JP2013224733A - Rolling bearing, rolling bearing device and pivot device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To reduce fluctuations of torque and resonance.SOLUTION: A rolling bearing device 1 includes: two rolling bearings 10, 20 which include inner wheels 11, 21 and outer wheels 13, 23 arranged concentrically and a plurality of rolling bodies 15, 25 arranged with an interval in the circumferential direction in an annular space between the inner wheels 11, 21 and the outer wheels 13, 23, and are arranged with an interval in the axial direction; and a shaft 31 fitted to the inner wheels 11, 21 of the rolling bearings 10, 20; wherein the rolling bearings 10, 20 have reference surface parts 11a, 21a and protruded surface parts 11b, 21b protruded in a radial direction with respect to the reference surface parts 11a, 21a on at least one side of an inner circumferential surface of the inner wheels 11, 21, and the protruded surface parts 11b, 21b are fixed to the outer circumferential surface of the shaft 31 in a press fit condition.

Description

  The present invention relates to a rolling bearing, a rolling bearing device, and a pivot device.

  Conventionally, a rolling bearing device used for a magnetic recording device (HDD) or the like is known (for example, see Patent Document 1). A rolling bearing device described in Patent Document 1 includes a rolling bearing including an inner ring and an outer ring arranged coaxially and a rolling element, a shaft (rotary shaft) fitted to the inner ring of the rolling bearing, and an outer ring of the rolling bearing. And a shaft and an inner ring and a housing and an outer ring by press-fitting or press-fitting and adhesive, respectively, by a radially projecting convex portion formed on the outer peripheral surface of the shaft and the inner peripheral surface of the housing. It is fixed by combined use.

Japanese Patent Laid-Open No. 11-182543

  However, in the conventional rolling bearing device in which the convex portion is formed on the outer peripheral surface of the shaft and the inner peripheral surface of the housing, the convex portion is processed with reference to the axial end surfaces of the shaft and the housing. Accumulation of component dimensions tends to vary the axial position of the convex portion of the rolling bearing with respect to the raceway. For this reason, the conventional rolling bearing device has the disadvantages that variations in the amount of deformation of the inner ring or outer ring caused by press-fitting occur, resulting in an increase in radial play variation and an increase in resonance and torque variations.

  The present invention has been made in view of the above-described circumstances, and an object thereof is to provide a rolling bearing, a rolling bearing device, and a pivot device that reduce variations in torque and resonance.

In order to achieve the above object, the present invention provides the following means.
The present invention includes an inner ring and an outer ring arranged coaxially, and a plurality of rolling elements arranged in the annular space between the inner ring and the outer ring at intervals in the circumferential direction, with an interval in the axial direction. Two rolling bearings arranged; a shaft member fitted to the inner ring of the rolling bearing; and an outer fitting member having a fitting hole for fitting the outer ring of the rolling bearing; At least one of the peripheral surface and the outer peripheral surface of the outer ring is composed of a reference surface portion and a convex surface portion that is disposed at at least one end in the axial direction and protrudes in the radial direction over the entire circumference with respect to the reference surface portion, Provided is a rolling bearing device in which a convex surface portion is fixed in a press-fit state to the outer peripheral surface of the shaft member or the inner peripheral surface of the outer fitting member.

  According to the present invention, the shaft member fitted to each inner ring of the two rolling bearings and the outer fitting member fitted to each outer ring are supported by these two rolling bearings so as to be relatively rotatable. In this case, in each rolling bearing, a convex surface portion provided on at least one of the inner peripheral surface of the inner ring or the outer peripheral surface of the outer ring is fixed in a press-fit state to the outer peripheral surface of the shaft member or the inner peripheral surface of the outer fitting member. Thus, the inner ring and the shaft member and / or the outer ring and the outer fitting member are joined.

  Therefore, as in the case where a plurality of convex surface portions are provided on the outer peripheral surface of the shaft member or the inner peripheral surface of the outer fitting member and press-fitted and fixed, the positional variation in the axial direction of the convex portion with respect to the raceway due to the accumulation of variation in component dimensions is caused. It can be avoided. As a result, variations in the deformation amount of the inner ring and / or outer ring caused by press fitting can be suppressed, and variations in torque and resonance can be reduced.

  Further, by arranging a convex surface portion at least one end in the axial direction of the inner ring and / or the outer ring, when the shaft member is fitted to the inner ring or the outer ring is fitted to the outer fitting member, It is possible to prevent the rolling elements from being pressed against the raceway of the inner ring and the outer ring by press-fitting and to prevent the raceway from being damaged. Accordingly, it is possible to prevent smooth rotation of the rolling bearing from being hindered by damage to the raceway of the inner ring or the outer ring.

  Further, by joining the inner ring and the shaft member and / or the outer ring and the outer fitting member by press-fitting and fixing the convex surface portion, there is no need to finish and polish the reference surface portion, and the inner ring surface of the inner ring and / or the outer ring surface of the outer ring Only the convex surface is sufficient for the area of final polishing. Therefore, as compared with the case where the entire inner ring and / or the entire outer ring are press-fitted and fixed, the polishing time can be shortened, and the consumption of the grindstone can be reduced and the cost can be reduced.

In the said invention, it is good also as the said convex surface part being arrange | positioned at the rear-end side of the fitting direction.
With this configuration, when the shaft member is fitted to the inner ring or the outer ring is fitted to the outer fitting member, the reference surface portion of the inner peripheral surface of the inner ring or the reference surface portion of the outer peripheral surface of the outer ring is used as a guide. Can function. Therefore, it is possible to prevent the rolling bearing from being press-fitted and fixed while being inclined obliquely, and to reduce variations in torque and resonance due to poor assembly.

Moreover, in the said invention, the said convex surface part is good also as arrange | positioning in the edge part of the side by which the inner ring | wheels or outer ring | wheels of the said two rolling bearings adjoin.
With this configuration, when the inner ring and / or the outer ring having the convex surface portion are pressed in a direction in which the inner rings or the outer rings are relatively close to each other in the axial direction to apply preload to the two rolling bearings, the inner ring and the outer ring are pressed. The contact position on the raceway between the inner ring or outer ring and the rolling element moves to the side opposite to the pressing direction. Therefore, the distance between the convex part of the inner ring and / or the outer ring and the rolling element contact position on the raceway can be increased, and deformation of the rolling element contact position on the raceway caused by the press-fitting of the convex part can be suppressed. Thereby, variation in torque and resonance can be further reduced.

Moreover, in the said invention, the said convex surface part is good also as arrange | positioning at the both ends of the axial direction of the said inner ring and / or the said outer ring | wheel.
By comprising in this way, when assembling a rolling bearing, a shaft member, and an external fitting member, the front-and-back determination of a rolling bearing becomes unnecessary, and mass productivity can be improved.

Moreover, in the said invention, the said shaft member and / or the said external fitting member which oppose the said convex-surface part are radial to the area | region facing either one of the said convex-surface parts arrange | positioned at the both ends of the said axial direction. It is good also as having a concave surface area which becomes depressed.
By configuring in this way, one of the two convex surface portions arranged at both ends of the inner ring and / or the outer ring is fixed by press-fitting to the shaft member or the outer fitting member, and the other is fixed to the shaft member by the concave region. Or it becomes non-contact with respect to an external fitting member. Compared with the case where both convex surface portions are pressed against the shaft member or the outer fitting member, deformation of the raceway of the inner ring and the outer ring can be suppressed. Thereby, variation in torque and resonance can be further reduced.

In the above invention, the reference surface portion of the inner ring and / or the outer ring may have a diameter dimension that is not in contact with the outer peripheral surface of the shaft member or the inner peripheral surface of the outer fitting member. .
With this configuration, when the rolling bearing, the shaft member, and the outer fitting member are assembled, the reference surface portion of the inner ring and / or outer ring, that is, the region on the back side of the raceway is the outer peripheral surface of the shaft member or the outer fitting member. Therefore, the raceway can be prevented from being deformed and the raceway can be prevented from being damaged.

Moreover, in the said invention, the said inner ring | wheel and / or the said outer ring | wheel are good also as having a groove part hollow in a radial direction in the vicinity of the said convex surface part in the said reference surface part.
By comprising in this way, the deformation | transformation of the convex part vicinity by the press fit of a convex part can be absorbed by a groove part. As a result, deformation of the raceway can be mitigated, and variations in torque and resonance can be further reduced.

