JP2007127199A - Retainer for rolling bearing and rolling bearing - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a rolling bearing hardly causing deformation and heat generation even if it is used under a high speed rotation condition, having stable rotation performance and achieving long life and low noise. <P>SOLUTION: The retainer 4 for the rolling bearing having a symmetric shape in an axial direction is installed in the rolling bearing, for example, a deep groove ball bearing. The retainer 4 comprises two integrated annular members 10, 10 made of resin; and annular reinforcement members 11, 11 integrally molded with the annular members 10, 10 made of resin respectively. Namely, the two annular members 10, 10 made of resin having recessed surfaces 4a forming a part of a pocket are integrally fixed by a rivet 12 while opposing/abutting the recessed surfaces 4a so as to form the pocket. Further, the annular reinforcement members 11, 11 are mounted on the annular members 10, 10 made of resin by integral molding so as to cover an axial end surface of the retainer and a part of an outer diameter surface. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a cage incorporated in a rolling bearing. The present invention also relates to a rolling bearing in which the cage is incorporated.

In recent years, there has been an increasing demand for rolling bearings for high speed rotation, light weight, low noise, and the like. However, in a conventional general rolling bearing, deformation or heat generation due to high-speed rotation occurs, and thus there is a case where the request for high-speed rotation cannot be sufficiently met.
For example, a rolling element guide type resin crown-shaped cage is often used for deep groove ball bearings. The crown-shaped cage is composed of an opening made of one holding a ball and an annular portion provided with the one, and has an asymmetric shape in the axial direction. Therefore, during high-speed rotation with a dmN value exceeding 800,000, the centrifugal force due to the cage rotation (rolling element revolution) acts on the two, and the torsional deformation (elastic deformation or plasticity) radially outward with the annular part as the axis Deformation) occurs (see FIG. 6). As a result, there is a possibility that abnormal heat generation occurs due to the cage being in local contact with balls or other parts. Further, when the high speed rotation becomes severe, damage such as breakage of the cage may occur.

Further, in the conventional cage, since the concave surface forming the pocket is a spherical shape, the edge of the pocket rotates while being in local contact with the ball due to the deformation of the cage as described above. As a result, the rotational torque increases and the bearing temperature rises abruptly, eventually leading to damage to the bearing.
Furthermore, if the cage is significantly deformed, the cage may break at the bottom of the pocket where the cage comes into contact with the raceway or stress concentration is likely to occur.

As a countermeasure for these problems, there is a method of adding a reinforcing material such as glass fiber to the resin constituting the crown-shaped cage (see Patent Document 1). There is also a method using a cage having a symmetrical shape in the axial direction as described in Patent Document 2. That is, this cage is a cage formed by abutting two annular members so as to sandwich the rolling elements from both sides in the axial direction and integrating them with rivets.
JP 2000-161365 A No. 1-3848

However, the cage described in Patent Document 2 has a problem in that it may be deformed by centrifugal force during high-speed rotation, and the radially outer portion of the butted surfaces of the two annular members may open.
SUMMARY OF THE INVENTION Accordingly, an object of the present invention is to solve the problems of the prior art as described above, and to provide a rolling bearing cage that is less likely to be deformed or heated even when used under high-speed rotation conditions. Another object of the present invention is to provide a rolling bearing that has a stable rotational performance and a long life and low noise.

  In order to solve the above problems, the present invention has the following configuration. That is, the rolling bearing cage of claim 1 according to the present invention is a rolling bearing cage having a symmetrical shape in the axial direction, and has a concave surface that forms a part of a pocket that is an accommodating portion of a rolling element. The two resin annular members are fixed to each other with the concave surfaces facing each other so that the pockets are formed, and at least a part of the axial end surface and at least a part of the outer diameter surface are covered with a substantially cross-section L A character-shaped annular reinforcing member is attached.

  Since such a rolling bearing retainer has a symmetrical shape in the axial direction, it is unlikely to be deformed outward in the radial direction due to centrifugal force even when used under high-speed rotation conditions. And since it is reinforced with the annular reinforcing member, the rigidity of the resin cage is enhanced, and deformation in the radially outward direction due to centrifugal force during high-speed rotation is less likely to occur. Furthermore, since the outer diameter surface is covered with the annular reinforcing member, the resin annular member is suppressed from expanding radially outward due to heat and centrifugal force generated during high-speed rotation. As a result, when incorporated in a rolling bearing, stable rotation performance is realized even when the rolling bearing is used under high-speed rotation conditions.

According to a second aspect of the present invention, there is provided a rolling bearing cage according to the first aspect of the present invention, wherein the rolling bearing cage is a bearing ring guide type cage having the concave surface as a cylindrical surface, and the annular bearing cage. The outer diameter surface of the reinforcing member forms a cage guide surface.
Since the concave surface is a cylindrical surface, the guide method of the rolling bearing retainer can be a raceway guide method. Further, since at least a part of the outer diameter surface of the rolling bearing retainer is covered with the annular reinforcing member, the outer diameter surface of the rolling bearing retainer (that is, the outer diameter surface of the annular reinforcing member) is guided to the cage. It can be a surface.

