JP2006029539A - Self-aligning roller bearing - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a self-aligning roller bearing with an outer ring and an inner ring free of great inclination when slight moment load works. <P>SOLUTION: The self-aligning roller bearing 10 comprises the outer ring 11 having outer ring raceway surfaces 12, 13 on the inner peripheral face in double row, the inner ring 14 having inner ring raceway surfaces 15, 16 on the outer peripheral face in double row, and a plurality of rollers 17 arranged between both raceway surfaces 12, 13 and 15, 16 in double row. Working points on the outer ring raceway surfaces 12, 13 in double row are located distant from each other. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a self-aligning roller bearing.

  In general, spherical roller bearings prevent the occurrence of abnormal loads and increase the radial load capacity because the contact state of the rollers does not change even when the outer ring or inner ring is inclined due to mounting errors or impact loads. be able to. For example, a conventional self-aligning roller bearing is known in which the alignment centers of a pair of outer rings are aligned and arranged symmetrically via a spacer (see, for example, Patent Document 1).

  As shown in FIG. 9, spherical roller bearings 100 described in Patent Document 1 are formed with spherical outer ring raceway surfaces 101 a and 102 a having the same curvature as the rollers 103 on the inner circumferential surfaces of a pair of outer rings 101 and 102. And arranged symmetrically with the spacer 104 in between. Further, spherical inner ring raceway surfaces 105 a and 106 a having the same curvature as the roller 103 are also formed on the outer peripheral surfaces of the inner rings 105 and 106. The width of the spacer 104 is set so that the alignment center P of the pair of outer rings 101 and 102 coincides on the axis.

  In such a self-aligning roller bearing 100, the outer ring raceway surfaces 101 a and 102 a of the outer rings 101 and 102 are formed only on necessary portions on both sides of the spacer 104, which affects the thickness of the spacer 104. In addition, the radius of curvature of the outer ring raceway surfaces 101a and 102a can be increased to expand the minimum inner diameter of the outer rings 101 and 102. Thereby, the width of the entire bearing is increased to increase the width of the roller 103, thereby increasing the load applied to the bearing.

  As a conventional rolling bearing, a roller bearing is known which has a high load capacity, misalignment and axial displacement allowance, and a good bearing life (for example, see Patent Document 2).

  As shown in FIG. 10, the roller bearing 110 described in Patent Document 2 has substantially the same radius of curvature R of the raceways 111 a and 112 a and 113 of the outer ring 111 and the inner ring 112, and the radius of curvature R is the outer raceway surface. The distance between 111a and the bearing axis 114 is made larger, and the relationship between the curvature radius R of the roller 113 and the length la of the 113 is R / la <20.

Further, as a conventional rolling bearing, there is known a self-aligning rolling bearing comprising a combination of a self-aligning roller bearing and a self-aligning ball bearing in which rollers and balls are sequentially arranged in the circumferential direction (for example, And Patent Document 3).
Japanese Utility Model Publication No. 05-0899947 (page 4-5, FIG. 1) JP 10-500199 (page 4-6, FIG. 1) DE10225572A1

  By the way, in the self-aligning roller bearing 100 described in Patent Document 1, the action point position of the outer ring raceway surface 101a in the right row and the action point position of the outer ring raceway surface 102a in the left row coincide with each other. Even if a slight moment load is applied, the outer rings 101 and 102 and the inner rings 105 and 106 are greatly inclined.

  On the other hand, the roller bearing 110 described in Patent Document 2 has an allowable tilt angle within a certain range. However, unlike Patent Document 1, the outer ring 111 and the inner ring 112 do not tilt significantly even when a slight moment load is applied. . However, such a roller bearing 110 has a large axial clearance and cannot be used as a fixed-side bearing.

  The present invention has been made in view of the above circumstances, and an object thereof is to provide a self-aligning roller bearing in which an outer ring and an inner ring do not greatly tilt when a slight moment load is applied. .

