JP2024038786A - Self-aligning roller bearing - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a self-aligning roller bearing (a self-aligning roller bearing with a seal) which is usable at a higher speed while suppressing the wear of a real lip part by reducing the torque on the seal lip part.

SOLUTION: The self-aligning roller bearing having both axial end opening parts sealed by a sealing device includes an outer ring having a concave spherical surface shaped raceway surface on the inner diameter face, an inner ring having double-row concave spherical shaped raceway surfaces on the outer diameter face, barrel shaped rollers arranged in double rows between the raceway surface of the outer ring and the raceway surface of the inner ring and having rolling surfaces swollen into a spherical shape, and a cage rollably holding the barrel shaped rollers, the sealing device including a seal member having the seal lip part for sliding on a seal slide surface provided at the axial end of the inner ring. In order that the seal slide surface is arranged on the inner diameter side further than the rolling surface of the inner ring, a step part is provided between the seal slide surface and the rolling surface of the inner ring.

SELECTED DRAWING: Figure 1

COPYRIGHT: (C)2024,JPO&INPIT

Description

The present invention relates to a spherical roller bearing, and more particularly to a spherical roller bearing with a seal that seals openings at both axial ends with a sealing device.

Roller bearings include self-aligning roller bearings. This self-aligning roller bearing has two rows of raceway surfaces on the inner ring, a spherical raceway surface on the outer ring, and barrel-shaped rolling elements. Since the center of the outer ring raceway surface coincides with the center of the bearing, it has self-aligning properties and can be used even when the inner ring and outer ring are tilted due to installation errors in the housing or deflection of the shaft. This bearing has a large load capacity and is suitable for applications subject to vibration and shock loads. As a self-aligning roller bearing, as described in Patent Document 1 and Patent Document 2, there is a self-aligning roller bearing with a seal that seals openings at both axial ends with a sealing device.

As shown in FIG. 7, the self-aligning roller bearing described in Patent Document 1 has two rows of raceway surfaces 2, 2 on the inner ring 1, a spherical raceway surface 4 on the outer ring 3, and rolling elements on barrel-shaped rollers 5. It is a roller bearing and includes a seal 6 fitted to the end of the outer ring 3. In this case, the seal 6 has a lip 7 formed by fixing a rubber material 9 to a core bar 8 made of a metal plate.

The lip 7 of the seal 6 slides on an inner ring seal surface 10 provided at the axial end of the inner ring. This inner ring sealing surface 10 is a tapered surface whose diameter decreases from the inside of the bearing toward the outside of the bearing. In this case, a guide surface 12 of the retainer 11 is formed between the raceway surface 2 of the inner ring 1 and the inner ring seal surface 10. Therefore, the inner ring sealing surface 10 is continuously formed on the raceway surface 2 via the guide surface 12.

The self-aligning roller bearing described in Patent Document 2 also has, as shown in FIG. It is a roller bearing. However, the axial end of the inner ring 1 is provided with a flange 15 that bulges toward the outer diameter side, and the axial outer end of the flange 15 has a taper that decreases in diameter from the inside of the bearing toward the outside of the bearing. A surface is provided, and this tapered surface constitutes a seal sliding surface 10.

Japanese Patent Application Publication No. 2008-232324 Japanese Patent Application Publication No. 2010-190241

Regardless of whether it is described in Patent Document 1 or Patent Document 2, the seal sliding surface has a relatively large diameter. For this reason, the circumferential speed of the seal lip portion increases, the torque related to the seal lip portion increases, and the seal lip portion is prone to wear and heat generation.

In view of these circumstances, the present invention aims to reduce the torque applied to the seal lip portion, suppress the wear of the reel lip portion, and provide a self-aligning roller bearing (sealed self-aligning roller bearing) that can be used at higher speeds. roller bearings).

The self-aligning roller bearing of the present invention has an outer ring having a concave spherical raceway surface on its inner diameter surface, an inner ring having multiple rows of concave spherical raceway surfaces on its outer diameter surface, and a raceway surface of the outer ring and a raceway of the inner ring. The device includes barrel-shaped rollers arranged in a plurality of rows between the rollers and the rollers, the rolling surfaces of which are bulged into a spherical shape, and a cage that holds the barrel-shaped rollers so that they can roll freely, and seals the openings at both ends in the axial direction. The self-aligning roller bearing is sealed with A stepped portion is provided between the seal sliding surface and the rolling surface of the inner ring so that the surface is disposed on the inner diameter side of the rolling surface of the inner ring.

