JP2018168992A - Double-row roller bearing - Google Patents

Abstract

To automatically adjust a clearance between a pocket of a holder and a rolling body in accordance with a rotation speed regarding a double-row roller bearing.SOLUTION: In a bearing 10, a clearance adjuster 16 movable in a radial direction of a pair of holders 14 is integrated between opposite surfaces of the holders 14, and the opposite surfaces are bridged by a spring 15 that energizes the holders 14 in such a direction that the holders get closer to each other. When a rotation speed of the bearing 10 is increased, the clearance adjuster 16 is moved outwards in the radial direction of the holders 14 by a centrifugal force. A wedge action that is performed between the clearance adjuster 16 and a tapered surface 14c on the opposite surface of the holder 14 causes the pair of holders 14 to move in such a direction that the holders are separated from each other, against the energization of the spring 15, thereby automatically reducing a clearance between a pocket of the holder 14 and the rolling body 13. When the rotation speed of the bearing 10 is decreased, the clearance adjuster 16 is moved inwards in the radial direction of the holder 14 and the pair of holders 14 are moved in such a direction that the holders get closer to each other according to the energization of the spring 15, thereby automatically enlarging the clearance between the pocket of the holder 14 and the rolling body 13.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a double row rolling bearing.

Double row roller bearings are used for rotation support parts of machine tools.
As in Patent Document 1, a general double row roller bearing includes an outer ring having a raceway surface formed on an inner diameter surface, an inner ring having a raceway surface formed on an outer diameter surface, a raceway surface of the outer ring, and a raceway surface of the inner ring. And a pair of cages that hold the rollers of each row in a rollable manner. The rollers are arranged in two rows in the width direction of the bearing.
Each cage has an annular portion and a column portion extending in the axial direction in parallel with the circumferential direction of the annular portion, and is assembled with the annular portion back-to-back between the inner diameter surface of the outer ring and the outer diameter surface of the inner ring. ing.
A space serving as a pocket is formed between the column portions adjacent to each other in the circumferential direction of the annular portion of each cage, and each roller is individually accommodated therein.

Here, the initial clearance from the pocket of the cage is set according to the rotational speed (the number of rotations) according to the use of the double row roller bearing.
In general, when the rotational speed is high, the rollers are likely to be skewed. Therefore, the clearance at the pocket of the cage is set to be relatively small in order to control the posture of the rollers. Further, when the rotational speed is low, the clearance is set to be relatively large in order to reduce the influence of rubbing or the like at the pocket of the cage.

JP 2011-231863 A

However, depending on the application, the rotational speed of the double row roller bearing may fluctuate during use, and the optimum clearance from the pocket of the cage may fluctuate every moment.
Further, even when the rotational speed of the double row roller bearing is constant, it is troublesome to adjust the clearance at the pocket of the cage each time according to the rotational speed in the specific application.
Such a problem is not limited to double row roller bearings, but is applicable to general double row roller bearings.

  Therefore, the problem to be solved by the present invention is to make it possible to automatically adjust the clearance between the cage pocket and the rolling element of the double row rolling bearing in accordance with the rotational speed.

In order to solve the above-described problems, a double row rolling bearing according to the present invention includes an outer ring having a raceway surface on an inner diameter surface, an inner ring having a raceway surface facing the raceway surface of the outer ring on an outer diameter surface, and a raceway of the outer ring. A plurality of rolling elements arranged in two rows between each raceway surface of the inner ring facing the surface, and an inner diameter surface of the outer ring and an outer diameter surface of the inner ring, and the rolling elements of each row are pocketed A pair of retainers that are rotatably held therein, a spring that is spanned between the pair of retainers and biases the pair of retainers in an approaching direction, and an opposing surface of the pair of retainers. And a clearance adjustment body that is incorporated and movable in the radial direction of the cage.
When the centrifugal force generated in proportion to the rotational speed of the cage increases, the clearance adjuster moves outward in the radial direction of the cage and is played between the opposing surfaces of the cage. When the pair of cages are moved away from each other against the urging force of the spring by the wedge action and the centrifugal force generated in proportion to the rotational speed of the cage is reduced, the inner diameter in the radial direction of the cage is reduced. It moves to direction, and it was set as the structure which moves the said pair of retainer to the direction which approaches according to the urging | biasing of the said spring.