Moreover, in the said invention, the said convex surface part and the said shaft member and / or the said external fitting member are good also as being welded.
By comprising in this way, since there is no clearance between a convex surface part and a shaft member and / or an external fitting member, it can weld favorably. Therefore, the inner ring and the shaft member and / or the outer ring and the outer fitting member can be joined more firmly.

In the above invention, the reference surface portion of the inner ring and / or the outer ring and the outer peripheral surface of the shaft member and / or the inner peripheral surface of the outer fitting member may be fixed by an adhesive.
By comprising in this way, an inner ring | wheel and a shaft member and / or an outer ring | wheel and an external fitting member can be joined more firmly by the press injection by a convex surface part, and adhesion | attachment of a reference surface part. By making the thickness of the adhesive layer uniform in the circumferential direction of the inner ring and the outer ring, deformation of the inner ring or the outer ring due to curing shrinkage of the adhesive can be suppressed, and torque swell can be improved.

Moreover, in the said invention, the said reference surface part is good also as surface roughness being larger than the said convex surface part.
By comprising in this way, the adhesive force of the adhesive agent in a reference surface part can be improved, making it easy to press-fit a convex surface part comparatively smoothly. Thereby, the inner ring and the shaft member and / or the outer ring and the outer fitting member can be bonded more firmly while preventing an assembly failure due to oblique pushing or the like.

Moreover, in the said invention, the said external fitting member is good also as providing the spacer part pinched by the axial direction between the said outer ring | wheels.
By comprising in this way, the clearance gap according to the length of the spacer part is formed between inner rings. Therefore, it is possible to easily apply a preload to the two rolling bearings by pressing the inner rings in a relatively close direction.

Moreover, in the said invention, it is good also as providing the spacer member pinched | interposed to one side between the said inner ring | wheels or between the said outer ring | wheels.
By comprising in this way, the clearance gap according to the length of the spacer member is formed between the outer rings in which the spacer member is not provided, or between the inner rings. Therefore, it is possible to easily apply a preload to the two rolling bearings by pressing the outer rings or the inner rings having these gaps in directions that are relatively close to each other.

In the above invention, the inner ring or the outer ring of the two rolling bearings has a length dimension that is longer in the axial direction than the outer ring or the inner ring that overlaps in the axial direction, and the length in the axial direction is longer. The inner rings or the outer rings may be arranged so as to abut against each other in the axial direction, and the outer rings or the inner rings having a short axial length may be arranged apart from each other in the axial direction.
In this case, the inner rings or outer rings having a long axial length may be integrally formed with each other in the axial direction.

  By configuring in this way, the length dimension between the inner rings or outer rings having a long axial length is between the outer rings or inner rings having a short axial length without using a spacer member. A gap corresponding to the difference is formed. Therefore, it is possible to easily apply preload to the two rolling bearings by reducing the number of parts by the amount of the spacer member.

The present invention provides any one of the above-described rolling bearing devices, a base member to which one of the shaft member and the outer fitting member is fixed, and a swing arm to be attached to the other outer fitting member or the shaft member. A pivot device is provided.
According to the present invention, the shaft member and the outer fitting member are relatively rotated by the two rolling bearings of the rolling bearing device, so that the shaft member or the base member fixed to the outer fitting member is moved to the other side. The mounted swing arm can be swung with a stable torque.

  The present invention includes an inner ring and an outer ring arranged coaxially, and a plurality of rolling elements arranged in the annular space between the inner ring and the outer ring at intervals in the circumferential direction, with an interval in the axial direction. Two rolling bearings arranged, and a shaft fitted to the two inner rings in a state where the outer rings of the two rolling bearings are abutted in the axial direction and the inner rings are spaced apart from each other in the axial direction An inner peripheral surface of the inner ring is composed of a reference surface portion and a convex surface portion that is disposed at least at one end in the axial direction and protrudes in the radial direction over the entire circumference with respect to the reference surface portion, Provided is a rolling bearing device in which a convex surface portion is fixed to the outer peripheral surface of the shaft member in a press-fit state.

  According to the present invention, in the two rolling bearings, the inner ring and the shaft member are joined by the convex surface portion provided on the inner peripheral surface of the inner ring being fixed to the outer peripheral surface of the shaft member in a press-fitted state. Therefore, as in the case where a plurality of convex surface portions are provided on the outer peripheral surface of the shaft member and press-fitted and fixed, variation in the axial position of the convex surface portion with respect to the raceway due to accumulation of variation in component dimensions can be avoided.

As a result, variations in the deformation amount of the inner ring caused by press-fitting can be suppressed, and variations in torque and resonance can be reduced. Also, when the shaft member is fitted to the inner ring, the pressing of the convex surface portion prevents the rolling elements from being pressed against the raceway of the inner ring, thereby preventing the raceway from being damaged and preventing the rolling bearing from rotating smoothly. Can be prevented. Further, the area of the finish polishing on the inner peripheral surface of the inner ring is only a convex portion, and the polishing time can be shortened and the cost can be reduced as compared with the case where the entire inner ring is press-fitted and fixed.
In the above invention, the two outer rings may be integrated as one member.

Moreover, in the said invention, the said convex surface part is good also as arrange | positioning at the rear-end side of the fitting direction of the said inner ring | wheel which fits the said shaft member.
With this configuration, when the shaft member is fitted to the inner ring, the region other than the convex portion of the inner peripheral surface of the inner ring can function as a guide, and the press-fit is fixed with the rolling bearing tilted obliquely. The variation in torque and resonance due to poor assembly can be reduced.

Moreover, in the said invention, the said convex-surface part is good also as arrange | positioning in the edge part of the side by which the inner rings of the said two rolling bearings adjoin.
By configuring in this way, when the inner rings are pressed in the direction in which they are relatively close to each other in the axial direction and the two rolling bearings are preloaded, the contact position on the raceway between the inner ring and the rolling element is determined as the pressing direction. Move to the other side. Therefore, the distance between the convex surface part of the inner ring and the rolling element contact position on the raceway is increased, and the deformation of the rolling element contact position on the raceway caused by the press-fitting of the convex surface part is suppressed, thereby reducing variations in torque and resonance. can do.

Moreover, in the said invention, the said convex surface part is good also as arrange | positioning at the both ends of the axial direction of the said inner ring | wheel.
By comprising in this way, when assembling a rolling bearing and a shaft member, the front-and-back determination of a rolling bearing becomes unnecessary, and mass productivity can be improved.

Moreover, in the said invention, the said shaft member is good also as having a concave surface area | region recessed in radial direction in the area | region facing either one of the said convex surface part arrange | positioned at the both ends of the axial direction of the said inner ring | wheel.
By comprising in this way, one of the convex surface parts arrange | positioned at the both ends of an inner ring | wheel is fixed by press injection with respect to a shaft member, and the other becomes non-contact with respect to a shaft member by a concave surface area | region. Compared with the case where both convex surface portions are pressed against the shaft member, deformation of the raceway of the inner ring can be suppressed, and variations in torque and resonance can be further reduced.

Moreover, in the said invention, it is good also as the said reference surface part of the said inner ring | wheel having a diameter dimension which becomes non-contact with respect to the outer peripheral surface of the said shaft member.
With this configuration, when the rolling bearing and the shaft member are assembled, the reference surface portion of the inner ring, i.e., the region on the back side of the raceway does not contact the outer peripheral surface of the shaft member, so that deformation of the raceway is suppressed. The raceway can be prevented from being damaged.

Moreover, in the said invention, the said inner ring | wheel is good also as having a groove part hollow in a radial direction in the vicinity of the said convex surface part in the said reference surface part.
With this configuration, the groove portion can absorb the deformation in the vicinity of the convex surface portion due to the press-fitting of the convex surface portion, relax the deformation of the raceway, and can further reduce variations in torque and resonance.

Moreover, in the said invention, it is good also as the said convex surface part and the said shaft member being welded.
By comprising in this way, since there is no gap between a convex surface part and a shaft member, it can weld favorably and can join an inner ring and a shaft member more firmly.