The above object of the present invention is achieved by the following configurations.
(1) An outer ring in which a spherical outer ring raceway surface is provided in a double row on the inner peripheral surface, an inner ring in which a spherical inner ring raceway surface is provided in a double row on the outer peripheral surface, and between both raceway surfaces of the double row A self-aligning roller bearing provided with a plurality of rollers
A self-aligning roller bearing characterized in that the position of the action point of the double row outer ring raceway surface has a distance.
(2) When the distance between the center position of the self-aligning roller bearing and the working point position of the outer ring raceway surface is L, the contact angle is α, and the radius of the outer ring raceway surface is R,
−R · sin α ≦ L ≦ 0.312R and L ≠ 0
The self-aligning roller bearing according to (1), wherein:
(3) The automatic adjustment according to (1) or (2), wherein the rollers arranged in the double row are arranged asymmetrically, and a center flange is provided between the inner ring raceway surfaces of the double row. Center roller bearing.
(4) The self-aligning roller bearing according to any one of (1) to (3), wherein the outer ring is divided into two.
(5) The self-aligning roller bearing according to (4), wherein a spacer is provided between the two outer rings.
(6) The self-aligning roller bearing according to (4) or (5), wherein the outer ring divided into two is coupled by a pin.

  According to the self-aligning roller bearing of the present invention, since the action point positions of the double row outer ring raceway surfaces are arranged with a distance, the inclination with respect to the moment load is limited. Therefore, when a moment load is applied, the conventional spherical roller bearing cannot support the moment load, and the outer ring and the inner ring are greatly inclined. However, in the spherical roller bearing of the present invention, the inner ring and the outer ring As a result, a radial load is generated in the right and left rows due to the inclination angle, and the outer ring and the inner ring do not tilt significantly. Further, since only a part of the conventional spherical roller bearing is improved, the spherical roller bearing of the present invention can be used as a fixed side bearing.

  Hereinafter, the self-aligning roller bearing according to each embodiment of the present invention will be described in detail with reference to the drawings.

(First embodiment)
FIG. 1 is a half sectional view showing a self-aligning roller bearing according to a first embodiment of the present invention, FIGS. 2 and 3 are explanatory views of functions when assembled in the self-aligning roller bearing of this embodiment, and FIG. It is a schematic diagram which determines an action point position.

  As shown in FIG. 1, the self-aligning roller bearing 10 of the first embodiment includes a single outer ring 11 having double-row outer ring raceway surfaces 12 and 13 inclined in a concave spherical shape on the inner peripheral surface, and an outer peripheral surface. A single inner ring 14 having double-row inner ring raceway surfaces 15, 16 inclined in a concave spherical shape, between the outer ring raceway surface 12 and the inner ring raceway surface 15, and between the outer ring raceway surface 13 and the inner ring raceway surface 16. A plurality of symmetrically arranged spherical rollers 17 having a contact angle α between them, and a pair of annular cages 18 and 19 incorporated in a bearing space between the outer ring 11 and the inner ring 14. ing. The self-aligning roller bearing 10 is lubricated by grease (not shown) sealed in the bearing space or by lubricating oil supplied from the oil hole of the outer ring 11.

  A housing 25 (see FIG. 2) is fitted on the outer peripheral surface of the outer ring 11, and a shaft 26 (see FIG. 2) is fitted on the inner diameter surface of the inner ring 14. The outer ring 11 is formed with a plurality of oil holes 20 in the circumferential direction at the center. The cages 18 and 19 are steel plate press cages or machined cages, and are pockets corresponding to the shape of the spherical rollers 17 so that the spherical rollers 17 can be inserted and held freely. A plurality of 21 and 22 are formed in the circumferential direction.

  The outer ring raceway surfaces 12 and 13 of the outer ring 11 have respective action point positions O1 and O2 that are intersections between the center of the force acting between the spherical roller 17 and the outer ring raceway surfaces 12 and 13 and the axial center line C. The distance 2L is arranged through the center position O. For this reason, even when a slight moment load is applied during assembly, radial loads are generated in the right row and the left row due to the inclination angles of the outer ring 11 and the inner ring 14, and the outer ring 11 and the inner ring 14 are not greatly inclined. Further, since the distance 2L is small, the spherical roller bearing 10 can have a certain range of allowable inclination angles such as 1 ° to 2.5 °.

  Table 1 shows the characteristics of the conventional self-aligning roller bearing described in Patent Document 1, the conventional roller bearing described in Patent Document 2, and the self-aligning roller bearing of the present invention.

  Conventional spherical roller bearings can be used on the fixed side and have good alignment, but tilt with a slight moment load. In addition, the conventional roller bearing cannot be used as a fixed-side bearing, although it does not tilt with a slight moment load. On the other hand, the self-aligning roller bearing 10 of the present embodiment has a certain degree of alignment, has good utilization as a fixed-side bearing, and does not tilt even with a slight moment load. Therefore, it is remarkable that it is superior to the above-mentioned conventional self-aligning roller bearings and roller bearings.

