JP2014126052A - Cage guide member of rolling bearing, and rolling bearing - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a rolling bearing capable of suppressing generation of frictional heat between an inner peripheral face of an outer ring raceway shoulder portion and a cage.SOLUTION: A cage guide member 50 of a rolling bearing assembled in an annular space between an outer ring 30 of a rolling bearing and a cage 45, has a supporting body 51 provided with a plurality of connection supporting portions 53 arranged at prescribed intervals in the circumferential direction, and a plurality of blade plates 55 extended toward at least a rear side in the rotating direction of the cage 45 in a state of being respectively supported by the connection supporting portions 53, and kept into contact with an inner peripheral face of the outer ring 30 at the extended ends 55a. Base portions 54 of the plurality of blade plates 55 are applied as a rotation guide portion of the cage 45. A first space 100 formed between the extended end 55a of the blade plate 55 and an outer peripheral face of the cage 45 is determined to be larger than a second space 101 formed between the base portion 54 of the blade plate 55 and the outer peripheral face of the cage 45.

Description

  The present invention relates to a cage guide member and a rolling bearing of a rolling bearing that is incorporated in an annular space between an inner circumferential surface of an outer ring of a rolling bearing and an outer circumferential surface of a cage to rotate and guide the cage.

In a rolling bearing, the inner peripheral surface of at least one outer ring raceway shoulder portion of both outer ring raceway shoulders of the outer ring is used as a cage guide surface, and the cage guide surface guides the outer peripheral surface of the cage. It is known to suppress the behavior of the cage with respect to the radial direction of the bearing.
In such a rolling bearing, when the rotating shaft rotates, the cage rotates as the rolling element rolls.
At this time, since the outer circumferential surface of the cage rotates while sliding in contact with the inner circumferential surface (cage guide surface) of the outer ring raceway shoulder, the friction generated between the inner circumferential surface of the outer ring raceway shoulder and the cage. Heat may cause the cage to be at a high temperature and damage the cage.
A cage formed of a heat-resistant resin is known in order to adapt to use at a high speed under high temperature (for example, see Patent Document 1).

JP 2011-185439 A

  Since the cage is made of heat-resistant resin, even if the cage becomes hot due to frictional heat generated between the inner circumferential surface of the outer ring raceway shoulder and the cage, thermal damage to the cage is suppressed. be able to. However, when the cage is in a high temperature state, the temperature in the rolling bearing rises, and as a result, a lubricant such as grease in the rolling bearing is thermally altered, which may adversely affect the bearing performance.

  In view of the above problems, an object of the present invention is to provide a cage guide member and a rolling bearing of a rolling bearing capable of suppressing generation of frictional heat between the inner peripheral surface of the outer ring and the cage. .

In order to solve the above-mentioned problem, a cage guide member for a rolling bearing according to claim 1 of the present invention includes an inner ring, an outer ring, a plurality of rolling elements, and an inner ring of the outer ring of a rolling bearing provided with a cage. A cage guide member of a rolling bearing that is incorporated in an annular space between a circumferential surface and an outer circumferential surface of the cage and rotationally guides the cage,
A support body on which a plurality of connection support portions spaced apart from each other in the circumferential direction are disposed;
In a state of being supported by each of the plurality of connection support portions, it is disposed in an annular space between the inner peripheral surface of the outer ring and the outer peripheral surface of the cage, and is directed at least to the rear side in the rotation direction of the cage. And a plurality of blades whose extended ends are in contact with the inner peripheral surface of the outer ring,
In the state of being incorporated in the annular space, the diameter dimension of a circle passing through the base part on the connection support part side of the plurality of blades is set slightly larger than the outer diameter dimension of the cage, and each base part is As a rotation guide for the cage,
The first space formed between the extending end of the blade and the outer peripheral surface of the cage is more than the second space formed between the base of the blade and the outer peripheral surface of the cage. It is characterized by being set large.