Moreover, in the said invention, the said reference surface part of the said inner ring | wheel and the outer peripheral surface of the said shaft member are good also as being fixed with the adhesive agent.
By comprising in this way, an inner ring | wheel and a shaft member can be joined more firmly by the press injection by a convex surface part, and adhesion | attachment of a reference surface part. By making the thickness of the adhesive layer uniform in the circumferential direction of the inner ring, it is possible to suppress deformation of the inner ring due to curing shrinkage of the adhesive and improve torque swell.

Moreover, in the said invention, the said reference surface part is good also as surface roughness being larger than the said convex surface part.
By constituting in this way, while making it easy to press-fit the convex surface part relatively smoothly, the adhesive force of the adhesive on the reference surface part is improved, while preventing the assembly failure due to oblique pushing, etc., the inner ring and the shaft member Can be bonded more firmly.

Moreover, in the said invention, it is good also as providing the spacer member pinched | interposed into the axial direction between the said outer ring | wheels.
With this configuration, the outer rings are indirectly abutted in the axial direction via the spacer member, and a gap corresponding to the length of the spacer member is formed between the inner rings. Therefore, it is possible to easily apply a preload to the two rolling bearings by pressing the inner rings in a relatively close direction.

  In the above invention, the outer rings of the two rolling bearings have a length dimension that is longer in the axial direction than the inner ring that overlaps in the axial direction, and are arranged such that the end faces in the axial direction directly abut each other. It is good to be.

  With this configuration, a gap corresponding to the difference in length between the outer rings is formed between the inner rings without using a spacer member, so the number of parts is reduced by the amount of the spacer member. Thus, preload can be easily applied to the two rolling bearings.

The present invention provides a pivot device comprising any one of the above-described rolling bearing devices, a base member to which one of the shaft member and the outer ring is fixed, and a swing arm mounted to the other outer ring or the shaft member. I will provide a.
According to the present invention, the swing arm attached to the other of the base member fixed to the shaft member or the outer ring can be swung with a stable torque.

  The present invention includes an inner ring and an outer ring arranged coaxially, and a plurality of rolling elements arranged in the annular space between the inner ring and the outer ring at intervals in the circumferential direction, with an interval in the axial direction. Two rolling bearings that are arranged and a fitting that fits the two outer rings in a state in which the inner rings of the two rolling bearings are abutted in the axial direction and the outer rings have a gap in the axial direction. An outer fitting member having a hole, and an outer peripheral surface of the outer ring is disposed at a reference surface portion and at least one end portion in the axial direction, and a convex surface portion projecting in a radial direction over the entire circumference with respect to the reference surface portion. A rolling bearing device in which the convex surface portion is fixed to the inner peripheral surface of the outer fitting member in a press-fitted state.

  According to the present invention, in the two rolling bearings, the outer ring and the outer fitting member are joined by fixing the convex surface portion provided on the outer circumferential surface of the outer ring to the inner circumferential surface of the outer fitting member in a press-fitted state. Therefore, as in the case where a plurality of convex surface portions are provided on the inner peripheral surface of the outer fitting member and press-fitted and fixed, it is possible to avoid variations in the axial position of the convex surface portion with respect to the raceway due to accumulation of variations in component dimensions.

Thereby, variation in the deformation amount of the outer ring caused by press-fitting can be suppressed, and variation in torque and resonance can be reduced. Also, when the outer ring is fitted to the outer fitting member, the rolling element is prevented from being pressed against the raceway of the outer ring by press-fitting the convex surface portion to prevent the raceway from being damaged, and the rolling bearing can be smoothly rotated. It can be prevented from being hindered. The area of the finish polishing on the outer peripheral surface of the outer ring is only the convex portion, and the polishing time can be shortened and the cost can be reduced as compared with the case where the entire outer ring is press-fitted and fixed.
In the above invention, the two inner rings may be integrated as one member.

In the said invention, the said convex surface part is good also as arrange | positioning in the rear-end side of the fitting direction of the said outer ring | wheel fitted by the said external fitting member.
With this configuration, when the outer ring is fitted to the outer fitting member, the region other than the convex portion of the outer peripheral surface of the outer ring is caused to function as a guide, and the rolling bearing is press-fitted and fixed while being inclined obliquely. Variation in torque and resonance due to poor assembly can be reduced.

Moreover, in the said invention, the said convex surface part is good also as arrange | positioning in the edge part of the side by which the outer ring | wheels of the said two rolling bearings adjoin.
With this configuration, when the outer rings are pressed in a direction relatively close to each other in the axial direction to apply preload to the two rolling bearings, the contact position on the raceway between the pressed outer ring and the rolling element is pressed. Move to the opposite side of the direction. Therefore, the distance between the convex surface part of the outer ring and the rolling element contact position on the raceway is increased, and the deformation of the rolling element contact position on the raceway caused by the press-fitting of the convex surface part is suppressed, thereby reducing variations in torque and resonance. can do.

Moreover, in the said invention, the said convex surface part is good also as arrange | positioning at the both ends of the axial direction of the said outer ring | wheel.
By comprising in this way, when assembling a rolling bearing and an external fitting member, the front-and-back determination of a rolling bearing becomes unnecessary, and mass productivity can be improved.

Moreover, in the said invention, the said external fitting member is good also as having a concave surface area | region recessed in radial direction in the area | region facing either one of the said convex surface part arrange | positioned at the both ends of the axial direction of the said outer ring | wheel. .
By comprising in this way, among the convex surface parts arrange | positioned at the both ends of an outer ring | wheel, one is fixed by press-fitting with respect to an external fitting member, and the other becomes non-contact with respect to an external fitting member by a concave surface area | region. Compared with a case where both convex portions are pressed against the outer fitting member, deformation of the raceway of the outer ring can be suppressed, and variations in torque and resonance can be further reduced.

Moreover, in the said invention, the said reference surface part of the said outer ring | wheel is good also as having a diameter dimension which becomes non-contact with respect to the internal peripheral surface of the said external fitting member.
With this configuration, when the rolling bearing and the outer fitting member are assembled, the reference surface portion of the outer ring, that is, the region on the back side of the raceway does not contact the inner peripheral surface of the outer fitting member. And the raceway can be prevented from being damaged.

Moreover, in the said invention, the said outer ring | wheel is good also as having a groove part hollow in a radial direction in the vicinity of the said convex surface part in the said reference surface part.
With this configuration, the groove portion can absorb the deformation in the vicinity of the convex surface portion due to the press-fitting of the convex surface portion, relax the deformation of the raceway, and can further reduce variations in torque and resonance.

Moreover, in the said invention, it is good also as the said convex surface part and the said external fitting member being welded.
By comprising in this way, since there is no gap between a convex surface part and an external fitting member, it can weld favorably and can join an outer ring and an external fitting member more firmly.

Moreover, in the said invention, the said reference surface part of the said outer ring | wheel and the inner peripheral surface of the said external fitting member are good also as being fixed with the adhesive agent.
By comprising in this way, an outer ring | wheel and an external fitting member can be joined more firmly by the press injection by a convex surface part, and adhesion | attachment of a reference surface part. By making the thickness of the adhesive layer uniform in the circumferential direction of the outer ring, the deformation of the outer ring due to the curing shrinkage of the adhesive can be suppressed, and the waviness of the torque can be improved.

Moreover, in the said invention, the said reference surface part is good also as surface roughness being larger than the said convex surface part.
By constituting in this way, it is possible to improve the adhesive force of the adhesive on the reference surface portion while making it easier to press-fit the convex surface portion relatively smoothly, and while preventing the assembly failure due to oblique push-in, etc. The outer fitting member can be more firmly bonded.

Moreover, in the said invention, it is good also as providing the spacer member pinched | interposed into the axial direction between the said inner ring | wheels.
With this configuration, the inner rings are indirectly abutted in the axial direction via the spacer member, and a gap corresponding to the length of the spacer portion is formed between the outer rings. Therefore, it is possible to easily apply preload to the two rolling bearings by pressing the outer rings in a relatively close direction.

  In the above invention, the outer rings of the two rolling bearings have a length dimension that is longer in the axial direction than the inner ring that overlaps in the axial direction, and are arranged such that the end faces in the axial direction directly abut each other. It is good to be.

