even when an oil film breakage occurs between the roller end surface and the collar, seizure between the roller end surface and the collar can be made difficult to occur.

  The sliding member can be fixed to the shading portion by injection molding, coating, adhesion, or the like of a resin such as polyimide, fluororesin, or polyamide. Of course, the frictional resistance of the sliding member is smaller than the collar.

Preferably, the sliding member is fixed so as to come into contact with the roller end surface before the collar, and the sliding member is moved until the roller end surface comes into contact with the collar according to the pressing force received from the roller end surface. It is preferable to adopt a configuration that can cause elastic compression deformation.
The sliding member has a lower rigidity than the collar that is a part of the race, but is fixed so as to come into contact with the roller end surface before the collar. For this reason, there is no sliding contact between the roller end face and the collar while the roller is guided only by the sliding member, and even if an oil film breakage occurs between the roller end face and the collar, seizure may occur between the roller end face and the collar. There is no.
If there is no sliding contact between the roller end face and the collar, the generation of wear powder inside the bearing is suppressed, so there is no wear powder between the roller end face and the collar without increasing the amount of lubricating oil supplied. As a result, the lubrication conditions are less likely to deteriorate, and these seizures are less likely to occur.
Even if the roller is skewed or an axial load is applied to the roller, the sliding member can be elastically compressed and deformed until the roller end surface comes into contact with the collar according to the pressing force received from the roller end surface. . Even if it becomes impossible to guide the roller only by the sliding member, the sliding member is elastically compressed and deformed, so that sliding contact with the roller end surface is obtained. At the same time, since the roller end face is in sliding contact with the collar, the roller is firmly guided. At this time, even if an oil film breakage occurs between the roller end surface and the collar, the roller end surface is in sliding contact with the collar and the sliding member, and thus is difficult to seize as described above.
When the skew of the roller disappears, the sliding member recovers elastically, so that the roller end surface and the sliding member are again brought into the sliding contact state.
Therefore, according to the present invention, it is possible to make it difficult to cause seizure when an oil film breakage occurs between the roller end face and the collar without increasing the supply amount of the lubricating oil.

  In addition, one or both of the inner and outer rings of the roller bearing is a raceway with a collar, and the roller skew is suppressed by receiving the roller from both sides in the axial direction with one or both collars of the inner and outer rings. . If the sliding member is fixed to both collars for receiving the roller from both sides in the axial direction, seizure when the roller is skewed can be prevented.

The present invention can be applied to a raceway with a flange of a cylindrical roller bearing, a tapered roller bearing, or a self-aligning roller bearing.
In particular, the cylindrical roller bearing has a configuration in which one of the inner and outer rings is a race ring with both collars, the other is a race ring with one collar or a race ring without collar, and the roller is a cylindrical roller. It is employed under operating conditions where no load is applied or where the axial load is relatively small. Cylindrical roller bearings premised on such usage conditions are easy to set to operating conditions in which the roller end face is in sliding contact with only the sliding member, and is particularly suitable for the present invention.

The thinning portion can be formed in series with a radial relief of the collar, an intermediate portion in the radial direction, or a grinding relief recessed from a side edge of the raceway surface of the raceway.
In particular, if the slack portion is formed in series with the grinding relief and is fixed so as to create a space between the roller end face and the roller chamfer connecting the rolling surface, the sliding member is elastically deformed. At this time, deformation can be released to the portion forming the space, and the sliding member is likely to be deformed following the roller end surface, so that the sliding contact between the roller end surface and the sliding member can be further ensured.

Since the sliding member is in sliding contact with the roller end face, it receives a rotational force in the circumferential direction around the bearing center axis as the roller revolves.
Here, if a recess having a partially increased depth is formed on the inner surface of the slidable part, the sliding member can be fixed to the slidable part by injection molding or coating. Also, a part of the sliding member can be formed.
If the inner surface of the dent and the sliding member are engaged in the circumferential direction, the sliding member is prevented from rotating by the engagement, so that the sliding contact between the roller end surface and the sliding member can be obtained more stably. be able to.

  As described above, according to the present invention, in the collar, a thin portion facing the roller end surface in the axial direction is formed in a part in the radial direction over the entire circumference in the circumferential direction around the bearing central axis, and a sliding member is formed on the thin portion. By adopting a structure in which the collar and the sliding member are made to be a sliding surface with the roller end surface, seizure can be made difficult to occur when an oil film breakage occurs between the roller end surface and the collar. .