According to the self-aligning roller bearing of the present invention, the seal sliding surface is arranged between the seal sliding surface and the rolling surface of the inner ring so that the seal sliding surface is disposed on the inner diameter side of the rolling surface of the inner ring. Since the stepped portion is provided, the diameter of the seal sliding surface can be made smaller than that of a conventional seal sliding surface which is formed continuously with the raceway surface of the inner ring and has a relatively large diameter. Therefore, the circumferential speed of the seal lip portion is slower than in conventional sealed roller center bearings of this type.

A stepped portion is formed by forming a circumferential end surface extending in the radial direction between the seal sliding surface and the rolling surface in the inner ring, and the retainer extends in the radial direction on the outer side of the bearing. A squirrel cage comprising a radial annular part and a circumferential annular part extending from the outer diameter part of the annular part to the inside of the bearing, and in which the rollers are fitted into pockets provided in the circumferential annular shape so as to be able to roll freely. There may be. Therefore, the rollers can be stably held between the raceway surfaces without providing a flange portion for receiving the rollers on the inner ring.

In this case, it is preferable that the angle between the outer diameter surface connected to the rolling surface and the circumferential end surface of the inner ring is 90 degrees or less. By setting in this way, the width dimension (length in the bearing axial direction) of the seal sliding surface can be set large, and when the bearing is aligned, it can be stably used as a seal sliding surface.

The stepped portion is formed by providing a flange portion that bulges toward the outer diameter side between the seal sliding surface and the rolling surface in the inner ring, and the retainer is connected to the annular portion and the annular portion. The comb-shaped cage is provided with a plurality of pillar parts extending in the axial direction from the part, and the rollers are fitted into pockets formed between adjacent pillar parts along the circumferential direction so as to be freely rollable. Good too. The comb-shaped cage makes it suitable for double-row roller bearings.

At this time, it is preferable that the angle formed by the outer diameter surface of the flange and the bearing outer side end surface of the flange in the inner ring is 90 degrees or less. By setting in this way, the width dimension (length in the bearing axial direction) of the seal sliding surface can be set large, and when the bearing is aligned, it can be stably used as a seal sliding surface. Furthermore, even if a flange that bulges toward the outer diameter is provided between the seal sliding surface and the rolling surface, interference between the flange and the seal lip can be prevented when the bearing is aligned. .

Preferably, a recess is provided at a corner portion of the seal sliding surface on the inner side of the bearing. By providing the recessed portion in this manner, the grindability of the seal sliding surface is improved.

It is preferable that the average wall thickness of the end of the inner ring where the seal sliding surface is formed is 60% or more of the thickness of the thinnest part of the inner ring where the raceway surface is formed. If the average wall thickness of the inner ring end where the seal sliding surface is formed is small, the strength of the seal sliding surface may be poor. There may be cases where it becomes impossible to secure a flat surface for holding down. However, by setting it to 60% or more, it is possible to prevent the seal sliding surface from being deteriorated in strength and to effectively secure the width when attaching the bearing to the shaft.

Preferably, the seal sliding surface has a tapered shape whose diameter decreases from the inner side of the bearing toward the outer side of the bearing. In this way, by forming the tapered shape, it is possible to reduce the amount of change in the interference of the seal lip portion during alignment.

The seal sliding surface may have a spherical shape centered on the bearing center. By forming the bearing into a spherical shape centered on the center of the bearing, the interference of the seal lip when not aligned and the interference of the seal lip when aligned can be made constant.

Since the present invention can lower the circumferential speed of the seal lip, it reduces the torque applied to the seal lip, suppresses wear on the seal lip, and enables use at higher speeds than conventional methods could handle. We can provide sealed spherical roller bearings.

FIG. 2 is a sectional view of a first self-aligning roller bearing of the present invention. FIG. 2 is an enlarged sectional view of a main part of the self-aligning roller bearing shown in FIG. 1. FIG. FIG. 3 is a sectional view of a second self-aligning roller bearing of the present invention. FIG. 4 is an enlarged sectional view of essential parts of the self-aligning roller bearing shown in FIG. 3; 4 is a sectional view of a modification of the self-aligning roller bearing shown in FIG. 3. FIG. FIG. 2 is a cross-sectional view of a modification of the self-aligning roller bearing shown in FIG. 1; FIG. 2 is an enlarged sectional view of a main part of a conventional self-aligning roller bearing. FIG. 2 is an enlarged sectional view of a main part of another conventional self-aligning roller bearing.