  With this configuration, a gap corresponding to the difference in length between the inner rings is formed between the outer rings without using a spacer member, so the number of parts is reduced by the amount of the spacer member. Thus, preload can be easily applied to the two rolling bearings.

The present invention includes any one of the above-described rolling bearing devices, a base member to which any one of the inner ring and the outer fitting member is fixed, and a swing arm attached to the other outer fitting member or the inner ring. A pivot device is provided.
According to the present invention, the swing arm mounted on the other side of the base member fixed to the inner ring or the outer fitting member can be swung with a stable torque.

  The present invention provides a rolling bearing used in any of the above rolling bearing devices.

  According to the present invention, there is an effect that variations in torque and resonance can be reduced.

1 is a schematic configuration diagram of a hard disk drive device including a pivot device according to a first embodiment of the present invention. It is a longitudinal cross-sectional view of the rolling bearing apparatus of FIG. It is a longitudinal cross-sectional view which shows a mode that a shaft is fitted to the 1st rolling bearing of the rolling bearing apparatus of FIG. It is a figure which shows the relationship between the width dimension of the convex part of an inner ring | wheel, and a resonance. It is a longitudinal cross-sectional view of the rolling bearing apparatus which concerns on the 1st modification of 1st Embodiment of this invention. It is a longitudinal cross-sectional view of the rolling bearing apparatus which concerns on the 2nd modification of 1st Embodiment of this invention. It is a longitudinal cross-sectional view of the rolling bearing apparatus which concerns on the 3rd modification of 1st Embodiment of this invention. It is a longitudinal cross-sectional view of the other rolling bearing apparatus which concerns on the 3rd modification of 1st Embodiment of this invention. It is a longitudinal cross-sectional view of the other rolling bearing apparatus which concerns on the 3rd modification of 1st Embodiment of this invention. It is a longitudinal cross-sectional view of the rolling bearing apparatus which concerns on the 4th modification of 1st Embodiment of this invention. It is a longitudinal cross-sectional view of the rolling bearing apparatus which concerns on the 5th modification of 1st Embodiment of this invention. It is a longitudinal cross-sectional view of the rolling bearing apparatus which concerns on the 6th modification of 1st Embodiment of this invention. It is a longitudinal cross-sectional view of the rolling bearing apparatus which concerns on the 7th modification of 1st Embodiment of this invention. It is a longitudinal cross-sectional view of the rolling bearing apparatus which concerns on 2nd Embodiment of this invention. In the rolling bearing device concerning the modification of a 2nd embodiment of the present invention, it is a longitudinal section showing the modification in which the outer rings are arranged to abut against each other in the axial direction. In the rolling bearing device concerning another modification of a 2nd embodiment of the present invention, it is a longitudinal section showing a modification in which inner rings are arranged so as to be faced mutually in the axial direction. In the rolling bearing device according to the first embodiment of the present invention, it is a longitudinal sectional view showing a modification in which outer rings are formed integrally with each other in the axial direction. In the rolling bearing device concerning a 2nd embodiment of the present invention, it is a longitudinal section showing an example in which an outer ring is mutually formed in the direction of an axis. In the rolling bearing device concerning a 2nd embodiment of the present invention, it is a longitudinal section showing a modification in which an inner ring is mutually formed in the direction of an axis.

[First Embodiment]
Hereinafter, a rolling bearing, a rolling bearing device, and a pivot device according to a first embodiment of the present invention will be described with reference to the drawings.
The pivot device 50 according to the present embodiment can be used for a hard disk drive device 100, for example, as shown in FIG. The pivot device 50 includes a base housing 2 having a substantially rectangular box shape, a swing arm 4 that can swing with respect to the base housing 2, and a rolling bearing device 1 that supports the swing arm 4 so as to be swingable. Yes. Reference numeral 6 denotes a magnetic recording medium, and reference numeral 8 denotes a drive unit such as a voice coil motor that swings the swing arm 4.

  A magnetic head 5 for writing magnetic information on the magnetic recording medium 6 and reading magnetic information recorded on the magnetic recording medium 6 is attached to the tip of the swing arm 4. The swing arm 4 is mounted with a rolling bearing device 1 in a bearing fitting hole (not shown), and can be swung around the central axis C by the driving unit 8 with the rolling bearing device 1 as a fulcrum. As a result, the magnetic head 5 can be positioned on the magnetic recording medium 6.

  As shown in FIG. 2, the rolling bearing device 1 is fitted to a first rolling bearing 10 and a second rolling bearing 20 that are arranged coaxially with an interval in the axial direction, and these rolling bearings 10 and 20. A shaft (shaft member) 31 and a spacer member 33 sandwiched between the rolling bearings 10 and 20 in the axial direction are provided.

  The shaft 31 is formed in a hollow substantially cylindrical shape. The shaft 31 is provided with a flange-shaped flange portion 31a that protrudes radially outward over the entire circumference at one end in the axial direction. The first rolling bearing 10 and the second rolling bearing 20 are fitted into the shaft 31 in this order from the flange portion 31a side.

  The first rolling bearing 10 includes a plurality of annular inner rings 11 and outer rings 13 that are coaxially arranged, and a plurality of annular bearings that are incorporated in an annular space between the inner ring 11 and the outer ring 13 at intervals in the circumferential direction. And rolling elements 15. As for the inner ring | wheel 11 of this 1st rolling bearing 10, the end surface of the axial direction is abutted against the flange part 31a. The second rolling bearing 20 has the same configuration and dimensions as the first rolling bearing 10, and includes an inner ring 21 and an outer ring 23, and a plurality of rolling elements 25. These rolling elements 15 and 25 are held so as to be able to roll in a state where they are arranged at equal intervals by a retainer (not shown).

  The inner rings 11, 21 each have a deep groove type or angular raceway (inner ring raceway) on the outer peripheral surface, and the outer rings 13, 23 each have a deep groove type or angular raceway (outer ring raceway) on the inner peripheral surface. Have. When the rolling elements 15 and 25 are respectively rolled between the raceway of the inner rings 11 and 21 and the raceway of the outer rings 13 and 23, the inner rings 11, 21 and the outer rings 13, 23 are relatively rotated. It is like that.

  The inner rings 11 and 21 have a stepped inner peripheral surface. Specifically, the inner peripheral surfaces of the inner rings 11 and 21 are reference surface portions 11a and 21a that occupy most of the wall surfaces, and the remaining portions of the wall surfaces, and protrude radially inward from the reference surface portions 11a and 21a. And convex surface portions 11b and 21b. The convex surface portions 11b and 21b are disposed at one end portion in the axial direction of the inner peripheral surfaces of the inner rings 11 and 21, and are formed over the entire region in the axial direction.

  In this embodiment, the convex surface parts 11b and 21b are arrange | positioned at the edge part of the side in which the inner rings 11 and 21 of the 1st rolling bearing 10 and the 2nd rolling bearing 20 separate, respectively. That is, as shown in FIG. 3, the first rolling bearing 10 has the inner ring 11 fitted with the shaft 31 with the axially convex surface portion 11 b side facing the flange portion 31 a, and the second rolling bearing 20 has the inner ring 21. The shaft 31 is fitted with the opposite side of the convex surface portion 21b in the axial direction facing the flange portion 31a.

  In these inner rings 11 and 21, the reference surface portions 11 a and 21 a have an inner diameter dimension larger than the outer diameter dimension of the shaft 31, and the convex surface portions 11 b and 21 b have an inner diameter dimension slightly smaller than the outer diameter dimension of the shaft 31. ing. And the convex parts 11b and 21b are fixed to the outer peripheral surface of the shaft 31 in a press-fitted state, whereby the inner rings 11 and 21 and the shaft 31 are joined. A gap is formed between the reference surface portions 11 a and 21 a of the inner rings 11 and 21 and the outer peripheral surface of the shaft 31.

  The outer rings 13 and 23 are respectively fitted in bearing fitting holes of the swing arm 4. The outer peripheral surfaces of the outer rings 13 and 23 are formed in a substantially flat shape with no step. The outer peripheral surfaces of the outer rings 13 and 23 and the bearing fitting holes of the swing arm 4 are joined by, for example, an adhesive. Examples of the adhesive include an anaerobic adhesive and a thermosetting adhesive.