According to the above configuration, in a state where the cage guide member is incorporated in the annular space between the inner circumferential surface of the outer ring and the outer circumferential surface of the cage, the base portions of the plurality of blades function as rotation guide portions of the cage. .
In addition, in a state where the cage guide member is incorporated in the annular space, the extended ends of the plurality of blade plates are in contact with the inner peripheral surface of the outer ring. A first space is formed between the extending end of the blade and the outer peripheral surface of the cage, and a second space smaller than the first space is formed between the base of the blade and the outer peripheral surface of the cage. Is done.
When the cage is rotated during rotation of the bearing, the air on the first space side flows toward the second space smaller than the first space. That is, the dynamic pressure is generated by the air that has lost its place when the air in the first space flows toward the second space like a wedge. This dynamic pressure acts in a direction away from each other with respect to the base portion of the blade plate constituting the first space and the outer peripheral surface of the cage.
The dynamic pressure increases as the rotation speed of the cage changes from the low speed rotation range to the high speed rotation range.
For this reason, in the high-speed rotation area of the cage, the base portion of the blade plate and the outer peripheral surface of the cage are not in contact with each other, so that heat generation due to friction between them can be suppressed.

The cage guide member of the rolling bearing according to claim 2 is the cage guide member of the rolling bearing according to claim 1,
The plurality of connection support portions of the support body extend to the front side in the rotation direction of the cage in the annular space between the inner circumferential surface of the outer ring and the outer circumferential surface of the cage, and the extension ends thereof A front blade that contacts the inner peripheral surface of the outer ring is formed.

According to the above configuration, when the cage rotates in the forward / reverse direction, when the cage rotates in the reverse direction, the front blades extend toward the rear side in the reverse direction.
Therefore, even when the cage is rotated in the reverse direction, a first space is formed between the extended end of the front blade and the outer peripheral surface of the cage, and the base of the front blade and the cage A second space smaller than the first space is formed between the outer peripheral surface.
As a result, even when the cage is rotated in the reverse direction, dynamic pressure is generated by the air flowing toward the second space, and this dynamic pressure generates the base of the blade plate and the outer circumference of the cage that constitute the second space. Acts in directions away from each other.
For this reason, in the high-speed rotation area of the cage, the base portion of the blade plate and the outer peripheral surface of the cage are not in contact with each other, so that heat generation due to friction between them can be suppressed.

The cage guide member of the rolling bearing according to claim 3 is the cage guide member of the rolling bearing according to claim 1 or 2,
The support body is provided with connection support portions on both axial sides of the plurality of blades, and has an inner diameter dimension equivalent to the diameter of a circle passing through the base portion on the connection support portion side of the plurality of blade plates. Formed into a cylindrical shape having
Between the outer peripheral surface of the axial direction edge part of a holder | retainer and the internal peripheral surface of both said support bodies, the annular space which can generate | occur | produce the dynamic pressure by the flow of air is comprised, It is characterized by the above-mentioned.

According to the above configuration, when the cage is rotated at the time of bearing rotation, the annular space between the outer peripheral surface of the axial end portion of the cage and the inner peripheral surfaces of both supports of the cage guide member has a wide portion. And a narrow part occur. Then, dynamic pressure of air is generated in a narrow part. This dynamic pressure acts in the direction away from each other with respect to the outer peripheral surfaces of both supports and the cage.
For this reason, in the high-speed rotation region of the cage, both supports are kept in a non-contact state with respect to the outer peripheral surface of the cage, so that heat generation due to friction between both the supports and the cage is suppressed. Can do.

The cage guide member of the rolling bearing according to claim 4 is the cage guide member of the rolling bearing according to any one of claims 1 to 3,
The support and the plurality of blades are integrally formed of a single thin leaf spring material.

  According to the above configuration, the number of parts and assembly man-hours can be minimized by integrally forming the support of the cage guide member and the plurality of blades with a single thin leaf spring material, thereby reducing costs. Is very effective.

  A rolling bearing according to a fifth aspect of the present invention is disposed so as to be able to roll in an inner ring disposed on the rotating shaft side, an outer ring disposed on the housing side, and an annular space between the inner ring and the outer ring. A plurality of rolling elements, a retainer that holds the plurality of rolling elements, and an annular space between an inner peripheral surface of the outer ring and an outer peripheral surface of the retainer to rotate and guide the retainer. The cage guide member according to any one of 1 to 4 is provided.