When the rotational speed of the double row rolling bearing is high, the pair of cages move away from each other by the wedge action as the clearance adjuster moves outward in the cage radial direction. As a result, the wall surfaces of the pockets of the pair of cages approach the rolling elements held by the respective cages, so that the clearance between the pockets of the cage and the rolling elements is automatically reduced. Therefore, when the double row rolling bearing rotates at a high speed, the posture of the rolling element is stabilized, and rotational runout and vibration are suppressed.
When the rotational speed of the double row rolling bearing is low, the pair of cages move toward each other by the biasing force of the spring as the clearance adjuster moves inward in the cage radial direction. Thereby, the wall surfaces of the pockets of the pair of cages are separated from the rolling elements held by the respective cages, and the clearance between the pockets of the cage and the rolling elements is automatically increased. Therefore, when the double row rolling bearing rotates at a low speed, rubbing between the rolling element and the cage is suppressed.

In the double-row rolling bearing according to the invention, it is preferable that the opposed surfaces of the pair of cages have a tapered surface that is inclined so that a gap between the cages is narrowed outward in the radial direction of the cage. .
In this way, when the clearance adjustment body slides radially outward during the high-speed rotation of the cage, the clearance adjustment body pushes the tapered surface of each cage in the direction in which the pair of cages are separated from each other. Is exhibited well.

In the double-row rolling bearing according to the invention, the clearance adjustment body may be a sphere, and a plurality of the clearance adjustment bodies may be arranged in parallel in the circumferential direction of the pair of cages.
In this way, since the surface of each clearance adjustment body is smooth, it is possible to suppress malfunctions caused by the clearance adjustment body being caught on the opposing surface of the cage.

  In the double-row rolling bearing according to the invention, the clearance adjusting body is a single annular elastic body, and is configured to expand when the applied centrifugal force increases and reduce the diameter when the applied centrifugal force decreases. Can be adopted. In this way, the number of parts can be reduced.

In the double-row rolling bearing according to the invention, it is preferable that the opposing surfaces of the pair of cages have a configuration in which a concave portion and a convex portion are fitted to each other.
If it does in this way, a pair of cage | baskets will rotate substantially integrally by the fitting of an unevenness | corrugation, and the rotational speed will become the same. For this reason, a pair of cages rotate individually, and a phase shift occurs due to the difference in rotational speed, so that the spring spanned between the cages breaks or the clearance adjuster incorporated between the cages falls off. Is prevented.
Here, the spring can be bridged between the bottom of the concave portion of one cage and the top of the convex portion of the other cage.

In the double-row rolling bearing according to the present invention, the inner diameter surface of the outer ring or the outer diameter surface of the inner ring has an outer flange located at both ends in the width direction, and a center flange positioned at the center in the width direction, The height of the said center collar is lower than the height of the said outer collar, The clearance adjustment body integrated between the opposing surfaces of a pair of said holder | retainer can employ | adopt the structure located on the said center collar.
If it does in this way, interference with a clearance adjustment body, a holder | retainer, and a middle collar can be prevented. In addition, the amount of movement of the clearance adjustment body in the radial direction of the double row roller bearing can be set larger than in the case where the height of the center collar is the same as the height of the outer casing. It becomes possible to increase the adjustment amount of the clearance with the rolling elements.

In the double row rolling bearing according to the invention, the rolling element is a roller, and each of the cages is arranged in parallel with an annular portion positioned between the row of rollers, in a circumferential direction of the annular portion, and from the annular portion. A plurality of column portions extending toward the row of rollers, and pockets are formed between the column portions adjacent to each other in the circumferential direction of the annular portion, and the clearance adjuster includes a pair of retainers. It is preferable to adopt a configuration that is incorporated between opposing surfaces of the annular portion.
If it does in this way, adjustment of clearance with a pocket will become easy because the end face of the bottom of a pocket approaches and separates with movement of a cage.