  As shown in FIG. 2, when the shaft 26 is assembled loosely into the inner ring of the self-aligning roller bearing after the self-aligning roller bearing is assembled to the housing 25, the shaft 26 hits the self-aligning roller bearing. However, in the conventional spherical roller bearing, the inner ring and the outer ring are greatly inclined, and the shaft 26 cannot be incorporated into the spherical roller bearing. On the other hand, since the self-aligning roller bearing 10 of the present embodiment has moment rigidity, the outer ring 11 and the inner ring 14 are only tilted in the clearance range, so that the shaft 26 is incorporated into the self-aligning roller bearing 10 as it is. Is possible.

  On the other hand, when the outer ring of the self-aligning roller bearing integrated with the shaft 26 is assembled loosely into the housing 25 after the shaft 26 is assembled to the self-aligning roller bearing, as shown in FIG. When the spherical roller bearing comes into contact with one side, in the conventional spherical roller bearing, the inner ring and the outer ring are greatly inclined, and the spherical roller bearing cannot be incorporated. On the other hand, since the self-aligning roller bearing 10 in this embodiment has moment rigidity, the outer ring 11 and the inner ring 14 are only tilted within the clearance, so that the shaft 26 integrated with the self-aligning roller bearing 10 is provided. Can be incorporated into the housing 25 as they are. As described above, the self-aligning roller bearing 10 according to the present embodiment has a good assembling property when assembled to the housing 25 and the shaft 26.

  Further, as shown in FIG. 4, each distance L between the center position O of the self-aligning roller bearing and the operating point position of the outer ring raceway surface is a margin that the spherical roller 17 does not protrude when the inner ring 14 is tilted. It is determined in consideration of cost. That is, when the self-aligning roller bearing of this embodiment has the same margin as the conventional self-aligning roller bearing in which the action point positions O1 and O2 are at the center position O, the inclination angle that does not protrude is the conventional bearing. L is determined to be in a range having 95% or more of the inclination angle that does not protrude.

Here, the inclination margin on the outer ring side in the conventional spherical roller bearing is Rθ (θ: allowable inclination angle, R: outer ring groove radius), and the outer ring 11 side in the spherical roller bearing 10 of the first embodiment. When the tilt margin is R′θ ′ (θ ′: allowable tilt angle, R ′: distance from the bearing center to the outer ring end face),
Rθ = R′θ ′ (1)
It becomes.
Here, since θ ′ / θ is desirably 0.95 or more,
θ ′ / θ = R / R ′ ≧ 0.95 (2)
Is given.

On the other hand, from the geometrical relationship, if the contact angle is α,
R ′ = (L ² + R ² −LR cos (π / 2 + α)) ^1/2 (3)
And
R ′ ² ≧ L ² + R ² (4)
From equation (2), 1−L ² / R ² ≧ R ² / R ′ ² ≧ 0.95 ² = 0.9025
≦ L ≦ 0.312R ′ ≒ 0.312R (5)
When the action lines cross, θ ′ / θ = R / R ′> 1 always holds because of the allowance. In addition, the maximum absolute value of L is geometrically R · sinα,
−R · sin α ≦ L (6)
It becomes.

Accordingly, each distance L between the center position O and the action point positions O1 and O2 of the double-row outer ring raceway surfaces 12 and 13 is expressed as follows.
−R · sin α ≦ L ≦ 0.312R and L ≠ 0 (7)
There is a relationship that satisfies. Thereby, the self-aligning roller bearing 10 can have an allowable inclination angle within a certain range while the outer ring 11 and the inner ring 14 are not greatly inclined when a slight moment load is applied.

  As described above, according to the self-aligning roller bearing 10 of the first embodiment, since the action point positions O1 and O2 of the double-row outer ring raceway surfaces 12 and 13 are arranged with a distance 2L, the moment When a load is applied, the conventional self-aligning roller bearing cannot support the moment load and the inner ring and the outer ring are largely inclined. However, depending on the inclination angle between the outer ring 11 and the inner ring 14, the right row and the left A radial load is generated in the row, and the outer ring 11 and the inner ring 14 can be prevented from being greatly inclined. Further, since the distance 2L of the action point positions O1 and O2 of the double-row outer ring raceway surfaces 12 and 13 is small, a certain range of allowable inclination angles can be maintained. Furthermore, since only a part of the conventional spherical roller bearing is improved, it can be used as a fixed side bearing.