According to the above configuration, during the rotation of the bearing that rotates the rotating shaft, the dynamic pressure generated with the rotation of the cage is relative to the base portion of the blade plate that constitutes the second space and the outer peripheral surface of the cage. Acts in directions away from each other.
As the cage rotation speed changes from the low-speed rotation range to the high-speed rotation range, the above-described dynamic pressure increases. Therefore, in the high-speed rotation range of the cage, the base of the blade plate and the outer peripheral surface of the cage are not Since it will be in a contact state, the heat_generation | fever by friction between these both can be suppressed.
As a result, thermal damage (deformation, breakage, etc.) of the cage can be suppressed, and the durability of the rolling bearing can be improved.

It is an axial sectional view showing the rolling bearing according to the first embodiment of the present invention. It is an axial direction sectional view which expands and shows the principal part of a rolling bearing similarly. It is a cross-sectional view which follows the III-III line | wire of FIG. 2 which shows the state which similarly arrange | positioned the retainer guide member between the outer ring | wheel and the retainer. It is a perspective view which similarly shows a retainer guide member. It is an expanded view which similarly shows a retainer guide member. It is an expanded view which shows the other embodiment of a holder guide member. It is a perspective view which shows the holder | retainer guide member of the rolling bearing which concerns on Example 2 of this invention. It is an expanded view which similarly shows a retainer guide member. It is an axial direction sectional view which expands and shows the principal part of a rolling bearing similarly. Similarly, it is a cross-sectional view exaggeratingly showing a state in which a wide portion and a narrow portion are generated in an annular space between the inner peripheral surface of the support of the cage guide member and the outer peripheral surface of the cage.

  A mode for carrying out the present invention will be described in accordance with an embodiment.

A rolling bearing according to Embodiment 1 of the present invention will be described with reference to FIGS.
As shown in FIGS. 1 and 2, the rolling bearing (angular ball bearing in FIG. 1) includes an inner ring 20, an outer ring 30, a plurality of rolling elements 40 (balls in FIG. 1), a cage 45, and a cage. And a guide member 50.

The inner ring 20 is disposed on the outer peripheral surface of the rotary shaft 1 so as to be rotatable integrally with the rotary shaft 1.
An inner ring raceway surface 21 is formed at the axially central portion of the outer circumferential surface of the inner ring 20.
The outer ring 30 has the same center on the outer peripheral surface of the inner ring 20 with an annular space therebetween, and is disposed in a fixed state on the housing 2.
An outer ring raceway surface 31 is formed at the axially central portion of the inner peripheral surface of the outer ring 30, and one of the outer ring raceway shoulders 32, 33 on both sides of the outer ring raceway surface 31 has a counter bore 33. It is formed into a shape.
The plurality of rolling elements 40 are arranged so as to roll between the inner ring raceway surface 21 and the outer ring raceway surface 31 while being held in the respective pockets 47 of the cage 45.
On the inner peripheral surface of the outer ring raceway shoulder portion 32, an annular groove 32a that suppresses the axial movement of the cage guide member 50 described in detail below is formed.

As shown in FIG. 2, the cage guide member 50 is disposed in an annular space between the inner peripheral surface of the outer ring raceway shoulder 32 and the outer peripheral surface of the cage 45 facing the inner peripheral surface. .
The cage guide member 50 is made of a metal material or a resin material having heat resistance, oil resistance, spring property, etc., and as shown in FIGS. 3 and 4, a plurality of connection support portions 53 that are spaced apart from each other in the circumferential direction. Between the inner peripheral surface of the outer ring raceway shoulder 32 of the outer ring 30 and the outer peripheral surface of the retainer 45 in a state of being supported by the cylindrical support 51 and the plurality of connection support portions 53 respectively. A plurality of rear side members arranged in the annular space and extending toward at least the rear side in the rotation direction of the cage 45 and having an extended end 55a contacting the inner peripheral surface of the outer ring raceway shoulder 32 of the outer ring 30 And a vane plate 55.