FIG. 1 is a sectional view of a self-aligning roller bearing according to the present invention, which includes an outer ring 23 having a concave spherical raceway surface 22 on an inner diameter surface 21, and a plurality of rows of concave spherical raceway surfaces on an outer diameter surface 24. 25, 25, and the raceway surfaces 22 of the outer ring 23 and the raceway surfaces 25, 25 of the inner ring 26 are arranged in multiple rows, and the rolling surfaces 27a, 27a are spherically bulged in double rows (this 2 rows) of barrel-shaped rollers 27, 27, and a pair of cages 28, 28 that rotatably hold the barrel-shaped rollers 27, 27, and sealing devices S, S for openings 30, 30 at both axial ends. This is a self-aligning roller bearing that is sealed in a sealed manner.

In this case, each retainer 28, 28 has a radial annular portion 31, 31 extending in the radial direction on the outer side of the bearing (on the axial opening side), and a radial annular portion 31, 31 extending in the radial direction from the outer diameter portion of the annular portion 31, 31 to the inner side of the bearing. It is provided with circumferential direction annular portions 32, 32 extending in the direction. Pockets 33, 33 are provided in the circumferential annular portions 32, 32, and barrel-shaped rollers 27, 27 are fitted into the pockets 33 so as to be freely rollable. Therefore, the cage guide surface 34 is formed axially outward from the raceway surfaces 25, 25. The cages 28, 28 may be metal cages or resin cages.

The sealing device S includes a seal member 37 consisting of a core metal 35 and a seal body 36 made of an elastic material that covers the core metal 35. A seal lip portion 38 is formed at the inner end of the seal member 37 . The core bar 35 includes a body portion 35a extending in the radial direction, a piece portion 35b bent toward the bearing inner side provided at the outer diameter end of the body portion 35a, and a piece portion 35b bent toward the bearing inner side provided at the inner diameter end of the body portion 35a. It has an inclined piece part 35c which is inclined towards. The core metal 35 is press-formed from a steel plate having rust prevention ability, such as an austenitic stainless steel plate (JIS standard SUS304 series, etc.) or a cold-rolled steel plate subjected to rust prevention treatment (JIS standard SPCC series, etc.). It is formed.

The bent piece portion 35b is covered with a bulge 39 at the outer diameter side end of the seal body 36, and this bulge 39 is covered with a recess provided at the axial end of the inner diameter surface of the outer ring 23. It fits into the circumferential groove 40. Thereby, the seal member 37 is attached to the outer ring 23. Further, the seal lip portion 38 covering the inclined piece portion 35c slides on a seal sliding surface 41 provided at the axial end of the inner ring 26.

The seal member 37 is made of synthetic rubber such as NBR (acrylonitrile-butadiene rubber), for example. In addition to NBR, the material of the sealing member 37 may include HNBR (hydrogenated acrylonitrile-butadiene rubber), which has excellent heat resistance, EPM, EPDM (ethylene propylene rubber), etc., as well as heat and chemical resistance. Examples of the material include ACM (polyacrylic rubber), FKM (fluororubber), silicone rubber, etc., which have excellent properties.

A step portion 42 is provided between the seal sliding surface 41 and the rolling surface 25 of the inner ring 26, and the seal sliding surface 41 is set to be disposed on the inner diameter side of the rolling surface 25 of the inner ring 26. . In this case, the stepped portion 42 is formed by forming a circumferential end surface 43 extending in the radial direction between the seal sliding surface 41 and the rolling surface 25. Specifically, as shown in FIG. 2, the circumferential end surface 43 is formed between the cage guide surface 34 and the seal sliding surface 41. Then, the angle α between the circumferential end surface 43 and the cage guide surface 34 is set to 90° or less. In this embodiment, the angle is 90°.