  Since the double-row rolling bearing according to the invention is configured as described above, the clearance between the pocket of the cage and the rolling element can be automatically adjusted according to the rotational speed.

(A) of the double row roller bearing of the first embodiment is a partially enlarged cross-sectional view during low-speed rotation, and (b) is a partially enlarged cross-sectional view during high-speed rotation. Partially enlarged end view of the cage of the double row roller bearing of the first embodiment The partially expanded side view of the cage | basket of the double row roller bearing of 1st Embodiment Partially enlarged side view of the cage of the double row roller bearing of the second embodiment Partially enlarged sectional view of the double row roller bearing of the third embodiment Partially enlarged end view of the cage of the double row roller bearing of the third embodiment Partially enlarged sectional view of the double row roller bearing of the fourth embodiment

Hereinafter, embodiments of the present invention will be described with reference to the drawings.
A double-row roller bearing 10 of the first embodiment shown in FIGS. 1 to 3 includes an outer ring 11, an inner ring 12, a roller 13, a cage 14, a spring 15, and a clearance adjusting body 16, and is held. The clearance between the container 14 and the pocket 13 can be automatically adjusted according to the rotational speed.

As shown in FIG. 1, the outer ring 11 has a substantially cylindrical shape as a whole, and has two rows of raceway surfaces 11 a arranged in parallel in the width direction on the inner diameter surface thereof.
The outer ring 11 has a pair of outer flanges 11b projecting in the inner diameter direction at both ends in the width direction of the inner diameter surface, and an intermediate collar 11c projecting in the inner diameter direction on the boundary between the two raceway surfaces 11a of the inner diameter surface. have. As shown in the figure, in this embodiment, the height of the outer collar 11b and the middle collar 11c are equal. The outer collar 11b and the middle collar 11c prevent the rollers 13 from falling off.
In order to prevent interference with the roller 13 at the boundary between the outer flange 11b and the intermediate flange 11c and the raceway surface 11a.
The outer ring 11 is attached to a housing of a machine tool, for example.
Although the material of the outer ring | wheel 11 is not specifically limited, It can illustrate that it is metal.

As shown in FIG. 1, the inner ring 12 as a whole has a substantially cylindrical shape, and its diameter is smaller than that of the outer ring 11 and is arranged coaxially with the outer ring 11.
A single raceway surface 12 a facing the raceway surface 11 a of the outer ring 11 is formed on the outer diameter surface of the inner ring 12.
Unlike the outer ring 11, no flange is provided on the outer diameter surface of the inner ring 12.
The inner ring 12 is attached to, for example, a main shaft of a machine tool.
Although the material of the inner ring | wheel 12 is not specifically limited, It can illustrate that it is metal.

As shown in FIG. 1, each roller 13 has a substantially cylindrical shape as a whole.
The rollers 13 are located between the raceway surface 11 a of the outer ring 11 and the raceway surface 12 a of the inner ring 12, and correspond to the two rows of raceway surfaces 11 a of the outer ring 11 and are arranged in two rows in the width direction of the double row roller bearing 10. Are arranged. Further, the rollers 13 are arranged in parallel at equal intervals in the circumferential direction of the double row roller bearing 10.
Although the material of the roller 13 is not specifically limited, It can illustrate that it is metal.