Since the guide method of the rolling bearing retainer is the raceway guide method, the amount of movement of the retainer is suppressed, and the rotation unevenness and noise of the retainer during high-speed rotation are suppressed. Moreover, since the cage guide surface is covered with the annular reinforcing member, wear of the cage guide surface is suppressed. The cylindrical surface is a surface whose axial direction is parallel to the radial direction of the cage.
Furthermore, the rolling bearing retainer according to claim 3 of the present invention is the rolling bearing retainer according to claim 1 or 2, wherein the two resin annular members are formed by rivets penetrating both end surfaces in the axial direction. Are fixed together.

Furthermore, the rolling bearing according to claim 4 of the present invention includes an inner ring, an outer ring, a plurality of rolling elements that are arranged to freely roll between the inner ring and the outer ring, and the inner ring and the outer ring between the inner ring and the outer ring. A rolling bearing comprising a cage that holds rolling elements, wherein the cage is the rolling bearing cage according to any one of claims 1 to 3.
Since the rolling bearing of the present invention incorporates the cage as described above, it has a stable rotational performance, a long life, and a low noise.

  The rolling bearing cage of the present invention is less likely to be deformed or heated even when used under high-speed rotation conditions. In addition, the rolling bearing of the present invention has a stable rotation performance, a long life and low noise.

DESCRIPTION OF EMBODIMENTS Embodiments of a rolling bearing cage and a rolling bearing according to the present invention will be described with reference to the drawings.
The deep groove ball bearing shown in FIG. 1 includes an inner ring 1, an outer ring 2, a plurality of rolling elements (balls) 3 that are arranged so as to roll freely between the inner ring 1 and the outer ring 2, and a plurality of rolling elements between the inner ring 1 and the outer ring 2. And a retainer 4 for retaining the rolling elements 3.
The cage 4 includes two integrated resin annular members 10 and 10 and annular reinforcing members 11 and 11 having a substantially L-shaped cross section integrally formed with the resin annular members 10 and 10, respectively. The deep groove ball bearing has a symmetrical shape with respect to the axial direction (see FIGS. 1 and 2).

  In the resin annular member 10, a portion having a concave surface 4 a that forms a part of a pocket that is a housing portion of the rolling element 3 and a portion corresponding to a column are alternately arranged in the circumferential direction. Since the guide method of the cage 4 is the raceway guide method, the shape of the concave surface 4 a is a cylindrical surface whose axial direction is parallel to the radial direction of the cage 4. The two resin annular members 10 and 10 are butted with the concave surface 4a facing each other so that a pocket is formed (that is, butted so as to sandwich the rolling element 3 from both sides in the axial direction). The retainer 4 is configured by being fixed to.

The method of fixing the resin annular member 10 is not particularly limited, but caulking and fixing with rivets is preferable. That is, it is preferable to provide a hole penetrating the both axial end surfaces of the retainer 4 in a portion corresponding to the above-described pillar, and insert the rivet 12 into the hole to fix the resin annular members 10 and 10 together.
Further, annular reinforcing members 11 and 11 are attached to the resin annular members 10 and 10 by integral molding so as to cover the axial end surface of the cage 4 and a part of the outer diameter surface. As can be seen from FIG. 1, a hole is provided in a portion of the annular reinforcing member 11 that covers the axial end surface of the cage 4, and the rivet 12 passes therethrough. And the part (outer diameter surface of the annular reinforcement member 11) which covers a part of outer diameter surface of the retainer 4 among the annular reinforcement members 11 has comprised the retainer guide surface.

  Such a retainer 4 has a shape symmetrical in the axial direction and is reinforced by the annular reinforcing member 11 to enhance rigidity. Therefore, the retainer 4 is radially outward due to centrifugal force even when used under high-speed rotation conditions. The deformation of is difficult to occur. Therefore, unlike the crown-shaped cage, twisting deformation outward in the radial direction does not occur. Further, the radially outer portions of the butted surfaces of the two resin annular members 10, 10 are hardly opened. In addition, although the convex part 20 which protrudes to a radial inside is provided in the internal diameter surface of the holder | retainer 4, it is suppressed by this convex part 20 also that the radial direction outer part of the said abutting surface opens.