  In the present embodiment, the first rolling bearing 10 and the second rolling bearing 20 have, for example, an axial thickness of 2.5 mm and an inner diameter (the inner diameter of the convex surface portions 11b and 21b of the inner rings 11 and 21) of 5 mm. The outer diameter (the outer diameter of the outer rings 13 and 23) has a dimension of 8 mm. Further, for example, the axial width of the convex surface portions 11b and 21b is 0.5 mm or less, and the convex surface portions 11b and 21b have a diameter of 12 μm (diameter).

  For example, the outer dimension of the spacer member 33 is substantially equal to the outer diameter of the outer rings 13 and 23, and the inner diameter is smaller than the inner diameter of the outer rings 13 and 23 and larger than the outer diameter of the inner rings 11 and 21. One end surface (upper end surface) of the outer ring 13 of the first rolling bearing 10 is applied to one end surface (lower end surface) of the spacer member 33 in the axial direction. The other end surface (lower end surface) in the axial direction of the outer ring 23 of the second rolling bearing 20 is applied to the end surface (upper end surface). Thereby, a gap corresponding to the axial length of the spacer member 33 is formed between the inner rings 11 and 21 of the first rolling bearing 10 and the second rolling bearing 20.

  Further, the first rolling bearing 10 and the second rolling bearing 20 are fixed to the shaft 31 in a state where the inner rings 11 and 21 are pressed in a direction close to each other by press-fitting the convex surface portions 11b and 21b. . As a result, the inner rings 11 and 21 and the outer rings 13 and 23 and the rolling elements 15 and 25 are in contact with each other with no gap in a state in which a preload is applied to the rolling bearings 10 and 20.

Hereinafter, the operation of the rolling bearing device 1 and the pivot device 50 thus configured will be described.
When the drive unit 8 is operated, the swing arm 4 is swung with the rolling bearing device 1 as a fulcrum. Specifically, in the rolling bearing device 1, the rolling elements 15 and 25 sandwiched between the inner and outer rings of the rolling bearings 10 and 20 are caused to roll, whereby the inner rings 11 and 21 fixed to the shaft 31 are moved. The outer rings 13 and 23 are rotated.

  Thereby, the swing arm 4 fixed to the outer rings 13 and 23 is swung around the central axis C with respect to the base housing 2 to which the shaft 31 is fixed. As a result, the magnetic head 5 is reciprocated on the magnetic recording medium 6. When the swing arm 4 is operated at high speed, the magnetic head 5 is instantaneously moved to data recorded at a predetermined position on the magnetic recording medium 6. The magnetic head 5 reads magnetic information recorded on the magnetic recording medium 6 and writes magnetic information.

  Here, the respective rolling bearings 10 and 20 of the rolling bearing device 1 have the convex portions 11b and 21b provided on the inner peripheral surfaces of the inner rings 11 and 21 fixed to the outer peripheral surface of the shaft 31 in a press-fit state. 11 and 21 and the shaft 31 are joined.

  As a comparative example for this, for example, if a plurality of convex surface portions are provided on the outer peripheral surface of the shaft 31 and the convex surface portions of the shaft 31 are press-fitted and fixed to the inner rings 11, 21, the flange portion 31a is used as a reference for the shaft 31. Although the convex surface portion is processed, the position of the convex surface portion in the axial direction with respect to the raceway varies due to the accumulation of variations in component dimensions.

  In the rolling bearing device 1 according to the present embodiment, the convex portions 11b and 21b are provided on the inner peripheral surfaces of the inner rings 11 and 21 and are fixed to the outer peripheral surface of the shaft 31 in a press-fitted state, resulting in accumulation of variations in component dimensions. As a result, it is possible to avoid variations in the axial position of the convex portions 11b and 21b with respect to the raceway.

  Therefore, according to the bearing device 1 and the pivot device 50 according to the present embodiment, it is possible to suppress variations in the deformation amount of the inner rings 11 and 21 caused by press-fitting and reduce variations in torque and resonance. For example, FIG. 4 shows the relationship between the width dimension of the convex surface portions 11b and 21b of the inner rings 11 and 21 and the resonance. Here, the resonance means a resonance point in the axial direction of the rotation center of the outer rings 13 and 23 of the rolling bearing device 1 when the inner rings 11 and 21 are fixed. This figure shows the case where the press-fit white (the length shrunk by press-fitting) is 12 μm, but as shown in this figure, from the end face of the rolling bearings 10 and 20 to the end part on the raceway side of the convex parts 11b and 21b. By reducing the width (a value obtained by subtracting the distance from the raceway to the end of the raceway side 11b, 21b from the raceway side) from the half of the thickness of the rolling bearings 10, 20, the resonance is reduced to 0.5 mm or less. Variation can be further reduced.

  Further, by arranging the convex surface portions 11b and 21b on one side in the axial direction of the inner races 11 and 21, when the shaft 31 is fitted to the inner races 11 and 21, the inner races 11 and 21 and the inner races 11 and 21 and It is possible to prevent the rolling elements 15 and 25 from being pressed against the raceway of the outer rings 13 and 23 and prevent the raceway from being damaged. Accordingly, it is possible to prevent smooth rotation of the rolling bearings 10 and 20 from being hindered by damage to the raceway of the inner rings 11 and 21 or the outer rings 13 and 23. Therefore, reading and writing of the hard disk drive device 100 can be performed stably.

  Further, since the reference surface portions 11 a and 21 b of the inner rings 11 and 21 are not brought into contact with the outer peripheral surface of the shaft 31, there is no need for finish polishing. Therefore, since the area of the finish polishing on the inner peripheral surfaces of the inner rings 11 and 21 is only the convex surface portions 11b and 21b, the polishing time is shortened and the grinding wheel is compared with the case where the entire inner rings 11 and 21 are press-fitted and fixed. Consumption can be reduced and the cost can be reduced.

This embodiment can be modified as follows.
In the present embodiment, the convex surface portions 11b and 21b are arranged at the end portions on the side where the inner rings 11 and 21 of the two rolling bearings 10 and 20 are separated from each other. As a first modification, for example, FIG. As shown in FIG. 5, it is good also as arrange | positioning convex-surface part 11b, 21b in the rear-end side of the fitting direction of each inner ring | wheel 11,21 with respect to the shaft 31. As shown in FIG.

  That is, the first rolling bearing 10 is fitted with the shaft 31 with the side opposite to the convex surface portion 11 b side of the inner ring 11 facing toward the flange portion 31 a, and the second rolling bearing 20 is also in the axial direction of the inner ring 21. It is good also as fitting the shaft 31 with the opposite side to the convex surface part 21b side facing the flange part 31a side.

  By doing in this way, when fitting the shaft 31 to the inner ring | wheels 11 and 21, the reference surface parts 11a and 21a whose diameter size is larger than the convex-surface parts 11b and 21b can each be functioned as a guide. Therefore, it is possible to prevent the rolling bearings 10 and 20 from being press-fitted and fixed to the shaft 31 in an oblique state, and to reduce variations in torque and resonance due to poor assembly.

  As a second modification, for example, as shown in FIG. 6, the convex surface portions 11 b and 21 b may be arranged at the end portions on the side where the inner rings 11 and 21 of the two rolling bearings 10 and 20 are close to each other. Good. That is, the first rolling bearing 10 is fitted with the shaft 31 with the opposite side to the convex surface portion 11 b side of the inner ring 11 in the axial direction facing the flange portion 31 a side, and the second rolling bearing 20 is arranged in the axial direction of the inner ring 21. It is good also as fitting the shaft 31 toward the convex part 21b side toward the flange part 31a.

  In this case, when the inner rings 11 and 21 are pressed in a direction in which the inner rings 11 and 21 are relatively close to each other in the axial direction and the two rolling bearings 10 and 20 are preloaded, the contact between the pressed inner rings 11 and 21 and the rolling elements 15 and 25 is reduced. The contact position on the raceway moves to the side opposite to the pressing direction. Therefore, the distance between the convex surface portions 11b and 21b of the inner rings 11 and 21 and the rolling element contact position on the raceway is increased, and deformation of the rolling element contact position on the raceway caused by the press-fitting of the convex surface portions 11b and 21b is suppressed. be able to. Thereby, variation in torque and resonance can be further reduced.