As shown in FIGS. 1 to 3, the pair of cages 14 are assembled back-to-back in parallel in the width direction of the double row roller bearing 10 between the inner diameter surface of the outer ring 11 and the outer diameter surface of the inner ring 12. .
As shown in the figure, the pair of cages 14 are so-called comb cages having the same shape and each have a single annular portion 14a and a plurality of column portions 14b.
The substantially annular annular portion 14a in each cage 14 is disposed between the rows of the rollers 13 forming two rows, and faces the boundary of the two raceways 11a of the outer ring 11, that is, the intermediate collar 11c. It is out.
Each substantially prismatic column portion 14 b extends from the annular portion 14 a in the width direction of the double row roller bearing 10 and reaches the row of rollers 13.
Here, in one of the pair of cages 14, for one cage 14, the column portion 14 b extends only to one row on the adjacent side of the two rows of rollers 13, and about the other cage The column portion 14 b extends only toward the other row on the adjacent side of the two rows of rollers 13.
The tip of the pillar portion 14b of the cage 14, that is, the end opposite to the end connected to the annular portion 14a is a free end that is not connected to other members. This free end terminates on the raceway surface 11 a of the outer ring 11 and does not reach the outer flange 11 b of the outer ring 11.
The column portions 14 b are arranged in parallel at equal intervals in the circumferential direction of the double row roller bearing 10.
A space serving as a pocket is formed between the column portion 14b and the column portion 14b adjacent to each other in the circumferential direction of the annular portion 14a. Each roller 13 is accommodated in this pocket so that it can roll. A clearance is provided between the roller 13 and the pocket.

As shown in FIG. 1, the surface (back surface) of the annular portion 14 a that is not connected to the column portion 14 b is a facing surface that faces each other in the pair of cages 14.
As shown in FIGS. 1 and 2, a tapered surface 14 c that is arranged in parallel with a gap in the circumferential direction of the annular portion 14 a is formed in a radially outer region of the opposing surface of the annular portion 14 a.
As shown in FIG. 1, each tapered surface 14c is inclined in the radial direction of the annular portion 14a, and the direction of the inclination is such that the gap is narrowed outward in the radial direction between the pair of cages. ing. In other words, the annular portion 14a has a thickness that gradually increases outward in the radial direction at the location where the tapered surface 14c is provided.
As shown in FIG. 3, each tapered surface 14c is curved in an arc shape in the circumferential direction of the annular portion 14a. Thereby, the three-dimensional shape of each taper surface 14c is a concave partial conical shape in which the axial line coincides with the radial direction of the annular portion 14a.
On the other hand, the radially inner region of the opposing surface of the annular portion 14a is a flat surface. Moreover, the area | region between the taper surface 14c and the taper surface 14c which adjoin the circumferential direction among the area | regions on the radial direction outer side is also a flat surface.

The material of the cage 14 is not particularly limited, and examples thereof include synthetic resins, metals, and composites of synthetic resins and metals. However, synthetic resins are preferable because they are lightweight, inexpensive, and easy to process. Although the kind of synthetic resin is not specifically limited, As a resin excellent in durability, a polyamide resin, a polyether ether ketone resin, and a polyphenylene sulfide resin can be exemplified.
The manufacturing method of the retainer 14 is not particularly limited, and examples thereof include injection molding, punching (pressing), and cutting-out (milling). The annular portion 14a and the column portion 14b may be integrally formed, or may be combined and integrated after being formed separately.

As shown in FIG. 1, the spring 15 is stretched between the opposing surfaces of the annular portions 14 a of the pair of cages 14 between the inner diameter surface of the outer ring 11 and the outer diameter surface of the inner ring 12. By the spring 15, the pair of cages 14 is urged in directions toward each other.
As shown in FIGS. 2 and 3, the springs 15 are arranged in parallel in the circumferential direction of the annular portion 14a, and an end portion thereof is provided with a tapered surface 14c among the opposing surfaces of the annular portion 14a. It is fixed by an appropriate means in a region not in the radial direction. As illustrated, the phase of the tapered surface 14c parallel to the circumferential direction of the annular portion 14a and the spring 15 that is also parallel to the circumferential direction of the annular portion 14a are out of phase. The type and material of the spring 15 are not limited as long as the pair of cages 14 can be biased in the approaching direction.