Furthermore, since the outer diameter surface of the cage 4 is covered with the annular reinforcing member 11, the resin annular member 10 is prevented from expanding radially outward due to centrifugal force and heat generation during high-speed rotation. Furthermore, since the axial end surface of the cage 4 is covered with the annular reinforcing member 11, it is possible to prevent the resin annular member 10 from being affected by the rivet 12 during caulking.
Furthermore, since the cage 4 is a raceway guide system, the amount of movement of the cage 4 is suppressed, and the rotation unevenness and noise of the cage 4 during high-speed rotation are suppressed. In this embodiment, the outer ring guide type retainer is illustrated, but an inner ring guide type retainer may be used. Moreover, it can also be set as the rolling element guide type holder | retainer by making the shape of the concave surface 4a into a spherical surface.

For these reasons, this deep groove ball bearing has stable rotation performance, long life, and low noise even when used under high-speed rotation conditions.
The material of the resin-made annular member 10 is not particularly limited. However, the resin-made annular member 10 can be made of an injection molding material such as polyamide resin (eg, polyamide 46, polyamide 66), polyphenylene sulfide (eg, L-PPS), or polyether ether ketone. Performance engineering plastics are preferred. Moreover, by adding 10-50 mass% fibrous filler (for example, glass fiber, carbon fiber) to such resin, the rigidity of the cage can be improved and the dimensional accuracy can be improved.

The material of the annular reinforcing member 11 is preferably a metal such as SPCC. However, the resin composition is not limited to metal as long as heat resistance and rigidity are sufficient, and a resin composition containing a fibrous filler (for example, glass fiber or carbon fiber) can also be used. When such a resin composition is used, the cage 4 can be further reduced in weight.
Furthermore, as shown in FIG. 3, you may provide the recessed part 21 in the outer-diameter surface (The outer-diameter surface of the part corresponded to the above-mentioned pillar) of the holder | retainer 4. As shown in FIG. With such a configuration, the raceway surface of the outer ring 2 is smoothly lubricated, and the cage 4 is reduced in weight, so that the outward deformation in the radial direction during high-speed rotation is further suppressed.

Further, the annular reinforcing member 11 is preferably integrally formed with the resin annular member 10 as shown in FIG. 1, but the annular reinforcing member 11 cannot be integrally formed with the resin annular member 10 due to dimensional reasons or the like. In this case, a separate object may be fixed with rivets 12 as shown in FIG.
Furthermore, if the shape of the outer diameter surface of the cage 4 is a curved surface as shown in FIG. 5, the contact form between the inner peripheral surface of the outer ring 2 and the outer diameter surface of the cage 4 is changed from surface contact to line contact. This can improve the life of the bearing.

  Furthermore, in the present embodiment, the deep groove ball bearing is shown and described as an example of the rolling bearing, but the type of the rolling bearing is not limited to the deep groove ball bearing, and the present invention is applicable to various types of rolling bearings. Can be applied. For example, radial rolling bearings such as angular contact ball bearings, self-aligning ball bearings, self-aligning roller bearings, cylindrical roller bearings, tapered roller bearings, needle roller bearings, and thrust types such as thrust ball bearings and thrust roller bearings This is a rolling bearing.

It is a fragmentary longitudinal cross-section explaining the structure of the deep groove ball bearing which is one Embodiment of the rolling bearing which concerns on this invention. It is sectional drawing of the holder | retainer integrated in the deep groove ball bearing of FIG. It is a fragmentary longitudinal cross-sectional view which shows the modification of this embodiment. It is a fragmentary longitudinal cross-section which shows another modification of this embodiment. It is a fragmentary longitudinal cross-section which shows another modification of this embodiment. It is a fragmentary longitudinal cross-section which shows the twist deformation | transformation of the holder | retainer by centrifugal force which arises in the conventional deep groove ball bearing with which the crown-shaped holder | retainer was integrated.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Inner ring 2 Outer ring 3 Rolling element 4 Cage 4a Concave surface 10 Resin annular member 11 Annular reinforcement member 12 Rivet

Claims (4)

  A cage for a rolling bearing having a symmetrical shape in the axial direction, wherein two resin annular members having a concave surface forming a part of a pocket which is a housing for a rolling element are formed so that the pocket is formed. A rolling bearing characterized by mounting a ring-shaped reinforcing member having a substantially L-shaped cross section that covers and fixes at least a part of the end face in the axial direction and at least a part of the outer diameter surface while facing and fixing the concave surfaces facing each other Cage.   The rolling bearing retainer according to claim 1, wherein the retainer is a raceway guide type retainer having a cylindrical surface as the concave surface, and an outer diameter surface of the annular reinforcing member forms a retainer guide surface.   The rolling bearing retainer according to claim 1 or 2, wherein the two resin annular members are integrally fixed by rivets penetrating through both end faces in the axial direction.   In a rolling bearing comprising an inner ring, an outer ring, a plurality of rolling elements that are arranged to freely roll between the inner ring and the outer ring, and a cage that holds the rolling element between the inner ring and the outer ring. A rolling bearing characterized in that the cage is the cage for a rolling bearing according to any one of claims 1 to 3.

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