Roller bearing

Abstract

The utility model relates to a roller bearing which can more reliably prevent a shell-shaped outer ring from being stuck when the shell-shaped outer ring is assembled to a shell. This roller bearing is provided with: a ring-shaped shell-shaped outer ring (10); a retainer (20) that is inserted into the shell-shaped outer ring (10); and a roller (30) held by the cage (20), the shell-shaped outer ring (10) being provided with: an outer ring section (13) that forms a raceway surface (15) that faces the rolling surface (31) of the roller (30); a first flange part (11) protruding from one axial end of the outer ring part (13) to the inner diameter side; a second flange part (12) protruding toward the inner diameter side from the other axial end of the outer ring part (13); and bent sections (14) that are provided between the outer ring section (13) and the first flange section (11) and between the outer ring section (11) and the second flange section (12), and that set the inner diameter (r11) of the inner diameter-side end (11a) of the first flange section (11) to 80% or more but less than 95% of the outer diameter (r20) of the maximum diameter section of the cage (20).

Description

TECHNICAL FIELD

[0001] The utility model relates to a roller bearing and a shell-shaped outer ring for the roller bearing. BACKGROUND

[0002] As a roller bearing, there is a bearing having a shell-shaped outer ring. This roller bearing has: a shell-shaped outer ring formed of a plate-shaped member made of metal; a retainer fitted to the inner diameter side of the shell-shaped outer ring; and rollers as rolling elements held by the retainer. The shell-shaped outer ring has: an outer ring portion in a cylindrical shape, forming a raceway surface opposed to the rolling surface of the rolling elements; and a flange portion protruding in the inner diameter direction at both axial end portions of the outer ring portion.

[0003] However, in recent automobile industry, from the viewpoint of improving fuel efficiency, in order to achieve lightweight of vehicles, the opportunity of using light alloy materials such as aluminum is increasing. Along with this, as a material of a shell (a shaft box) that supports a bearing, the case of using a light alloy material such as aluminum is also increasing. In the shell made of a light alloy, compared to the shell made of steel (iron), the risk of seizure of the shell-shaped outer ring increases. Therefore, in the shell-shaped outer ring of Patent Literature 1, a tapered portion is provided on the outer peripheral surface of the axial one end portion of the outer ring portion, the tapered portion gradually decreases in outer diameter from the axial inner side toward the outer side of the axis direction, the taper angle of the tapered portion with respect to the axis direction is set to a range of 0.5 degrees or more and less than 5 degrees, and the occurrence of seizure is prevented.

[0004] In addition, in the shell-shaped outer ring of Patent Literature 2, a curved R portion is interposed on the outer surface of the ridge portion between the outer ring portion and the flange portion, and a connection portion where the tapered portion of the outer peripheral surface of the outer ring portion and the curved R portion are smoothly connected is provided.

[0005] Patent Literature 1: Japanese Patent Application Laid-Open No. 2023-43353

[0006] Patent Literature 2: Japanese Patent Application Laid-Open No. 2023-114019

[0007] As an advantage of the roller bearing using the shell-shaped outer ring, compared to other forms of bearings such as ball bearings, it can be applied in a compact size. In particular, in recent years, in electric vehicles, the demand for power devices "eAxle" that integrate a reducer including an inverter, a motor, and a differential is increasing. In such a power device, in order to realize downsizing of the device while ensuring load capacity, there is also a case where a shell-shaped bearing having a narrower bearing width and a larger outer diameter is adopted.

[0008] However, as described above, the roller bearing using the shell-shaped outer ring is likely to be galling with respect to the housing made of a light alloy. In addition, the shell-shaped outer ring is press-formed. Therefore, as the bearing is increased in diameter, there is a concern that the machining accuracy of the shell-shaped outer ring deteriorates. In addition, as the fitting area of the shell-shaped outer ring with respect to the housing increases, there is a concern that the press-in force increases. If galling or excessive press-in force occurs, the flange portion of the shell-shaped outer ring can be deformed to pinch the inner member or the like.