Hereinafter, embodiments of the present invention will be described with reference to FIGS.
FIG. 1 shows only half the axial cross section of the roller bearing according to the embodiment. FIG. 2 shows a perspective view of the outer appearance of the bearing ring 1 of FIG.
As shown in FIG. 1 and FIG. 2, the roller bearing according to the embodiment is configured as a cylindrical roller bearing in which one of the inner and outer rings is a race ring 1 integrally formed with both collars 10 and 10, and the roller 2 is a cylindrical roller. Has been.

  FIG. 3 (a) shows an enlarged view of the vicinity of the collar 10 of the race 1 of FIG. As shown in FIGS. 1 and 3 (a), a wedge-spaced guide clearance is set between the roller end surfaces 21 of the collar 10 and 2 of the bearing ring 1 so as to approach the roller central axis as viewed in the axial section. Has been. This is to make it easier for the lubricating oil to enter between the two roller end faces 21 at the collar 10. If there is no such purpose, it is possible to provide a guide clearance in which the gap between the end faces 21 at the collar 10 is parallel. is there.

In the collar 10, a thin portion 11 facing the roller end surface 21 in the axial direction is formed partly in the radial direction and over the entire circumference in the circumferential direction around the bearing central axis.
The relief portion 11 is formed by a series of grinding reliefs recessed in the radial direction and the axial direction from the side edges 13 and 13 of the raceway surface 12 of the raceway 1.

  As shown in FIG. 2 and FIG. 3A, recesses 14 whose depths are partially increased in the radial direction and the axial direction are formed in a plurality of locations in the circumferential direction.

  A sliding member 15 is fixed to the thinning portion 11 by injection molding. The sliding member 15 is fixed so as to be positioned closer to the roller end face 21 than the collar 10 in the axial direction. For this reason, the sliding member 15 can contact the roller end surface 21 in the axial direction before the collar 10.

  The sliding member 15 formed by synthetic resin injection molding has lower rigidity than the collar 10 which is a part of the metal race 1. Therefore, as a result of the roller 2 shown in FIG. 1 being skewed or the roller 2 being subjected to an axial load, the sliding member 15 that contacts the roller end surface 21 before the collar 10 is shown in FIG. As shown, it is compressed according to the pressing force received from the roller end face 21.

  While the roller 2 shown in FIG. 1 is guided only by the sliding member 15, there is no sliding contact between the roller end face 21 and the collar 10, as shown in FIG. Even if an oil film breakage occurs between the roller end face 21 and the collar 10 in this state, there is no fear of seizure between the roller end face 21 and the collar 10, and generation of wear powder inside the bearing is suppressed. For this reason, even if the supply amount of the lubricating oil is not increased, it is difficult for wear powder to intervene between the roller end face 21 and the collar 10 to deteriorate the lubrication conditions, and these seizures are difficult to occur.

  As shown in FIG. 3B, the synthetic resin forming the sliding member 15 can be elastically compressed and deformed until the roller end surface 21 contacts the collar 10 in accordance with the pressing force received from the roller end surface 21. Has been. Even if the roller 2 cannot be guided only by the sliding member 15 due to the skew of the roller 2 or the axial load shown in FIG. 1, the sliding member 15 is elastically deformed. For this reason, as shown in FIG.3 (b), the sliding contact of the roller end surface 21 and the sliding member 15 is obtained. At the same time, the roller end face 21 is also in sliding contact with the collar 10, so that the roller 2 shown in FIG. 1 is firmly guided. At this time, even if an oil film breakage occurs between the roller end surface 21 and the collar 10, the collar 10 and the sliding member 15 function as sliding surfaces that are in sliding contact with the roller end surface 21. For this reason, the contact surface pressure between the roller end surface 21 and the collar 10 is prevented from increasing, and sliding contact between the roller end surface 21 and the sliding member 15 is obtained. Since sliding contact with the sliding member 15 is obtained, seizure between the roller end face 21 and the collar 10 is less likely to occur.

When the skew or the like disappears, the sliding member 15 recovers elastically, so that the state returns to the state of FIG. 3A where only the roller end surface 21 and the sliding member 15 are in sliding contact.
Therefore, the roller bearing according to this embodiment can hardly cause seizure when an oil film breakage occurs between the roller end face 21 and the collar 10 without increasing the supply amount of the lubricating oil.