  Moreover, as a 3rd modification, as shown in FIG. 7, it is good also as arrange | positioning the convex-surface parts 11b and 21b to the both ends of the axial direction of the inner rings 11 and 21, respectively. That is, it is good also as having the two convex-surface parts 11b and 21b arrange | positioned at the quantity edge part of an axial direction for every inner ring | wheels 11 and 21. FIG. By doing so, the shape of the rolling bearings 10 and 20 becomes equal in the axial direction. Therefore, when the rolling bearings 10 and 20 and the shaft 31 are assembled, the front and back judgment of the rolling bearings 10 and 20 is not required, and mass productivity is increased. Can be improved.

  In the present modification, as shown in FIG. 8, the shaft 31 has a region facing either one of the convex surface portions 11 b disposed at both ends in the axial direction of the inner ring 11 of the first rolling bearing 10, and It is good also as having the concave surface area | region 31b hollow in radial direction in the area | region which opposes any one of the convex-surface part 21b arrange | positioned at the axial direction both ends of the inner ring | wheel 21 of the 2nd rolling bearing 20, respectively.

  FIG. 8 shows a region where the shaft 31 is opposed to the convex surface portion 11b disposed at the end of the inner ring 11 on the axial flange portion 31a side, and the end of the inner ring 21 opposite to the axial flange portion 31a side. The example which has the concave surface area | region 31b in the area | region which opposes the convex surface part 21b arrange | positioned at the part is shown.

  By doing so, one of the two convex surface portions 11b disposed at both end portions of the inner ring 11 and the two convex surface portions 21b disposed at both end portions of the inner ring 21 is fixed to the shaft 31 by press-fitting. The other is not in contact with the shaft 31 by the concave region 31b. Compared to the case where both convex portions 11b and 21b of the inner rings 11 and 12 are pressed against the shaft 31, deformation of the raceways of the inner rings 11 and 21 can be suppressed. Thereby, variation in torque and resonance can be further reduced.

  In the present modification, as shown in FIG. 9, the reference surface portions 11 a and 21 a of the inner rings 11 and 21 may have a diameter dimension that is not in contact with the outer peripheral surface of the shaft 31. By doing so, when the rolling bearings 10 and 20 and the shaft 31 are assembled, the reference surface portions 11 a and 11 b of the inner rings 11 and 21, that is, the region on the back side of the raceway does not contact the outer peripheral surface of the shaft 31. The raceway can be prevented from being deformed and the raceway can be prevented from being damaged.

  As a fourth modification, for example, as shown in FIG. 10, the inner rings 11 and 21 have grooves 11c and 21c that are recessed in the radial direction in the vicinity of the convex portions 11b and 21b in the reference surface portions 11a and 21a. It is good. FIG. 10 shows an example in which grooves 11c and 21c are formed at the boundary between the convex surface portions 11b and 21b and the reference surface portions 11a and 21a arranged at the end portions on the side where the inner rings 11 and 21 of the two rolling bearings 10 and 20 are close to each other. Show.

  By doing in this way, the deformation | transformation of the convex surface part vicinity by the press fit of the convex surface parts 11b and 21b can be absorbed by the groove parts 11c and 21c. As a result, the deformation of the raceway can be relaxed, and variations in torque and resonance can be further reduced.

  As a 5th modification, as shown in FIG. 11, it is good also as welding convex-surface part 11b, 21b and the shaft 31, for example. FIG. 11 shows an example in which the convex surface portion 21b arranged at the end of the inner ring 21 of the second rolling bearing 20 opposite to the axial flange portion 31a and the outer peripheral surface of the shaft 31 are laser-welded. In the figure, reference numeral 37 indicates a welding mark.

  By doing in this way, since there is no gap between the convex surface part 21b and the outer peripheral surface of the shaft 31, which are in contact with each other in the press-fitted state, it is possible to weld well. Therefore, the inner ring 21 and the shaft 31 can be joined more firmly.

  As a sixth modification, for example, as shown in FIG. 12, the reference surface portions 11 a and 21 a of the inner rings 11 and 21 and the outer peripheral surface of the shaft 31 may be fixed by an adhesive 39. In FIG. 12, convex surface portions 11 b and 21 b are arranged at the end portions of the first rolling bearing 10 and the second rolling bearing 20 on the side where the inner rings 11 and 21 are separated from each other, and the respective reference surface portions 11 a and 21 a and the outer periphery of the shaft 31 are arranged. The example which adhere | attached the surface with the adhesive agent 39 over the circumferential direction is shown. Examples of the adhesive 39 include an anaerobic adhesive and a thermosetting adhesive.

  By doing in this way, the inner ring | wheels 11 and 21 and the shaft 31 can be joined more firmly by the press injection by the convex surface parts 11b and 21b and adhesion | attachment of the reference surface parts 11a and 21a. By making the thickness of the adhesive layer uniform in the circumferential direction of the inner rings 11, 21, deformation of the inner rings 11, 21 due to curing shrinkage of the adhesive 39 can be suppressed, and torque waviness can be improved.

  In this modification, it is desirable that the reference surface portions 11a and 21a have a larger surface roughness than the convex surface portions 11b and 21b. By doing in this way, the adhesive force of the adhesive 39 on the reference surface portions 11a and 21a can be improved while making it easier to press-fit the convex surface portions 11b and 21b relatively smoothly. Thereby, the inner rings 11 and 21 and the shaft 31 can be more firmly bonded to each other while preventing an assembly failure due to oblique pushing or the like.

  Moreover, as a 7th modification, as shown in FIG. 13, the outer rings 13 and 23 of the two rolling bearings 10 and 20 have a length dimension longer in the axial direction than the inner rings 11 and 21, and these The outer rings 13, 23 may be disposed so as to abut against each other in the axial direction, and the inner rings 11, 21 may be disposed apart from each other in the axial direction. In this case, it is only necessary that the outer rings 13 and 23 are arranged such that the axial end faces directly abut each other.

  By doing this, the length dimension between the outer rings 13 and 23 having a long axial length is between the inner rings 11 and 21 having a short axial length without using the spacer member 33. Since a gap corresponding to the difference is formed, the two rolling bearings 10 and 20 are pressed by pressing the inner rings 11 and 21 in a relatively close direction while reducing the number of parts by the amount of the spacer member 33. Can be easily preloaded.

[Second Embodiment]
Next, a rolling bearing device and a pivot device according to a second embodiment of the present invention will be described.
As shown in FIG. 14, the rolling bearing device 101 according to the present embodiment includes a sleeve (outer fitting member) having a fitting hole 135 a into which the outer rings 113 and 123 of the first rolling bearing 10 and the second rolling bearing 20 are fitted. ) 135 and the pivot device 50 is different from the first embodiment in that the swing arm 4 fits the sleeve 135. In the following, portions having the same configuration as those of the rolling bearing device 1 and the pivot device 50 according to the first embodiment are denoted by the same reference numerals and description thereof is omitted.

  The sleeve 135 includes a spacer portion 135b that protrudes inward in the radial direction substantially at the center in the axial direction of the fitting hole 135a. The outer surface of the sleeve 135 is fixed to the fitting hole 135a of the swing arm 4 with an adhesive.

  In the first rolling bearing 10, one end surface (upper end surface) of the outer ring 113 in the axial direction is abutted against the lower end surface of the spacer portion 135 b of the sleeve 135, and the second rolling bearing 20 The end face (lower end face) is abutted against the upper end face of the spacer portion 135 b of the sleeve 135.

  These outer rings 113 and 123 have a stepped outer peripheral surface. Specifically, the outer peripheral surfaces of the outer rings 113 and 123 are reference surface portions 113a and 123a that occupy most of the wall surfaces, and the remaining portions of the wall surfaces, and protrude outward in the radial direction from the reference surface portions 113a and 123a. It is comprised by the convex surface parts 113b and 123b. The convex surface portions 113b and 123b are arranged at one end portion in the axial direction of the outer peripheral surfaces of the outer rings 113 and 123, and are formed over the entire region in the axial direction.