[0009] According to the shell-shaped outer ring of Patent Documents 1 and 2, it is possible to prevent galling at the time of press-in. However, if the shell-shaped outer ring is increased in diameter, the force required at the time of press-in into the housing becomes large. Therefore, a technique for further reliably preventing galling at the time of press-in is required. SUMMARY

[0010] Therefore, the present application has an object to more reliably prevent galling at the time of assembly of a roller bearing having a shell-shaped outer ring into a housing.

[0011] To solve the above-described problem, the present application adopts a roller bearing including a shell-shaped outer ring in a ring shape, a retainer fitted into the shell-shaped outer ring, and a roller held by the retainer, the shell-shaped outer ring including an outer ring portion forming a raceway surface opposite a rolling surface of the roller, a first flange portion protruding from an axial one end of the outer ring portion toward an inner diameter side, a second flange portion protruding from an axial other end of the outer ring portion toward the inner diameter side, and a bent portion provided between the outer ring portion and the first flange portion and between the outer ring portion and the second flange portion, an inner diameter of an inner diameter side end of the first flange portion being set to be more than 80% and less than 95% of an outer diameter of a maximum diameter portion of the retainer (Structure 1).

[0012] A structure in which the shell-shaped outer ring is pressed into an inner diameter of the housing and the first flange portion is set to a front end side at the time of press-in into the inner diameter of the housing (Structure 2) can be adopted on the basis of Structure 1.

[0013] A structure in which a plate thickness of the first flange portion is set to be more than 45% and less than 70% of a plate thickness of the outer ring portion (Structure 3) can be adopted on the basis of Structure 1 or Structure 2.

[0014] In addition, a structure in which an end portion on an axial one end side of the outer ring portion has a plate thickness varying portion, a plate thickness of the plate thickness varying portion gradually decreases from the plate thickness of the outer ring portion to the plate thickness of the first flange portion, and an inner surface of the plate thickness varying portion is an inclined surface that faces an outer diameter side at an angle of more than 25° and less than 35° with respect to an axial direction as it approaches the first flange portion (Structure 4) can be adopted on the basis of Structure 1, Structure 2, or Structure 3.

[0015] Further, the following structure can be employed: on the basis of any one of Structure 1 to Structure 4, the hardness of at least the first flange portion of the shell-shaped outer ring is 600 HV or less (Structure 5).

[0016] Further, the following structure can be employed: on the basis of any one of Structure 1 to Structure 5, Rb > Ra ≥ Rc or Rb > Rc > Ra is satisfied between an outer diameter Ra at an axially other end of the outer ring portion from the opposed range of the rolling surface, an outer diameter Rb at an axially central portion of the outer ring portion from the opposed range of the rolling surface, and an outer diameter Rc at an axially one end of the outer ring portion from the opposed range of the rolling surface (Structure 6).

[0017] According to the present application, when a roller bearing having a shell-shaped outer ring is assembled to a housing, occurrence of galling can be more reliably prevented. BRIEF DESCRIPTION OF DRAWINGS

[0018] Figure 1 is a longitudinal sectional view showing one embodiment of the present application.

[0019] Figure 2A is Figure 1 is a main part enlarged view of

[0020] Figure 2B is Figure 2A is a main part enlarged view of

[0021] Figure 3 is a longitudinal sectional view showing a state in which the roller bearing is pressed into the housing.