  Further, according to the self-aligning roller bearing 10 of the first embodiment, the outer ring raceway surfaces 12 and 13 have the action point positions O1 and O2 in which −R · sin α ≦ L ≦ 0.312R and L ≠ 0. The outer ring 11 and the inner ring 14 can be prevented from being largely inclined when a slight moment load is applied, and a certain range of allowable inclination angles can be maintained.

FIG. 1 shows the case where the spherical rollers are arranged symmetrically at the contact angle α, but when the spherical rollers are arranged asymmetrically so that the contact angles are different from α ₁ and α ₂ in each row, In applying the above equation (7), the larger contact angle is used.

(Second Embodiment)
Next, the self-aligning roller bearing of the second embodiment will be described with reference to FIG.
FIG. 5 is a half sectional view of the self-aligning roller bearing according to the second embodiment of the present invention. Note that the same or equivalent parts as those in the first embodiment are denoted by the same reference numerals, and description thereof is omitted or simplified.

  As shown in FIG. 5, in the self-aligning roller bearing 30 of the second embodiment, the action lines on the outer ring raceway surfaces 12 and 13 of the outer ring 11 intersect, and the action point positions O1 and O2 on the axis center line C. Are arranged with a distance 2L via the center position O. Each distance L between the center position O and the action point positions O1 and O2 of the outer ring raceway surfaces 12 and 13 is set to −R · sin α ≦ L ≦ 0.312R and L ≠ 0.

  According to the self-aligning roller bearing 30 of the second embodiment, even when the action lines of the double-row outer ring raceway surfaces 12 and 13 intersect, the action point positions O1 and O1 of the outer ring raceway surfaces 12 and 13 are obtained. Since O2 is arranged with a distance of 2L, when a moment load is applied, a radial load is generated in the right row and the left row due to the inclination angle between the outer ring 11 and the inner ring 14, and the outer ring 11 and the inner ring 14 Can be prevented from tilting greatly. Further, since the distance 2L of the action point positions O1 and O2 of the double-row outer ring raceway surfaces 12 and 13 is small, an allowable inclination angle within a certain range can be maintained. Furthermore, since only a part of the conventional spherical roller bearing is improved, it can be used as a fixed side bearing.

In addition, according to the self-aligning roller bearing 30 of the second embodiment, the outer ring raceway surfaces 12 and 13 have the action point positions O1 and O2 in which −R · sin α ≦ L ≦ 0.312R and L ≠ 0. The outer ring 11 and the inner ring 14 can be prevented from being largely inclined when a slight moment load is applied, and a certain range of allowable inclination angles can be maintained.
Other configurations and operations are the same as those in the first embodiment.

(Third embodiment)
Next, a self-aligning roller bearing according to a third embodiment will be described with reference to FIG.
FIG. 6 is a half sectional view of a self-aligning roller bearing according to a third embodiment of the present invention. Note that the same or equivalent parts as those in the first embodiment are denoted by the same reference numerals, and description thereof is omitted or simplified.

  As shown in FIG. 6, in the self-aligning roller bearing 40 of the third embodiment, the left-side spherical roller 17 and the asymmetrical spherical roller 41 are incorporated in the right row. For this reason, the outer ring raceway surface 12 of the outer ring 11 and the inner ring raceway surface 15 of the inner ring 14 in the left row, and the outer ring raceway surface 13 of the outer ring 11 and the inner ring raceway surface 16 of the inner ring 14 in the right row are the spherical rollers 17, 41. Depending on the shape of the rolling surface, each is formed asymmetrically.

  Further, the self-aligning roller bearing 40 of the present embodiment also has a distance L1 + L2 between the action point positions O1 and O2 of the outer ring raceway surfaces 12 and 13, but the center ring O of the self-aligning roller bearing 40 and the outer ring in the left row. A distance L1 between the contact point position O1 of the raceway surface 12 and a distance L2 between the center position O and the action point position O2 of the outer ring raceway surface 13 in the right row are different from each other. However, the distances L1 and L2 between the center position O and the action point positions O1 and O2 of the outer ring raceway surfaces 12 and 13 in each row are also −R · sin α ≦ L1, L2 ≦ 0.312R and L1, L2 ≠ 0 is set.

  Further, an intermediate collar 42 is provided between the double row inner ring raceway surfaces 15 and 16. The intermediate collar 42 restricts the movement of the left side spherical roller 17 and the right side spherical roller 41 in the axial direction.