In this case, the seal sliding surface 41 has a tapered shape that is inclined (diameter reduced) from the inner diameter end of the circumferential end surface 43 toward the outside of the bearing. The inclination angle θ of this seal sliding surface 41 is set, for example, to about 10° to 20°. The seal sliding surface 41 needs to be able to follow the operating range of the seal lip portion 38 during alignment. In other words, it is necessary to set the seal so that no gap is formed between the seal sliding surface 41 and the seal lip 38, and the seal lip 38 does not come into too much pressure contact with the seal sliding surface 41.

Furthermore, the average wall thickness of the inner ring end in the area where the seal sliding surface 41 is formed is set to be 60% or more of the thickness of the thinnest part of the inner ring 26 in the area where the raceway surface 25 is formed. . That is, as shown in FIG. 2, the average wall thickness of the inner ring end where the seal sliding surface 41 is formed is t, and the wall thickness of the thinnest part where the raceway surface 25 is formed is T. Then, t/T=60%. Here, the thinnest part is the thickness at the axial end 27a1 of the rolling surface 27a of the roller 27. Further, the length L of the seal sliding surface 41 needs to be long enough to follow the operating range of the seal lip portion during alignment.

According to the self-aligning roller bearing of the present invention, the seal sliding surface 41 and the rolling surface 25 of the inner ring 26 are arranged so that the seal sliding surface 41 is disposed on the inner diameter side of the rolling surface 25 of the inner ring 26. Since the stepped portion 42 is provided between the inner ring 26 and the raceway surface 25 of the inner ring 26, the diameter of the seal sliding surface 41 is smaller than that of the conventional seal sliding surface which is formed continuously with the raceway surface 25 of the inner ring 26 and has a relatively large diameter. It can be done. Therefore, the circumferential speed of the seal lip portion 38 is slower than in conventional sealed center roller bearings of this type.

Since the present invention can lower the circumferential speed of the seal lip portion 38, the torque applied to the seal lip portion 38 is reduced, the wear of the seal lip portion 38 is suppressed, and the present invention can be used at higher speeds than conventional methods. It is possible to provide a sealed spherical roller bearing that can be used.

In the embodiment shown in FIGS. 1 and 2, the stepped portion 42 is formed by forming a circumferential end surface 43 extending in the radial direction between the seal sliding surface 41 and the rolling surface 25 in the inner ring 26, The retainer 28 includes a radial annular part 31 extending in the radial direction on the outer side of the bearing, and a circumferential annular part 32 extending from the outer diameter part of the annular part 31 to the inside of the bearing. The cage is a cage-shaped cage in which the rollers are fitted into pockets 33 provided so as to be able to freely roll. Therefore, the barrel rollers 27 can be stably held between the raceway surfaces 22 and 25 without providing a flange portion for receiving the barrel rollers 27 on the inner ring 26.

Further, it is preferable that the angle α between the outer diameter surface 34 continuous with the rolling surface 25 and the circumferential end surface 43 of the inner ring 26 is 90° or less. By setting in this way, the width dimension (length in the bearing axial direction) of the seal sliding surface 41 can be set large, and the seal sliding surface 41 can stably respond when the bearing is aligned.

It is preferable that the average thickness of the end of the inner ring where the seal sliding surface 41 is formed is 60% or more of the thickness of the thinnest part of the inner ring where the raceway surface is formed. If the average wall thickness of the inner ring end where the seal sliding surface 41 is formed is small, the strength of the seal sliding surface 41 may be poor, and the flat part of the inner ring width surface (when installing the bearing on the shaft) There may be cases where it is not possible to secure a flat surface for holding down the width. However, by setting it to 60% or more, it is possible to prevent the seal sliding surface 41 from deteriorating in strength and to effectively secure the width when attaching the bearing to the shaft.

It is preferable that the seal sliding surface 41 has a tapered shape whose diameter decreases from the inner side of the bearing toward the outer side of the bearing. By forming the tapered shape in this way, it is possible to reduce the amount of change in the interference of the seal lip portion 38 during alignment.

Next, in the self-aligning roller bearing shown in FIG. The retainer 51 includes an annular portion 52 and a plurality of pillar portions 53 extending in the axial direction from the annular portion 52, and a pocket 54 formed between adjacent pillar portions 53 along the circumferential direction. This is a comb-shaped cage into which rollers 27 are fitted so as to be able to roll freely.