[0022] Figure 4 is Figure 3 is an IV-IV sectional view of

[0023] BRIEF DESCRIPTION OF DRAWINGS

[0024] 1… roller bearing (bearing); 10… shell-shaped outer ring; 11… first flange portion; 12… second flange portion; 13… outer ring portion; 14… bent portion; 15… raceway surface; 16… plate thickness varying portion; 16a… inner surface (inclined surface); 20… retainer; 30… roller; 31… rolling surface; r11… inner diameter at the inner diameter side end; r20… outer diameter at the maximum diameter portion; t11, t13… plate thickness; R, Ra, Rb, Rc… outer diameter. DETAILED DESCRIPTION

[0025] An embodiment of the present application will be described based on the drawings. Figure 1 is a longitudinal sectional view of the roller bearing 1 of the present embodiment. Figure 2A and Figure 2B is a detailed view of the shell-shaped outer ring 10 used in the roller bearing 1.Figure 3 is a sectional view showing a state in which the roller bearing 1 is pressed into a housing H.

[0026] The roller bearing 1 has a shell-shaped outer ring 10, a retainer 20 fitted into the shell-shaped outer ring 10, and needle rollers 30 of a cylindrical shape held by the retainer 20. In the embodiment, as the needle rollers 30, needle rollers of a length in the axial direction of the cylinder that is longer than the diameter (for example, a length of about 3 times or more and less than 10 times the diameter) are used. In the embodiment, a large roller bearing 1 of an outer diameter of 60 φ or more and 100 φ or less used in a power device "eAxle" of an electric automobile is assumed.

[0027] The retainer 20 has a pair of circular ring portions 21, 21, and a plurality of column portions 22 connecting the circular ring portions 21, 21 in the axial direction. Spaces between the column portions 22, 22 adjacent in the circumferential direction become pocket portions that hold the needle rollers 30. The needle rollers 30 are held from falling out by roller stop portions (not shown) protruding from the column portions 22.

[0028] The shell-shaped outer ring 10 has an outer ring portion 13 that forms a raceway surface 15 opposed to a rolling surface 31 of the needle rollers 30, a first flange portion 11 protruding from an axial one end of the outer ring portion 13 toward an inner diameter side, and a second flange portion 12 protruding from an axial other end of the outer ring portion 13 toward the inner diameter side. In addition, the first flange portion 11 and the second flange portion 12 each have a bent portion 14 connected to the outer ring portion 13.

[0029] The shell-shaped outer ring 10 is formed by bending processing of a cylindrical member made of metal. The bent portion 14 on the axial other end side (the second flange portion 12 side) is formed by press processing of an end portion of the cylindrical member. The bent portion 14 on the axial one end side (the first flange portion 11 side) is formed by bending processing after the retainer 20 and the needle rollers 30 are inserted into the inside of the outer ring portion 13. Hereinafter, the processing of the bent portion 14 on the axial other end side is referred to as first bending processing, and the processing of the bent portion 14 on the axial one end side is referred to as second bending processing.

[0030] The retainer 20 and the needle rollers 30 are inserted into the inside of the shell-shaped outer ring 10 in which the second flange portion 12 is formed by the first bending processing, and the first flange portion 11 is formed by the second bending processing, thereby becoming a state in which the retainer 20 and the needle rollers 30 are held inside the outer ring portion 13, and the roller bearing 1 is constituted. In addition, the roller bearing 1 is pressed into and fixed to the inner diameter of the housing H having a hole of a sectional circular shape. At this time, a press-in allowance of about 40 to 350 μm in terms of a difference in diameter is set. Further, a shaft (not shown) is inserted through the inside of the needle rollers 30 arranged in the circumferential direction, that is, the side of the axis O of the roller bearing 1, and the shaft is supported so as to be relatively rotatable about the axis with respect to the housing H.

[0031] In this embodiment, the housing H is envisioned as the axle housing of the roller bearing 1 used in the power unit "eAxle" of an electric vehicle, but the housing H could also be any component other than the axle housing within such an "eAxle". The housing H is made of a light metal, primarily composed of aluminum or other light metals. Regarding the shell-shaped outer ring 10, when pressed into the inner diameter of the housing H, the first flange portion 11 side of the shell-shaped outer ring 10 is pressed in first. That is, the first flange portion 11 side is designated as the front end side during pressing, and the second flange portion 12 side is designated as the rear end side during pressing.