In this embodiment, the convex surface parts 113b and 123b are arrange | positioned at the edge part by which the outer rings 113 and 123 of the 1st rolling bearing 10 and the 2nd rolling bearing 20 space apart, respectively. That is, the first rolling bearing 10 is fitted in the fitting hole 135a with the opposite side of the outer ring 113 from the axially convex surface 113b side facing the spacer portion 135b side of the sleeve 135, and the second rolling bearing 20 is The outer ring 123 is fitted into the fitting hole 135a with the opposite side of the convex surface part 123b in the axial direction facing the spacer part 135b side of the sleeve 135.
Further, the convex surface portions 11b and 21b of the inner rings 11 and 21 are respectively disposed at the end portions of the first rolling bearing 10 and the second rolling bearing 20 on the side where the inner rings 11 and 21 are close to each other.

  The outer rings 113 and 123 are joined to the sleeve 135 by fixing the convex surface portions 113b and 123b to the fitting 135a in a press-fitted state, and the inner rings 11 and 21 have the convex surface portions 11b and 21b of the shaft 31. It is joined to the shaft 31 by being fixed to the inner peripheral surface in a press-fitted state. Furthermore, it is good also as fixing between the reference surface parts 11a and 21a of the inner ring | wheels 11 and 21 and the outer peripheral surface of the shaft 31, and between the outer ring | wheels 113 and 123 and the fitting hole 135a of the sleeve 135 with the adhesive agent 39. .

  Therefore, according to the rolling bearing device 101 and the pivot device 50 according to the present embodiment, variations in the positions of the inner rings 11 and 21 and the outer rings 113 and 123 can be prevented. As a result, variations in deformation amounts of the inner rings 11 and 21 and the outer rings 113 and 123 caused by press fitting can be suppressed, and variations in torque and resonance can be further reduced.

  In the present embodiment, the sleeve 135 includes the spacer portion 135b. For example, the sleeve 135 does not include the spacer portion 135b but includes a ring-shaped spacer member that is sandwiched between the outer rings 113 and 123 in the axial direction. It is good as well. Further, a spacer member sandwiched in the axial direction between the inner rings 11 and 21 may be employed, and a gap corresponding to the axial length of the spacer member may be formed between the outer rings 113 and 123. In this case, it is only necessary to apply preload to the two rolling bearings 10 and 20 by pressing the outer rings 113 and 123 in a relatively close direction.

  In the present embodiment, the convex surface portions 113b and 123b are arranged at the end portions on the side where the outer rings 113 and 123 of the first rolling bearing 10 and the second rolling bearing 20 are separated from each other. A configuration corresponding to the configuration of the inner rings 11 and 21 according to the first to seventh modifications of the first embodiment may be applied to the outer rings 113 and 123.

  For example, as shown in FIG. 15, the outer rings 113 and 123 of the two rolling bearings 10 and 20 have a length that is longer in the axial direction than the inner rings 11 and 21, and the outer rings 113 and 123 are axially connected to each other. The inner rings 11 and 21 may be arranged to be spaced apart from each other in the axial direction.

  In this way, even if no spacer member is used, the difference in the length dimension between the inner rings 11 and 21 having a short axial length between the outer rings 113 and 123 having a long axial length. Accordingly, the preload can be easily applied to the two rolling bearings 10 and 20 by pressing the inner rings 11 and 21 in a relatively close direction.

  Further, as shown in FIG. 16, the inner rings 11 and 21 of the two rolling bearings 10 and 20 have a length that is longer in the axial direction than the outer rings 113 and 123 that overlap in the axial direction. May be arranged so as to be abutted against each other in the axial direction, and the outer rings 113 and 123 may be arranged apart from each other in the axial direction.

  In this case, a gap is formed between the outer rings 113 and 123 having a short axial length according to the difference in length between the inner rings 11 and 21 having a long axial length. The preload may be easily applied to the two rolling bearings 10 and 20 by pressing the 113 and 123 in a relatively close direction.

  Moreover, in the said 1st Embodiment, the rolling bearing apparatus 1 provided with the two rolling bearings 10 and 20 and the shaft 31 is illustrated, and in 2nd Embodiment, the rolling bearing apparatus 101 further provided with the sleeve 135 is illustrated. As described above, for example, the rolling bearing device may include the two rolling bearings 10 and 20 and the sleeve 135 without including the shaft 31.

  In this case, similarly to the second embodiment, the convex portions 113b and 123b may be provided on the outer peripheral surfaces of the outer rings 113 and 123. Moreover, what is necessary is just to apply the structure corresponding to the structure of the inner rings 11 and 21 which concern on the 1st modification of the said 1st Embodiment to the 7th modification to the outer rings 113 and 123. FIG.

  As mentioned above, although embodiment of this invention was explained in full detail with reference to drawings, the specific structure is not restricted to this embodiment, The design change etc. of the range which does not deviate from the summary of this invention are included. For example, the present invention is not limited to those applied to the above-described one embodiment and modifications, but may be applied to embodiments in which these embodiments and modifications are appropriately combined, and is not particularly limited. Absent.

  Further, for example, a convex portion may be provided on at least one of the inner peripheral surfaces of the inner rings 11, 21 of the rolling bearings 10, 20, and the outer peripheral surfaces of the outer rings 13, 23 (113, 123). For example, the first rolling The bearing 10 may be provided with a convex surface portion on the inner ring 11, and the second rolling bearing 20 may be provided with a convex surface portion on the inner ring 11. In addition, the first rolling bearing 10 is provided with a convex surface portion 11b on one side of the inner ring 11 in the axial direction, and the second rolling bearing 20 is provided with convex surface portions 21b on both ends of the inner ring 11 in the axial direction. Thus, an arbitrary position or an arbitrary number of convex surface portions in the axial direction of the inner and outer rings may be provided.

  Further, the example in which the swing arm 4 is swung by rotating the outer rings 13 and 23 with respect to the inner rings 11 and 21 fixed to the shaft 31 has been described above, but the outer ring is fixed and the swing arm is fixed to the shaft 31. It is good also as a structure which rotates an inner ring | wheel with respect to an outer ring | wheel by attaching 4 and swings a swing arm.

  In addition, an example in which two rolling bearings are configured by two inner rings and two outer rings that are arranged coaxially with an interval in the axial direction has been shown. However, two inner rings or two outer rings and a spacer member are integrated. A structure having a structure in which either one of the inner ring or the outer ring is formed of a single member and has two race rings may be used.

  For example, in the configuration of the first embodiment, as illustrated in FIG. 17, the outer rings 13 and 23 may be integrally formed in the axial direction. In this case, the inner rings 11 and 21 may be arranged so as to be separated from each other in the axial direction. In the configuration of the second embodiment, as shown in FIG. 18, the outer rings 113 and 123 are formed integrally with each other in the axial direction, and the inner rings 11 and 21 are spaced apart from each other in the axial direction. It is good. Moreover, as shown in FIG. 19, the inner rings 11 and 21 may be formed integrally with each other in the axial direction, and the outer rings 113 and 123 may be spaced apart from each other in the axial direction.