In this case, the retainer guide surface as shown in FIG. 1 etc. is not formed, but the flange portion 50 is provided at the guide surface forming portion in FIG. As shown in FIG. 4, an end surface 50a of this collar portion 50 on the outer side in the bearing axis direction constitutes a stepped portion 42. As shown in FIG. Also in this case, the seal sliding surface 41 has a tapered shape that is inclined (diameter reduced) from the inner diameter end of the circumferential end surface 43 toward the outside of the bearing. The inclination angle θ of this seal sliding surface 41 is set, for example, to about 10° to 20°. The angle β formed by the outer end surface 50a of the flange 50 in the bearing axial direction and the outer diameter surface 50b of the flange 50 is set to 90° or less. In this embodiment, the angle is 90°.

Furthermore, the average wall thickness of the inner ring end in the area where the seal sliding surface 41 is formed is 60% or more of the thickness of the thinnest part of the inner ring 26 in the area where the raceway surface 25 is formed. . That is, as shown in FIG. 2, the average wall thickness of the inner ring end where the seal sliding surface 41 is formed is t, and the wall thickness of the thinnest part where the raceway surface 25 is formed is T. Then, t/T=60%. Here, the thinnest part is the thickness at the axial end 27a1 of the rolling surface 27a of the roller 27. Further, the length L of the seal sliding surface 41 needs to be long enough to follow the operating range of the seal lip portion during alignment.

Therefore, even with the spherical roller bearings shown in FIGS. 3 and 4, the circumferential speed of the seal lip portion 38 can be lowered, similar to the spherical roller bearings shown in FIGS. 1 and 2. It is possible to provide a sealed self-aligning roller bearing that reduces the torque applied to the seal lip portion 38, suppresses wear of the seal lip portion 38, and can be used at higher speeds than conventionally possible. It can be effective.

Furthermore, by setting the angle β between the outer diameter surface 50b of the flange 50 and the bearing outer side end surface 50a of the flange 50 to 90° or less in the inner ring 26, self-aligning as shown in FIGS. 1 and 2 can be achieved. Similar to roller bearings, the width dimension (length in the axial direction of the bearing) of the seal sliding surface 41 can be set large, and the seal sliding surface 41 can stably respond when the bearing is aligned. Furthermore, even if the flange portion 50 that bulges toward the outer diameter side is provided between the seal sliding surface 41 and the rolling surface 25, the flange portion 50 and the seal lip portion 38 will disintegrate when the bearing is aligned. Interference can be prevented.

Also in this case, the average wall thickness of the inner ring end in the area where the seal sliding part 41 is formed is 60% or more of the thickness of the thinnest part of the inner ring 26 in the area where the raceway surface 25 is formed. Therefore, similar to the self-aligning roller bearings shown in FIGS. 1 and 3, it is possible to prevent the seal sliding surface 41 from deteriorating in strength and to effectively secure the width when installing the bearing on the shaft. . Further, by forming the seal sliding surface 41 into a tapered shape, it is possible to reduce the amount of change in the interference of the seal lip portion during alignment.

In the self-aligning roller bearing shown in FIG. 85°). In this way, by setting the angle to less than 90°, a wider width of the seal sliding surface 41 can be ensured. Further, a recessed portion 55 is provided at a corner portion of the seal sliding surface 41 on the inner side of the bearing. By providing the recessed portion 55 in this manner, the grindability of the seal sliding surface 41 is improved.

The other structure of the spherical roller bearing shown in FIG. 5 is the same as that of the spherical roller bearing shown in FIGS. 3 and 4, and the same members are designated by the same symbols as in FIGS. 3 and 4. and explain their explanations. Therefore, the spherical roller bearing shown in FIG. 5 has the same effect as the spherical roller bearing shown in FIGS. 3 and 4.

Next, the spherical roller bearing shown in FIG. 6 has the following features in the spherical roller bearing shown in FIGS. 1 and 2:
The seal sliding surface is spherical. Specifically, the seal sliding surface 41 has a smaller diameter at the outer end of the bearing than at the inner end of the bearing, and has a spherical shape with a radius of curvature R centered on the bearing center O (see FIG. 1). Good too. It has a spherical shape centered on the center of the bearing.

By forming the seal sliding surface 41 into a spherical shape centered on the bearing center, the interference of the seal lip portion 38 when not aligned and the interference of the seal lip portion when aligned are constant. can do.