2 and 3, in a state where the cage guide member 50 is incorporated in the annular space between the inner circumferential surface of the outer ring raceway shoulder 32 and the outer circumferential surface of the cage 45, a plurality of rear side The diameter A of the circle passing through the inner surface of the base 54 on the connection support portion 53 side of the blade 55 is set to be slightly larger than the outer diameter B of the retainer 45, and the inner surface of each base 54 is connected to the retainer 45. The rotation guide part.
Further, the first space 100 formed between the extending end 55 a of the rear blade 55 and the outer peripheral surface of the retainer 45 has a base 54 of the rear blade 55 and the outer peripheral surface of the retainer 45. It is set larger than the second space 101 formed between the two.
The cylindrical support 51 has an inner diameter that is the same as the diameter A of a circle that passes through the inner surfaces of the bases 54 of the plurality of rear blades 55.

In the first embodiment, considering that the cage 45 is switched in both forward and reverse directions, the plurality of connection support portions 53 of the support body 51 include the inner peripheral surface of the outer ring raceway shoulder portion 32 and the cage 45. A plurality of front blades 56 that extend forward in the rotational direction of the retainer 45 in the annular space between the outer peripheral surfaces and whose extended ends 56 a contact the inner peripheral surface of the outer ring raceway shoulder 32. However, the base portions 54 of the plurality of rear blades 55 are formed continuously as a common base portion 54.
In the assembled state of the cage guide member 50, the cage guide member 50 is configured such that the extended ends 55 a and 56 a of the plurality of rear blades 55 and the front blade 56 are the inner circumference of the outer ring raceway shoulder 32. The retainer guide member 50 is held on the inner peripheral surface of the outer ring raceway shoulder 32 by being fitted into the annular groove 32a of the surface and elastically contacting the groove bottom surface of the annular groove 32a. The movement in the axial direction is regulated by 32a. The annular groove 32a may be configured to fit the entire cage guide member 50 in the axial direction.
Further, in the first embodiment, as shown in FIG. 2, the axial width dimension C of the rear blade 55 and the front blade 56 of the cage guide member 50 is the inner surface of the pocket 47 of the cage 45. Is set to be appropriately larger than the thickness dimension (minimum thickness dimension) D of the axial end portion 45a from the axial end surface to the axial end face. And the extension end 55a, 56a of the rear blade 55 of the cage guide member 50 and the front blade 56 is fitted into the annular groove 32a on the inner peripheral surface of the outer ring raceway shoulder 32, and the axial direction In a state where the movement is suppressed, both end portions in the axial direction of the rear blade plate 55 and the front blade plate 56 protrude from the both ends of the axial end portion 45a of the retainer 45 by a predetermined amount.

In the first embodiment, the support body 51 of the cage guide member 50, the plurality of rear blades 55, and the plurality of front blades 56 are integrally formed of a single thin leaf spring material. .
That is, as shown in FIG. 5, the support 51 is appropriately longer than the unfolded length of the support 51, and the axial width of the support 51 and the rear blade 55 (or the front blade 56). Vertical and horizontal cuts 70 and 71 are formed by breath processing or the like on a long sheet metal (or resin) thin plate spring material 50A having a width dimension including the width dimension in the axial direction. . In this way, a support member constituting portion 51A for forming the support member 51 and blade plate constituting portions 55A and 56A for forming a plurality of rear blades 55 and front blades 56 are formed. At this time, the connection support portion 53 is formed at an intermediate portion between the blade plate constituting portions 55A and 56A. Further, slit-like cuts 72 and 73 in the axial direction are formed in the terminal coupling portions 52 at both ends of the support member constituting portion 51A.
After that, the support body constituting part 51A is rolled into a cylindrical shape, and the notches 72 and 73 of the both terminal coupling parts 52 are fitted to each other to form the support body 51. As a result, a plurality of rear blades 55 and front blades 56 having a flat base 54 and a common base 54 are formed by the blade plate components 55A and 56A (see FIG. 4).

  Further, in the first embodiment, the notches 72 and 73 are formed larger than the plate thickness dimension of the thin leaf spring material 50A (several times larger) in the terminal coupling portions 52 at both ends of the support member constituting portion 51A. Then, when the support body 51 is rounded into a cylindrical shape and the notches 72 and 73 of the both end coupling portions 52 are fitted into each other to form the support body 51, the diameter of the support body 51 is the groove width of the notches 72 and 73. Inside, it can be shrunk slightly.