As shown in FIGS. 1 to 3, the clearance adjustment body 16 has a substantially spherical shape, and the annular portions 14 a of the pair of cages 14 are opposed to each other between the inner diameter surface of the outer ring 11 and the outer diameter surface of the inner ring 12. It is incorporated between the tapered surfaces 14c formed on the surface. Due to the three-dimensional shape of the tapered surface 14c having a concave partial cone shape, the clearance adjusting body 16 can move in the radial direction of the annular portion 14a between the tapered surface 14c and the tapered surface 14c. It is impossible to move in the direction. The clearance adjustment body 16 rotates in the circumferential direction of the annular portion 14a at the same speed as the rotation speed of the cage 14 by being incorporated between the tapered surfaces 14c.
The clearance adjuster 16 is incorporated between the tapered surfaces 14c of the pair of cages 14 so as to be parallel to the circumferential direction of the annular portion 14a.

Here, the clearance adjusting body 16 incorporated between the tapered surfaces 14c of the cage 14 and the spring 15 spanned between the opposing surfaces of the cage 14 are out of phase in the circumferential direction of the annular portion 14a. In addition, since the positions do not overlap in the radial direction of the annular portion 14a, interference between the clearance adjustment body 16 and the spring 15 is prevented. Moreover, since the clearance adjustment body 16 is spherical, it is hard to unintentionally catch on the opposing surface of the holder | retainer 14, etc., and the malfunction is suppressed.
The material of the clearance adjustment body 16 is not particularly limited, and examples thereof include metals and resins. Examples of the metal include brass and iron, and examples of the resin include polyamide resin, polyether ether ketone resin, and polyphenylene sulfide resin. In addition, a ball for ball bearings can be used as the clearance adjuster 16.

  The configuration of the double row roller bearing 10 of the first embodiment is as described above, and when the rotational speed of the double row roller bearing 10 increases now, the centrifugal force generated in the clearance adjusting body 16 (the radial direction of the annular portion 14a). The outward force) increases in proportion to the rotational speed.

As long as the centrifugal force generated in the clearance adjusting body 16 is small, the clearance adjusting body 16 can overcome the force of the spring 15 because the clearance adjusting body 16 is interposed between the tapered surfaces 14c of the pair of cages 14 and is sandwiched by the force of the spring 15. Therefore, it cannot move radially outward of the annular portion 14a.
On the other hand, when the rotational speed of the double row roller bearing 10 exceeds a certain speed and the centrifugal force becomes greater than a certain level, the clearance adjusting body 16 overcomes the pinching force by the spring 15 and starts from the state of FIG. It moves outward in the radial direction of the annular portion 14a toward the state of FIG.

As the clearance adjuster 16 moves, a wedge action is generated between the retainer 14 and the tapered surface 14c, and the pair of retainers 14 are pushed away from each other. Thus, the pair of cages 14 moves in the width direction toward the width surface on the side where the double row roller bearing 10 is close to each other against the urging force of the spring 15.
The rollers 13 in the double row roller bearing 10 are regulated by the outer flange 11b and the intermediate flange 11c of the outer ring 11, and the position in the width direction is constant regardless of the rotational speed. From the state 1 (a) to the state shown in FIG. 1 (b), the end surface of the bottom 13 of the pocket approaches and the clearance with the pocket 13 decreases.
In this way, when the rotational speed of the double row roller bearing 10 is increased, the clearance of the pocket 13 is automatically reduced, the posture of the roller 13 is controlled, and rotational vibration and vibration are suppressed.

On the other hand, when the rotational speed of the double row roller bearing 10 decreases and falls below a certain speed, the centrifugal force generated in the clearance adjusting body 16 cannot overcome the pinching force by the spring 15, and FIG. The clearance adjustment body 16 moves inward in the radial direction of the annular portion 14a from the state toward the state of FIG.
As a result, the pressing force from the clearance adjusting body 16 due to the wedge action to the tapered surface 14c of the retainer 14 disappears, and the pair of retainers 14 is in the width direction of the double row roller bearing 10 according to the biasing force of the spring 15. Move toward each other.
Due to the movement of the cage, from the state of FIG. 1B toward the state of FIG. 1A, the end surface of the bottom 13 of the pocket is separated and the clearance with the pocket 13 is increased.
Thus, when the rotational speed of the double row roller bearing 10 is reduced, the clearance of the pocket 13 is automatically increased, and the friction between the roller 13 and the pocket of the cage 14 is suppressed.