[0032] The shell-shaped outer ring 10 is formed by cold rolling carbon steel or stainless steel for mechanical structures. Examples include SPC, SCM, and SUS. The plate thickness t13 of the outer ring portion 13 is, for example, 0.5 mm or more and less than 2.5 mm. Furthermore, the inner surface of the hole of the shell H that contacts the outer surface 17 of the outer ring portion 13 is machined to a specified average roughness or less.

[0033] like Figure 1 As shown, the outer diameter r20 of the maximum diameter portion of the retainer 20 is larger than the inner diameter r11 of the inner diameter side end 11a of the first flange portion 11, and also larger than the inner diameter r12 of the inner diameter side end 12a of the second flange portion 12. Therefore, the axial movement of the retainer 20 is restricted by the first flange portion 11 and the second flange portion 12. Furthermore, in Figure 1 In the attached figure, the outer diameter of the outer shell 10 is indicated by the reference numeral R.

[0034] Furthermore, the inner diameter r11 of the inner diameter side end 11a of the first flange portion 11 is set to be more than 80% and less than 95% of the outer diameter r20 of the maximum diameter portion of the retainer 20. This can be expected to prevent seizing during pressing into the housing H. That is, if the pressing force of the roller bearing 1 relative to the housing H is too large, seizing is likely to occur between the first flange portion 11 of the outer ring 10 and the housing H on the object side. However, by increasing the inner diameter of the first flange portion 11, which is the front end side during pressing, compared to the past, the rigidity of the flange portion is reduced, resulting in smooth pressing by reducing the pressing force.

[0035] Here, if the ratio of the inner diameter rll of the inner diameter side end 11a of the first flange portion 11 to the outer diameter r20 of the largest diameter portion of the retainer 20 is less than 80%, the rigidity of the shell-shaped outer ring 10 becomes high, and there is a tendency that seizure is easily generated. Also, in the case where the roller bearing 1 is oil-lubricated, there is a possibility that the smooth outflow and inflow of oil to the inside of the shell-shaped outer ring 10 is hindered. On the contrary, if the ratio becomes 95% or more, in the case where the retainer 20 is inclined (in the case where the axis of the retainer 20 is inclined with respect to the axis of the shell-shaped outer ring 10), there is a possibility that the end portion of the retainer 20 is hooked to the inner diameter side end of the shell-shaped outer ring 10 or the retainer 20 is dropped, depending on the use condition. In these points, it is also preferable that the ratio of the inner diameter rll of the inner diameter side end 11a of the first flange portion 11 to the outer diameter r20 of the largest diameter portion of the retainer 20 be set to 80% or more and less than 95%.

[0036] Also, the first flange portion 11 stands up to the inner diameter side from the one end in the axial direction of the outer ring portion 13 which is in a cylindrical shape. With respect to the outer ring portion 13, the plate thickness t13 is constant over the entire length in the axial direction except for the plate thickness changing portion 16 at the one end in the axial direction. The plate thickness tl l of the first flange portion 11 is set to be smaller (thinner) than the plate thickness t13 of the outer ring portion 13. In the embodiment, the plate thickness tl l of the first flange portion 11 is set to be 45% or more and less than 70% of the plate thickness t13 of the outer ring portion 13. With this setting of the plate thickness, the suppression effect of the generation of seizure is further improved. That is, by setting the plate thickness tl l of the first flange portion 11 to be thinner than the plate thickness t13 of the outer ring portion 13 and reducing the rigidity of the flange portion, smooth press-in is achieved. Also, the first flange portion 11 is the flange portion on the side of the rear bending process, and such a setting of the plate thickness also contributes to the easiness of the rear bending process.