  According to the self-aligning roller bearing 40 of the third embodiment, even if the action point positions O1, O2 of the double-row outer ring raceway surfaces 12, 13 are asymmetric, the action point positions O1, O1 of the outer ring raceway surfaces 12, 13 are asymmetric. Since O2 is arranged with a distance L1 + L2, when a moment load is applied, a radial load is generated in the right row and the left row due to the inclination angle between the outer ring 11 and the inner ring 14, and the outer ring 11 and the inner ring 14 Can be prevented from tilting greatly. In addition, the movement of the spherical rollers 17 and 41 in the axial direction is also restricted by the center flange 42 provided between the double-row inner ring raceway surfaces 15 and 16, and when a slight moment load acts, the outer ring 11 and A large inclination of the inner ring 14 can be suppressed. Furthermore, since the distances L1 + L2 of the action point positions O1 and O2 of the double-row outer ring raceway surfaces 12 and 13 are small, a certain range of allowable inclination angles can be maintained. Further, since only a part of the conventional spherical roller bearing is improved, it can be used as a fixed side bearing.

Further, according to the self-aligning roller bearing 40 of the third embodiment, the outer ring raceway surfaces 12 and 13 have the points of action where -R · sin α ≦ L1, L2 ≦ 0.312R and L1, L2 ≠ 0. It is arranged with a distance L1 + L2 between the positions O1 and O2, and when a slight moment load is applied, the outer ring 11 and the inner ring 14 can be prevented from being greatly inclined, and a certain range of allowable inclination angles can be maintained. it can.
In this embodiment, the right and left rows of the spherical rollers 17 and 41 themselves are made asymmetrical, but the same spherical rollers may be arranged asymmetrically in the right and left rows.
Other configurations and operations are the same as those in the first embodiment.

(Fourth embodiment)
Next, a self-aligning roller bearing according to a fourth embodiment will be described with reference to FIG.
FIG. 7 is a half sectional view of a self-aligning roller bearing according to a fourth embodiment of the present invention. In addition, about the same or equivalent part as 3rd Embodiment, the same code | symbol is attached | subjected and description is abbreviate | omitted or simplified.

  As shown in FIG. 7, in the self-aligning roller bearing 50 of the fourth embodiment, a spacer 53 is arranged between outer rings 51 and 52 divided into two, and the spacer 53 includes two outer rings 51 and 52. Are connected to each other through a pin 54. The shapes of the outer ring raceway surface 12 of the outer ring 51 and the outer ring raceway surface 13 of the outer ring 52 and the shapes of the inner ring 14 and the spherical rollers 17 and 41 are configured in the same manner as in the third embodiment.

  According to the self-aligning roller bearing 50 of the fourth embodiment, even when the spacer 53 is assembled between the outer rings 51 and 52 divided into two, the position of the action point of the outer ring raceway surfaces 12 and 13 is obtained. Since O1 and O2 are arranged with a distance L1 + L2, when a moment load is applied, a radial load is generated in the right row and the left row due to the inclination angle between the outer ring 11 and the inner ring 14, and the outer ring 11 and The inner ring 14 can be prevented from being greatly inclined. Further, since the distances L1 + L2 of the action point positions O1, O2 of the double-row outer ring raceway surfaces 12, 13 are small, a certain range of allowable inclination angles can be maintained. Furthermore, since only a part of the conventional spherical roller bearing is improved, it can be used as a fixed side bearing.

Further, since the two outer rings 51 and 52 are coupled by the pin 54 via the spacer 53, for example, the shaft 26 integrated with the self-aligning roller bearing is attached to the housing 25 as shown in FIG. When assembled, the outer rings 51 and 52, the inner ring 14, the spherical rollers 17 and 41, and the cages 18 and 19 connected by the pin 54 can be integrated as a unit.
Other configurations and operations are the same as those of the third embodiment.

(Fifth embodiment)
Next, a self-aligning rolling bearing of a fifth embodiment will be described with reference to FIG.
FIG. 8 is a partially broken external perspective view of a self-aligning rolling bearing of a fifth embodiment according to the present invention. In addition, the same code | symbol is attached | subjected about the same or equivalent part as 1st-4th embodiment, and description is abbreviate | omitted or simplified.