The other configuration of the spherical roller bearing shown in FIG. 6 is the same as the configuration of the spherical roller bearing shown in FIGS. 1 and 2, and the same members are designated by the same symbols as in FIGS. 1 and 2. and explain their explanations. Therefore, the spherical roller bearing shown in FIG. 6 has the same effect as the spherical roller bearing shown in FIGS. 1 and 2.

Although the embodiments of the present invention have been described above, the present invention is not limited to the above embodiments and can be modified in various ways. For example, in the self-aligning roller bearing shown in FIGS. The angle α between the directional end surface 43 and the cage guide surface 34 may be an acute angle of less than 90 degrees as shown in FIG. 5, or it may have a recessed portion 55 as shown in FIG. Furthermore, the recessed portion 55 may also be provided in the self-aligning roller bearing shown in FIGS. 3 and 4. Furthermore, in the self-aligning roller bearings shown in FIGS. 3 and 4 and the self-aligning roller bearing shown in FIG. 5, the seal sliding surface 41 may have a spherical shape as shown in FIG. 6. Note that the seal sliding surface 41 may be a flat surface extending in the bearing axial direction without having a tapered shape.

21 Inner diameter surface 22 Raceway surface 23 Outer ring 24 Outer diameter surface 25 Rolling surface 26 Inner ring 27a Rolling surface 28 Cage 31 Radial annular portion 32 Circumferential annular portion 33 Pocket 37 Seal member 38 Seal lip portion 41 Seal sliding surface 42 Step portion 43 Circumferential end surface 50 Flange portion 50a End surface 51 Cage 52 Annular portion 53 Pillar portion 54 Pocket 55 Recessed portion O Bearing center S Sealing device

Claims (9)

An outer ring having a concave spherical raceway surface on the inner diameter surface, an inner ring having multiple rows of concave spherical raceway surfaces on the outer diameter surface, and multiple rows of raceways arranged between the outer ring raceway surface and the inner ring raceway surface. , a self-aligning roller bearing comprising barrel-shaped rollers with spherical rolling surfaces and a cage that holds the barrel-shaped rollers so that they can roll freely, and whose openings at both ends in the axial direction are sealed with a sealing device. There it is,
The sealing device includes a seal member having a seal lip portion that slides on a seal sliding surface provided at an axial end of the inner ring, and the seal sliding surface is arranged on the inner diameter side of the rolling surface of the inner ring. A self-aligning roller bearing characterized in that a stepped portion is provided between the seal sliding surface and the rolling surface of the inner ring. By forming a circumferential end surface extending radially between the seal sliding surface and the rolling surface in the inner ring, the stepped portion is formed, and the retainer is moved in the radial direction on the outer side of the bearing. A cage-shaped retainer comprising an extending radial annular part and a circumferential annular part extending from the outer diameter part of the annular part to the inside of the bearing, and in which the rollers are fitted into pockets provided in the circumferential annular part so as to be freely rollable. The self-aligning roller bearing according to claim 1, wherein the self-aligning roller bearing is a roller bearing. 3. The self-aligning roller bearing according to claim 2, wherein the angle formed between the outer diameter surface connected to the rolling surface and the circumferential end surface of the inner ring is 90 degrees or less. The stepped portion is formed by providing a flange portion that bulges toward the outer diameter side between the seal sliding surface and the rolling surface in the inner ring, and the retainer is connected to the annular portion and the annular portion. A comb-shaped cage is provided with a plurality of pillar parts extending in the axial direction from the part, and the rollers are fitted into pockets formed between adjacent pillar parts along the circumferential direction so as to be freely rollable. The self-aligning roller bearing according to claim 1. 5. The self-aligning roller bearing according to claim 4, wherein in the inner ring, an angle between an outer diameter surface of the flange and a bearing outer end surface of the flange is 90 degrees or less. The self-aligning roller bearing according to claim 1, wherein a recessed portion is provided at a corner portion of the seal sliding surface on the inner side of the bearing. The average wall thickness of the end of the inner ring where the seal sliding surface is formed is 60% or more of the thickness of the thinnest part of the inner ring where the raceway surface is formed. The self-aligning roller bearing according to claim 1. The self-aligning roller bearing according to claim 1, wherein the seal sliding surface has a tapered shape whose diameter decreases from the inner side of the bearing toward the outer side of the bearing. The self-aligning roller bearing according to claim 1, wherein the seal sliding surface has a spherical shape centered on the bearing center.

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