The rolling bearing according to the first embodiment is configured as described above.
Therefore, as shown in FIGS. 2 and 3, in the state where the cage guide member 50 is incorporated in the annular space between the inner circumferential surface of the outer ring raceway shoulder 32 and the outer circumferential surface of the cage 45, a plurality of rear wheels are installed. A common base 54 for the side blades 55 and the front blades 56 functions as a rotation guide for the cage 45.
Further, in a state where the cage guide member 50 is incorporated in the annular space, the extending ends 55a and 56a of the plurality of rear blades 55 and the front blades 56 are the inner peripheral surface of the outer ring raceway shoulder 32. Each of the annular grooves 32a is in elastic contact with the groove bottom surface. A first space 100 is formed between each of the extended ends 55a and 56a of the plurality of rear blades 55 and the front blades 56 and the outer peripheral surface of the retainer 45, and a common base 54 and A second space 101 smaller than the first space 100 is formed between the outer peripheral surface of the cage 45.
Further, as shown in FIG. 3, the rear blade 55 and the front blade 56 are extended from the extending ends 55 a and 56 a of the rear blade 55 and the front blade 56 toward the base 54. It is desirable that the space between the outer peripheral surface of the retainer 45 is set to be gradually reduced.

During rotation in one direction (forward direction) of the rotating shaft 1, the retainer 45 rotates in the same direction later than the rotating shaft 1 by the plurality of rolling elements 40 that roll in the same direction.
During rotation in one direction (forward direction) of the cage 45, the first space 100 between the extended ends 55 a of the plurality of rear blades 55 located on the rear side in the rotational direction and the outer peripheral surface of the cage 45. The side air flows toward the second space 101 that is smaller than the first space 100 between the base portion 54 and the outer peripheral surface of the retainer 45.
That is, in the rear slat 55, the dynamic pressure is generated by the air that has lost its place when the air on the first space 100 side flows toward the second space 101 like a wedge. This dynamic pressure acts in a direction away from each other with respect to the base portion 54 of the rear blade 55 and the outer peripheral surface of the cage 45 constituting the first space 100.
As the rotational speed of the cage 45 changes from the low speed rotation range to the high speed rotation range, the above-described dynamic pressure increases.
For this reason, in the high-speed rotation area of the retainer 45, the base 54 of the rear vane plate 55 and the outer peripheral surface of the retainer 45 are not in contact with each other. Can do.

In addition, when the rotating shaft 1 is switched and rotated in the other direction (reverse direction), and the cage 45 is switched and rotated in the other direction (reverse direction), the front side of the cage 45 is rotated in the opposite direction. This blade plate 56 extends toward the rear side of the reverse rotation.
Thereby, even when the retainer 45 rotates in the reverse direction, the air on the first space 100 side flows toward the second space 101 side like a wedge. As a result, dynamic pressure due to air is generated on the second space 101 side, and this dynamic pressure is in a direction away from the base 54 of the front blade plate 56 and the outer peripheral surface of the retainer 45 constituting the second space 101. Works.
For this reason, in the high-speed rotation area of the retainer 45, the base 54 of the front slat 56 and the outer peripheral surface of the retainer 45 are not in contact with each other. it can.

  Further, in the first embodiment, the cage guide member 50 is formed by integrally forming the support 51, the plurality of rear blades 55 and the front blade 56 with a single thin leaf spring material. The number of points and assembly man-hours can be minimized, and cost reduction is highly effective.

  In the first embodiment, axial notches 72 and 73 are formed in the terminal coupling portions 52 at both ends of the support member constituting portion 51A, and the support member constituting portion 51A is rounded into a cylindrical shape to The cylindrical supports 51 are formed by fitting the cuts 72 and 73 to each other. However, as shown in FIG. 6, the radial cuts 72 ′ and 73 ′ are formed in the terminal coupling portions 52 at both ends of the support component 51A. Alternatively, the cylindrical support 51 may be formed by rounding the support component 51A into a cylindrical shape and fitting the cuts 72 ′ and 73 ′ of the both end coupling portions 52 together. In this case, the contraction operation in the circumferential direction of the support 51 is not restricted by the cuts 72 ′ and 73 ′.