The principal part of the double row roller bearing 10 of 2nd Embodiment is shown in FIG. Hereinafter, description of the same configuration as that of the first embodiment will be omitted.
In 2nd Embodiment, the convex part 14d and the recessed part 14e are provided in the opposing surface of the cyclic | annular part 14a of a pair of holder | retainer 14. FIG.

As shown in FIG. 4, the convex portions 14d and the concave portions 14e are alternately arranged in parallel in the circumferential direction of the annular portion 14a. The convex portions 14d protrude in the axial direction of the retainer 14, and the concave portions 14e. Is recessed in the axial direction of the cage 14.
The formation part in the opposing surface of the annular part 14a of the convex part 14d and the recessed part 14e is between the taper surface 14c and the taper surface 14c adjacent to the circumferential direction of the annular part 14a. Therefore, the clearance adjustment body 16 incorporated between the convex portion 14d and the concave portion 14e and the tapered surface 14c is out of phase in the circumferential direction of the annular portion 14a, and both are prevented from interfering with each other.

As shown in the figure, a pair of cages 14 includes a convex portion 14d of one cage 14 and a concave portion 14e of the other cage 14, and a concave portion 14e of one cage 14 and a convex portion of the other cage 14. 14d fit into each other.
Furthermore, between the opposing surfaces of the annular portion 14a of the pair of cages 14, a spring 15 is stretched between the top of the convex portion 14d and the bottom of the concave portion 14e.
When the double row roller bearing 10 is used, the pair of cages 14 rotate integrally due to the fitting of the convex portions 14d and the concave portions 14e. Therefore, unlike the case where the pair of cages rotate individually, the circumferential phase shifts with the difference in rotational speed, the spring 15 breaks, or the clearance adjuster 16 falls off between the tapered surfaces 14c. Is prevented.

5 and 6 show a double row roller bearing 10 of the third embodiment. Hereinafter, description of the same configuration as that of the first embodiment will be omitted.
In the third embodiment, the clearance adjustment body 16 is a single elastic body. The clearance adjusting body 16 is formed by winding a wire in a coil shape, and has an annular shape having substantially the same diameter as the annular portion 14 a of the cage 14. The clearance adjusting body 16 can be expanded and contracted due to its elasticity.

A tapered surface 14c continuous in the circumferential direction of the annular portion 14a is formed on the opposing surface of the annular portion 14a of the pair of cages 14, and a clearance adjusting body 16 is incorporated between the opposing tapered surfaces 14c. .
When the rotational speed of the double row roller bearing 10 is increased, the clearance adjusting body 16 is expanded in diameter by the centrifugal force generated in the whole, and the pair of cages 14 are pushed away from the pockets 13 and the pockets 13 and 13 are pushed away. The clearance becomes smaller. On the other hand, when the rotational speed of the double row roller bearing 10 is reduced, the clearance adjusting body 16 is reduced in diameter, the pair of cages 14 are brought closer to the bias of the spring 15, and the clearance from the pocket 13 is increased.

FIG. 7 shows a double row roller bearing 10 of the fourth embodiment. Hereinafter, description of the same configuration as that of the first embodiment will be omitted.
In the fourth embodiment, the height of the center rod 11c provided on the inner diameter surface of the outer ring 11 is smaller than the height of the outer rod 11b by h in the figure. That is, the inner diameter at the location where the outer ring 11 is provided with the intermediate collar 11c is larger than the inner diameter at the location where the outer collar 11b is provided.
Thus, by relatively reducing the height of the intermediate collar 11c, the function of preventing the roller 13 from falling off by the outer flange 11b is maintained, and interference between the intermediate collar 11c and the clearance adjuster 16 or the cage 14 is prevented. can do.
In addition, the movement space of the clearance adjustment body 16 in the radial direction of the retainer 14 is increased compared to the case where the intermediate flange 11c is the same height as the outer flange 11b, so that the movement distance of the clearance adjustment body 16 can be increased. it can. Therefore, the moving distance of the cage 14 in the width direction of the double row roller bearing 10 can be increased, and the adjustment amount of the clearance between the roller 13 and the pocket of the cage 14 can be increased.