  As shown in FIG. 8, the self-aligning rolling bearing 60 of the fifth embodiment is a combination of a self-aligning ball bearing and the self-aligning roller bearings of the first to fourth embodiments. The self-aligning rolling bearing 60 includes a single outer ring 11 having double-row outer ring raceway surfaces 12 and 13 inclined in a concave spherical shape on the inner peripheral surface, and a double-row inner ring raceway inclined in a concave spherical shape on the outer peripheral surface. A single inner ring 14 having surfaces 15, 16, between the outer ring raceway surface 12 of the outer ring 11 and the inner ring raceway surface 15 of the inner ring 14, and between the outer ring raceway surface 13 of the outer ring 11 and the inner ring raceway surface 16 of the inner ring 14. A plurality of spherical rollers 17, balls 61, 61 arranged in between, and an annular machined cage 62 incorporated in a bearing space between the outer ring 11 and the inner ring 14 are provided.

  The left column consisting of a plurality of spherical rollers 17 and balls 61, 61 arranged between the outer ring raceway surface 12 of the outer ring 11 and the inner ring raceway surface 15 of the inner ring 14 is the inner ring raceway of the outer ring raceway surface 13 of the outer ring 11 and the inner ring raceway 14. With respect to the right row composed of a plurality of spherical rollers 17 and balls 61, 61 arranged between the surface 16, the spherical rollers 17 and the balls 61, 61 are arranged offset in the circumferential direction. ing. Note that at least three spherical rollers 17 may be arranged in each row, and are preferably arranged at equal intervals in the circumferential direction.

According to the self-aligning rolling bearing 60 of the fifth embodiment, since the operating point positions of the double-row outer ring raceway surfaces 12 and 13 are arranged with a distance, when a slight moment load is applied, the outer ring A radial load is generated in the right row and the left row due to the inclination angle between the inner ring 14 and the inner ring 14, and the outer ring 11 and the inner ring 14 can be prevented from being largely inclined. In addition, since the distance of the action point positions of the double-row outer ring raceway surfaces 12 and 13 is small, a certain range of allowable inclination angles can be maintained. Furthermore, since only a part of the conventional self-aligning rolling bearing is improved, it can be used as a fixed-side bearing.
About another structure and effect | action, it is the same as that of the thing of 1st-4th embodiment.

  In addition, this invention is not limited to each embodiment mentioned above, A deformation | transformation, improvement, etc. are possible suitably. Moreover, each embodiment mentioned above can be used in combination within the feasible range.

1 is a half sectional view showing a self-aligning roller bearing according to a first embodiment of the present invention. It is function explanatory drawing at the time of the assembly in the self-aligning roller bearing of 1st Embodiment. FIG. 3 is a function explanatory diagram at the time of incorporation in a case different from FIG. It is a schematic diagram which determines an action point position. It is a half sectional view showing a self-aligning roller bearing of a second embodiment according to the present invention. It is a half sectional view showing a self-aligning roller bearing of a third embodiment according to the present invention. It is a half sectional view showing a self-aligning roller bearing of a fourth embodiment according to the present invention. It is a partial fracture appearance perspective view of the self-aligning roller bearing of a 5th embodiment concerning the present invention. It is a half sectional view showing a conventional self-aligning roller bearing. It is sectional drawing which shows the conventional roller bearing.

Explanation of symbols

10, 30, 40, 50 Spherical roller bearings 11, 51, 52 Outer ring 12, 13 Outer ring raceway surface 14 Inner ring 15, 16 Inner ring raceway surface 17, 41 Spherical roller (roller)
42 Lieutenant 53 Spacer 54 Pin

Claims (6)

An outer ring having a spherical outer ring raceway surface provided in a double row on the inner peripheral surface, an inner ring having a spherical inner ring raceway surface provided in a double row on the outer peripheral surface, and a plurality of arrangements between both raceway surfaces of the double row A self-aligning roller bearing provided with
A self-aligning roller bearing characterized in that the position of the action point of the double row outer ring raceway surface has a distance. When the distance between the center position of the self-aligning roller bearing and the working point position of the outer ring raceway surface is L, the contact angle is α, and the radius of the outer ring raceway surface is R,
−R · sin α ≦ L ≦ 0.312R and L ≠ 0
The self-aligning roller bearing according to claim 1, wherein:   3. The self-aligning roller bearing according to claim 1, wherein the rollers arranged in the double row are arranged asymmetrically, and a center flange is provided between the inner ring raceway surfaces of the double row.   The self-aligning roller bearing according to any one of claims 1 to 3, wherein the outer ring is divided into two.   The self-aligning roller bearing according to claim 4, wherein a spacer is provided between the outer ring divided into two.   The self-aligning roller bearing according to claim 4 or 5, wherein the outer ring divided into two is coupled by a pin.

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