Next, a rolling bearing according to Embodiment 2 of the present invention will be described with reference to FIGS.
In the second embodiment, the shape of the cage guide member 150 is changed, and the width E of the plurality of rear blades 155 and front blades 156 is determined from the inner surface of the pocket 47 of the cage 45. It is set smaller than the thickness dimension (thickness minimum dimension) D of the axial direction end part 45a to the axial direction end surface (for example, smaller by about a fraction).
In addition, the support body 151 is provided with connection support portions 153 on both side portions in the axial direction of the plurality of rear blades 155 and the front blades 156.
Further, both supports 151 are formed in a cylindrical shape having an inner diameter that is equivalent to the diameter of a circle that passes through the base 154 on the connection support portion 153 side of the plurality of rear blades 155 and the front blades 156. ing.
And as shown in FIG. 10, between the outer peripheral surface of the axial direction edge part 45a of the holder | retainer 45, and the internal peripheral surface of both the support bodies 151, the annular space S which can generate | occur | produce the dynamic pressure by the flow of air is produced. Composed.
The axial width dimension F of the cage guide member 150 having a plurality of rear blades 155 and front blades 156 and both supports 151 is the thickness of the axial end portion 45 a of the cage 45. It is set appropriately larger than the thickness dimension D.

Also in the second embodiment, both the support members 151 of the cage guide member 150, the plurality of rear blades 155 and the front blades 156 are integrally formed by a single thin leaf spring material. .
That is, as shown in FIG. 8, it is appropriately longer than the length dimension of the both support bodies 151 in the unfolded state, and the width dimension in the axial direction of both support bodies 151 and the rear blade plate 155 (or the front blade plate). 156) The longitudinal and lateral cuts 170 and 171 are formed by bracing or the like on a single thin leaf spring material 150A having a width obtained by adding the width in the axial direction of 156). Both support member constituting portions 151A for forming, and blade plate constituting portions 155A and 156A for forming the rear blade plate 155 and the front blade plate 156 are formed. At this time, a connection support portion 153 is formed between the blade plate constituting portions 155A and 156A. Further, cuts 172 and 173 are formed in the terminal coupling portions 152 at both ends of both support member constituting portions 151A.
Thereafter, as shown in FIG. 7, both support member constituting portions 151 </ b> A are respectively rounded into a cylindrical shape, and the notches 172 and 173 of the terminal connecting portion 152 are fitted into each other to form both support members 151. The combined blade plate portions 155A and 156A form a rear blade plate 155 and a front blade plate 156, thereby forming a cage guide member 150.
Since the other structure of this Example 2 is comprised similarly to Example 1, the same code | symbol is attached | subjected with respect to the same component, and the description is abbreviate | omitted.

In the rolling bearing according to the second embodiment configured as described above, in a state where the cage guide member 150 is incorporated in the annular space between the inner circumferential surface of the outer ring raceway shoulder and the outer circumferential surface of the cage, The inner surface of the common base 154 of the plurality of rear blades 155 and the front blades 156 of the cage guide member 150 functions as a rotation guide portion of the cage. Also, both supports 151 can function as a rotation guide for the cage.
Further, in a state where the cage guide member 150 is incorporated, the extended ends 155a and 156a of the plurality of rear blades 155 and the front blade plates 156 are elastically formed on the inner peripheral surface of the outer ring raceway shoulder 32, respectively. To touch. A first space is formed between each of the extended ends 155a and 156a of the plurality of rear blades 155 and front blades 156 and the outer peripheral surface of the retainer 45, and a common base 154 and retainer are formed. A second space smaller than the first space is formed between the first outer space and the outer peripheral surface. As a result, as described in the first embodiment, the dynamic pressure is generated by the air that has lost its place because the air on the first space side flows into the second space like a wedge.