1,101 Rolling bearing device 2 Base housing (base member)
4 Swing arm 10 First rolling bearing 20 Second rolling bearing 11, 21 Inner ring 11a, 21a, 113a, 123a Reference surface portion 11b, 21b, 113b, 123b Convex surface portion 13, 23, 113, 123 Outer ring 15, 25 Rolling element 20 First 2 Rolling bearings 31 Shaft (shaft member)
31b Concave surface area 33 Spacer member 39 Adhesive 50 Pivot device 135 Sleeve (outer fitting member)
135a Fitting hole 135b Spacer part

Claims (44)

The inner ring and the outer ring arranged coaxially, and a plurality of rolling elements arranged in the annular space between the inner ring and the outer ring at intervals in the circumferential direction, are arranged with an interval in the axial direction 2 With two rolling bearings,
A shaft member fitted to the inner ring of the rolling bearing;
An outer fitting member having a fitting hole for fitting the outer ring of the rolling bearing;
At least one of the inner peripheral surface of the inner ring and the outer peripheral surface of the outer ring is composed of a reference surface portion and a convex surface portion that is disposed at at least one end in the axial direction and protrudes in the radial direction with respect to the reference surface portion,
A rolling bearing device in which the convex surface portion is fixed in a press-fitted state to the outer peripheral surface of the shaft member or the inner peripheral surface of the outer fitting member.   The rolling bearing device according to claim 1, wherein the convex surface portion is disposed on a rear end side in the fitting direction.   The rolling bearing device according to claim 1, wherein the convex surface portion is disposed at an end portion of the two rolling bearings on the side where inner rings or outer rings are close to each other.   The rolling bearing device according to claim 1, wherein the convex surface portions are arranged at both end portions in the axial direction of the inner ring and / or the outer ring.   The shaft member and / or the external fitting member facing the convex surface portion has a concave region that is recessed in a radial direction in a region facing either one of the convex surface portions disposed at both end portions in the axial direction. Item 5. The rolling bearing device according to Item 4.   The said reference surface part of the said inner ring | wheel and / or the said outer ring | wheel has the diameter dimension used as the non-contact with respect to the outer peripheral surface of the said shaft member, or the inner peripheral surface of the said external fitting member. The rolling bearing device described.   The rolling bearing device according to any one of claims 1 to 6, wherein the inner ring and / or the outer ring has a groove portion that is recessed in the radial direction in the vicinity of the convex surface portion of the reference surface portion.   The rolling bearing device according to any one of claims 1 to 7, wherein the convex surface portion and the shaft member and / or the outer fitting member are welded.   The reference surface part of the inner ring and / or the outer ring and the outer peripheral surface of the shaft member and / or the inner peripheral surface of the outer fitting member are fixed by an adhesive. Rolling bearing device.   The rolling bearing device according to claim 9, wherein the reference surface portion has a surface roughness larger than that of the convex surface portion.   The rolling bearing device according to any one of claims 1 to 10, wherein the outer fitting member includes a spacer portion that is sandwiched between the outer rings in the axial direction.   The rolling bearing device according to any one of claims 1 to 10, further comprising a spacer member sandwiched in an axial direction between the inner rings or the outer rings.   The inner ring or the outer ring of the two rolling bearings has a length dimension that is longer in the axial direction than the outer ring or the inner ring that overlaps in the axial direction, and the inner rings or the outer rings that are longer in the axial direction. 11. The outer rings or the inner rings having short axial lengths are disposed so as to be axially abutted with each other, and the inner rings are spaced apart from each other in the axial direction. Rolling bearing device.   The rolling bearing device according to claim 13, wherein inner rings or outer rings having a long axial length are integrally formed with each other in the axial direction. A rolling bearing device according to any one of claims 1 to 14,
A base member to which any one of the shaft member and the outer fitting member is fixed;
A pivot device comprising a swing arm attached to the other outer fitting member or the shaft member. The inner ring and the outer ring arranged coaxially, and a plurality of rolling elements arranged in the annular space between the inner ring and the outer ring at intervals in the circumferential direction, are arranged with an interval in the axial direction 2 With two rolling bearings,
A shaft member fitted to the two inner rings in a state where the outer rings of the two rolling bearings are abutted in the axial direction and the inner rings are spaced apart in the axial direction;
An inner peripheral surface of the inner ring is composed of a reference surface portion and a convex surface portion that is arranged at least at one end in the axial direction and protrudes in the radial direction with respect to the reference surface portion,
A rolling bearing device in which the convex portion is fixed to the outer peripheral surface of the shaft member in a press-fitted state.   The rolling bearing device according to claim 16, wherein the two outer rings are integrated as one member.   The rolling bearing device according to claim 16 or 17, wherein the convex surface portion is disposed on a rear end side in a fitting direction of the inner ring into which the shaft member is fitted.   The rolling bearing device according to claim 16 or 17, wherein the convex surface portion is disposed at an end portion on a side where inner rings of the two rolling bearings are close to each other.   The rolling bearing device according to claim 16 or 17, wherein the convex surface portions are disposed at both end portions in the axial direction of the inner ring.   The said shaft member has a concave surface area | region recessed in radial direction in the area | region facing either one of the said convex surface part arrange | positioned at the both ends of the axial direction of the said inner ring | wheel. Rolling bearing device.   The rolling bearing device according to claim 21, wherein the reference surface portion of the inner ring has a diameter dimension that is not in contact with the outer peripheral surface of the shaft member.   The rolling bearing device according to any one of claims 16 to 22, wherein the inner ring has a groove portion that is recessed in a radial direction in the vicinity of the convex surface portion of the reference surface portion.   The rolling bearing device according to any one of claims 16 to 23, wherein the convex surface portion and the shaft member are welded.   The rolling bearing device according to any one of claims 16 to 24, wherein the reference surface portion of the inner ring and an outer peripheral surface of the shaft member are fixed by an adhesive.   The rolling bearing device according to claim 25, wherein the reference surface portion has a surface roughness larger than that of the convex surface portion.   The rolling bearing device according to any one of claims 16 to 26, further comprising a spacer member sandwiched between the outer rings in the axial direction.   The outer ring of the two rolling bearings has a length dimension that is longer in the axial direction than the inner ring that overlaps in the axial direction, and is disposed such that the end faces in the axial direction directly abut each other. The rolling bearing device according to any one of 26. A rolling bearing device according to any one of claims 16 to 28;
A base member to which one of the shaft member and the outer ring is fixed;
A pivot device comprising a swing arm attached to the other outer ring or the shaft member. The inner ring and the outer ring arranged coaxially, and a plurality of rolling elements arranged in the annular space between the inner ring and the outer ring at intervals in the circumferential direction, are arranged with an interval in the axial direction 2 With two rolling bearings,
An outer fitting member having a fitting hole for fitting the two outer rings in a state where the inner rings of the two rolling bearings are abutted in the axial direction and the outer rings have a gap in the axial direction. ,
The outer peripheral surface of the outer ring is composed of a reference surface portion and a convex surface portion that is disposed at least at one end in the axial direction and protrudes in the radial direction with respect to the reference surface portion,
A rolling bearing device in which the convex portion is fixed to the inner peripheral surface of the outer fitting member in a press-fitted state.   The rolling bearing device according to claim 30, wherein the two inner rings are integrated as one member.   The rolling bearing device according to claim 30 or 31, wherein the convex surface portion is disposed on a rear end side in a fitting direction of the outer ring fitted to the outer fitting member.   32. The rolling bearing device according to claim 30, wherein the convex surface portion is disposed at an end portion on the side where the outer rings of the two rolling bearings are close to each other.   The rolling bearing device according to claim 30 or 31, wherein the convex surface portions are disposed at both end portions in the axial direction of the outer ring.   The rolling bearing device according to claim 34, wherein the outer fitting member has a concave surface region that is recessed in a radial direction in a region facing either one of the convex surface portions disposed at both end portions in the axial direction of the outer ring.   The rolling bearing device according to any one of claims 30 to 35, wherein the reference surface portion of the outer ring has a diameter dimension that makes no contact with the inner peripheral surface of the outer fitting member.   The rolling bearing device according to any one of claims 30 to 36, wherein the outer ring has a groove portion that is recessed in the radial direction in the vicinity of the convex surface portion of the reference surface portion.   The rolling bearing device according to any one of claims 30 to 37, wherein the convex surface portion and the outer fitting member are welded.   The rolling bearing device according to any one of claims 30 to 38, wherein the reference surface portion of the outer ring and an inner peripheral surface of the outer fitting member are fixed by an adhesive.   The rolling bearing device according to claim 39, wherein the reference surface portion has a surface roughness larger than that of the convex surface portion.   The rolling bearing device according to any one of claims 30 to 40, further comprising a spacer member sandwiched between the inner rings in the axial direction.   The inner ring of the two rolling bearings has a length dimension that is longer in the axial direction than the outer ring that overlaps in the axial direction, and is disposed such that the end faces in the axial direction directly abut each other. 40. The rolling bearing device according to any one of 40. A rolling bearing device according to any one of claims 30 to 42;
A base member to which either the inner ring or the outer fitting member is fixed;
A pivot device comprising: the other outer fitting member or a swing arm attached to the inner ring.   A rolling bearing used in the rolling bearing device according to any one of claims 1, 16, and 30.

Images