  The embodiments disclosed herein are illustrative and non-restrictive in every respect. The scope of the present invention is defined by the terms of the claims, and includes all modifications and variations that fall within the scope of the claims and equivalents thereto.

For example, the configuration of the opposing surface of the cage 14 and the clearance adjustment body 16 is not limited to the embodiment as long as a wedge action is exerted between them.
The shape of the cage 14 is not limited to the comb shape of the embodiment, and may be a cage shape, for example.
The shapes of the outer ring 11 and the inner ring 12 are not limited to the embodiment, and for example, a hook may be provided on the inner ring 12 side.
A rolling element is not limited to the roller 13 of embodiment, A ball | bowl may be sufficient.

DESCRIPTION OF SYMBOLS 10 Double row roller bearing 11 Outer ring 11a Raceway surface 11b Outer flange 11c Middle flange 12 Inner ring 12a Raceway 13 Roller 14 Cage 14a Annular part 14b Pillar part 14c Tapered surface 14d Convex part 14e Concave part 15 Spring 16 Clearance adjustment body

Claims (8)

An outer ring having a raceway surface on the inner diameter surface;
An inner ring having a raceway surface facing the raceway surface of the outer ring on the outer diameter surface;
A plurality of rolling elements arranged in two rows between each raceway surface of the inner ring facing the raceway surface of the outer ring;
A pair of cages having a pocket that is incorporated between an inner diameter surface of the outer ring and an outer diameter surface of the inner ring and holds the rolling elements of each row in a rollable manner;
A spring spanned between the pair of cages and biasing the pair of cages in an approaching direction;
A clearance adjuster that is incorporated between opposing surfaces of the pair of cages and is movable in the radial direction of the cage;
The clearance adjuster is
When the centrifugal force generated according to the rotational speed of the cage increases, the pair of cages move due to a wedge action that moves outward in the radial direction of the cage and plays with the opposing surface of the cage. To move away from the bias of the spring,
When the centrifugal force generated according to the rotational speed of the cage decreases, the double row rolling moves inward in the radial direction of the cage and moves the pair of cages in the approaching direction according to the bias of the spring. bearing.   2. The double-row rolling bearing according to claim 1, wherein the opposing surfaces of the pair of cages have a tapered surface inclined so that a gap between the cages is narrowed outward in a radial direction of the cage.   The double-row rolling bearing according to claim 1 or 2, wherein the clearance adjusting body is a sphere, and a plurality of the clearance adjusting bodies are arranged in parallel in a circumferential direction of the pair of cages.   The double-row rolling according to claim 1 or 2, wherein the clearance adjusting body is a single annular elastic body, and expands when the applied centrifugal force increases and contracts when the applied centrifugal force decreases. bearing.   5. The double-row rolling bearing according to claim 1, wherein the opposing surfaces of the pair of cages have a concave portion and a convex portion that fit together.   The double row rolling bearing according to claim 5, wherein the spring is stretched between the bottom of the concave portion of one cage and the top of the convex portion of the other cage. The inner diameter surface of the outer ring or the outer diameter surface of the inner ring has an outer collar located at both ends in the width direction and a center collar located at the center in the width direction. Lower than the height of the outer fence,
The double row rolling bearing according to any one of claims 1 to 6, wherein a clearance adjusting body incorporated between opposing surfaces of the pair of cages is located on the intermediate collar. The rolling element is a roller,
Each of the cages is
An annular portion located between the rows of rollers, and
Parallel to the circumferential direction of the annular portion, and having a plurality of column portions extending from the annular portion toward the row of rollers,
A pocket for holding the roller is formed between the column portions adjacent to each other in the circumferential direction of the annular portion,
The double-row rolling bearing according to any one of claims 1 to 7, wherein the clearance adjusting body is incorporated between opposing surfaces of the annular portions of the pair of cages.

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