  The sliding member 15 is fixed so that a space is formed between the roller end face 21 and the roller chamfer 23 that connects the rolling surfaces 22. When the sliding member 15 undergoes elastic compression deformation, the deformation can be released to the portion forming the space. For this reason, the sliding member 15 is easily deformed following the roller end surface 21, and the sliding contact between the roller end surface 21 and the sliding member 15 can be made more reliable.

  The material for forming the sliding member 15 can be appropriately selected according to the applied axial load as long as the elastic compressive deformation is obtained. Since the sliding contact between the roller end surface 21 and the collar 10 becomes easier as the rigidity of the sliding member 15 is higher, it is preferable to use a sliding material for high surface pressure. The sliding member for high surface pressure has an allowable surface pressure at room temperature of 50 [MPa] or more. For example, the product name: BEAREE FL9000 (manufactured by NTN Precision Resin Co., Ltd.) can be used for fixing to the thinned portion 11 by adhesion, and the product name: BEAREE for fixing to the thinned portion 11 by injection molding or coating. PI5001 (made by NTN Precision Resin Co., Ltd.) can be used.

  Since the sliding member 15 is injection-molded in the shank portion 11, as shown in FIGS. 2 and 3 (b), the sliding member 15 enters each recess 14 with a partially increased depth. Engage in the circumferential direction around. With the revolution of the roller 2 shown in FIG. 1, the sliding member 15 receives a circumferential rotational force around the bearing center axis, but is prevented from rotating by the engagement. For this reason, the sliding contact between the roller end surface 21 and the sliding member 15 can be obtained more stably.

It should be noted that the number, shape, etc. of the recesses 14 shown in FIG. 2 should be changed appropriately as long as the rotation stop of the sliding member 15 is obtained in a state where the roller end surface 21 is in sliding contact with both the collar 10 and the sliding member 15. Can do.
Furthermore, the stickiness of the injection-molded sliding member 15 increases as the surface roughness of the inner surface of the thinning portion 11 and the like increases. For this reason, the thinning portion 11 has a roughened inner surface by turning.

  In this embodiment, the N-type cylindrical roller bearing has been described as an example. However, in each of the NU-type, NJ-type, NF-type, NUP-type, and NH-type, the sliding member is similarly applied to the collar of each bearing ring. Can be fixed. For the purpose of preventing seizure due to skew and axial load, it is most preferable to fix the sliding members to all the collars of the roller bearing. In the case where seizure can occur extremely close to the flange on the load side as in a tapered roller bearing, the sliding member may be fixed only to the flange on the load side.

Sectional drawing which shows the whole structure of the roller bearing which concerns on embodiment The perspective view which expanded a part of inner ring of Drawing 1 1 is an operation diagram showing a state where the roller end surface of FIG. 1 is in sliding contact with only the sliding member, and b is an operation diagram showing a state where the roller end surface of FIG. 1 is in sliding contact with the sliding member and the collar. Sectional view showing a conventional example

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Race ring 2 Roller 10 Collar 11 Nuts part 12 Race surface 14 Recess 15 Sliding member 21 Roller end surface 22 Rolling surface 23 Roller chamfering

Claims (4)

  In the roller bearing having a race ring integrally formed with a collar, a thin portion facing the axial direction on the end surface of the roller in the axial direction is formed in the radial direction partially over the entire circumference in the circumferential direction around the bearing central axis. A roller bearing characterized in that a sliding member is fixed to a portion, and the collar and the sliding member are formed as a sliding surface with the roller end surface.   The sliding member is fixed so as to come into contact with the roller end face before the collar, and the sliding member is elastically compressed and deformed until the roller end face comes into contact with the collar according to the pressing force received from the roller end face. The roller bearing according to claim 1, wherein the roller bearing can be formed.   The relief portion is formed in a series of grinding reliefs recessed from the side edges of the raceway surface of the raceway so that a space is created between the roller end face and the roller chamfer that connects the rolling surface. The roller bearing according to claim 1 or 2, which is fixed.   The recess according to any one of claims 1 to 3, wherein a recess having a partially increased depth is formed on the inner surface of the shank, and the inner surface of the recess and the sliding member are engaged in the circumferential direction. The described roller bearing.

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