In particular, in the second embodiment, when the cage 45 is rotated during the rotation of the bearing, as shown in FIG. 10, the outer peripheral surface of the axial end portion 45 a of the cage 45 and both supports of the cage guide member 150. A wide portion Sa and a narrow portion Sb are generated in the annular space S between the inner peripheral surface of 151. Then, dynamic pressure of air is generated in the narrow portion Sb. This dynamic pressure acts in a direction away from each other with respect to the outer peripheral surfaces of both supports 151 and the axial end 45a of the retainer 45.
For this reason, in the high-speed rotation area of the retainer 45, both the supports 151 are kept in a non-contact state with respect to the outer peripheral surface of the axial end portion 45a of the retainer 45. For this reason, the heat_generation | fever by the friction between both the support body 151 and the holder | retainer 45 can be suppressed.

In addition, this invention is not limited to the said Example 1 and 2, In the range which does not deviate from the summary of this invention, it can implement with a various form.
For example, in the first and second embodiments, the support member constituting portion 51A (151A) is rounded into a cylindrical shape, and the notches 72 and 73 (172 and 173) of the terminal coupling portion 52 (152) are fitted into each other to form a cylindrical shape. Although the support body 51 (151) is formed, the support body constituting part 51A (151A) may be rounded into a cylindrical shape, and the terminal coupling part 52 (152) may be joined by welding, an adhesive, or the like.
Further, the cage guide member 50 integrally including the support 51, the plurality of rear blades 55, and the front blades 56 is formed by injection molding of a resin material having heat resistance, oil resistance, spring properties, and the like. It is also possible to do.

DESCRIPTION OF SYMBOLS 1 Rotating shaft 2 Housing 20 Inner ring 30 Outer ring 40 Rolling body 45 Retainer 50 Retainer guide member 51 Support body 55 Rear blade (blade plate)
56 Front slat (blade)

Claims (5)

A rolling bearing having an inner ring, an outer ring, a plurality of rolling elements, and a cage is incorporated into an annular space between the inner circumferential surface of the outer ring and the outer circumferential surface of the cage to rotate the cage. A cage guide member for a rolling bearing to be guided,
A support body on which a plurality of connection support portions spaced apart from each other in the circumferential direction are disposed;
In a state of being supported by each of the plurality of connection support portions, it is disposed in an annular space between the inner peripheral surface of the outer ring and the outer peripheral surface of the cage, and is directed at least to the rear side in the rotation direction of the cage. And a plurality of blades whose extended ends are in contact with the inner peripheral surface of the outer ring,
In the state of being incorporated in the annular space, the diameter dimension of a circle passing through the base part on the connection support part side of the plurality of blades is set slightly larger than the outer diameter dimension of the cage, and each base part is As a rotation guide for the cage,
The first space formed between the extending end of the blade and the outer peripheral surface of the cage is more than the second space formed between the base of the blade and the outer peripheral surface of the cage. A cage guide member for a rolling bearing, characterized by being set large. A cage guide member for a rolling bearing according to claim 1,
The plurality of connection support portions of the support body extend to the front side in the rotation direction of the cage in the annular space between the inner circumferential surface of the outer ring and the outer circumferential surface of the cage, and the extension ends thereof A cage guide member for a rolling bearing, characterized in that a front blade is formed in contact with the inner peripheral surface of the outer ring. A cage guide member for a rolling bearing according to claim 1 or 2,
The support body is provided with connection support portions on both axial sides of the plurality of blades, and has an inner diameter dimension equivalent to the diameter of a circle passing through the base portion on the connection support portion side of the plurality of blade plates. Formed into a cylindrical shape having
An annular space is formed between the outer peripheral surface of the axial end portion of the cage and the inner peripheral surfaces of the two supports so that dynamic pressure can be generated by the flow of air. Cage guide member. A cage guide member for a rolling bearing according to any one of claims 1 to 3,
A cage guide member for a rolling bearing, wherein the support and the plurality of blades are integrally formed by a single thin leaf spring material.   An inner ring disposed on the rotating shaft side, an outer ring disposed on the housing side, a plurality of rolling elements disposed in an annular space between the inner ring and the outer ring, and a plurality of these rolling elements The rolling element, a retainer to be held, and an annular space between an inner peripheral surface of the outer ring and an outer peripheral surface of the retainer to rotate and guide the retainer. A rolling bearing comprising the cage guide member described above.

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