[0037] Here, if the ratio of the plate thickness tl l of the first flange portion 11 to the plate thickness t13 of the outer ring portion 13 is less than 45%, there is a possibility that the shape of the first flange portion 11 is unstable at the time of press working of the shell-shaped outer ring 10. Also, the plate thickness tl l of the first flange portion 11 is too thin, and there is a possibility that the first flange portion 11 is deformed at the time of press-in of the shell-shaped outer ring 10 into the housing H. On the contrary, if the ratio becomes 70% or more, the rigidity of the shell-shaped outer ring 10 becomes high, and there is a tendency that seizure is easily generated. In these points, it is also preferable that the ratio of the plate thickness tl l of the first flange portion 11 to the plate thickness t13 of the outer ring portion 13 be set to 45% or more and less than 70%.

[0038] Further, as Figure 2AAs shown, the inner diameter side end 11a of the first flange portion 11 is the portion that protrudes most toward the inner diameter side among the portions of the first flange portion 11. In the embodiment, the first flange portion 11 has a first portion 11c connected to the inner diameter side of the curved portion 14, and a second portion 11d connected to the inner diameter side of the first portion 11c. The first portion 11c extends linearly along the radial direction of the roller bearing 1 from the inner diameter side end of the curved portion 14. The side surface 11b of the first portion 11c is the portion that protrudes most toward the one axial end side of the shell-shaped outer ring 10. The second portion 11d extends in a direction that slightly inclines toward the other axial end side as it approaches the inner diameter side from the inner diameter side end of the first portion 11c. The inner diameter side end 11a of the first flange portion 11 corresponds to the leading end edge of the one axial end side of the inclined second portion 11d.

[0039] The curved portion 14 on the one axial end side is located on the outer diameter side end of the first flange portion 11, and combines the first flange portion 11 with the outer ring portion 13. The outer surface 18 and the inner surface 19 of the curved portion 14 are concentric circles each composed of a circular arc formed with a single radius in any longitudinal cross section including the axis O of the roller bearing 1. The outer surface 18 of the curved portion 14 is formed as a circular-arc-shaped ridge line portion that protrudes toward the outside on the entire circumference of the shell-shaped outer ring 10, and thus the shell-shaped outer ring 10 is more smoothly pressed into the housing H.

[0040] Here, in order to prevent galling from occurring, it is preferable that the hardness of at least the first flange portion 11 of the shell-shaped outer ring 10 be 600 HV (Vickers hardness) or less. This is because if the hardness of the first flange portion 11 is too high (too hard), galling is likely to occur. In addition, HV (Vickers hardness) is a measure of the hardness of a test body based on the size of the dent (indentation) formed when a rigid body (indenter) made of diamond is pressed into the test body. The measurement method is based on Japanese Industrial Standard JIS-Z 2244:2009. In the embodiment, the hardness of at least the first flange portion 11 is made to be 600 HV or less. However, depending on the material and the use, the entire shell-shaped outer ring 10 can also be made to be 600 HV or less.

[0041] Further, the outer ring portion 13 has a plate thickness varying portion 16 at the end portion on the one axial end side thereof, and the plate thickness of the plate thickness varying portion 16 gradually decreases from the plate thickness t13 of the outer ring portion 13 to the plate thickness t11 of the first flange portion 11. In any longitudinal cross section including the axis of the shell-shaped outer ring 10, the inner surface 16a of the plate thickness varying portion 16 includes an inclined surface that inclines toward the outer diameter side as it approaches the first flange portion 11, and the inclined surface 16a is angled at an angle a with respect to the axis of the shell-shaped outer ring 10 (see FIG. 2). The plate thickness varying portion 16 is formed by press working. Figure 2BThe angle α is preferably 25° or more and less than 35°. By providing a thickness variation portion 16 at one end of the outer ring portion 13 along its axial direction, the post-bending process of the first flange portion 11 is facilitated. Here, it is assumed that if the angle α is less than 25 degrees, there is a possibility that the shape of the first flange portion 11 may become unstable during bending. Conversely, if the angle α is 35 degrees or more, the rigidity near the thickness variation portion 16 is low, and therefore there is a possibility that the component may deform when the shell-shaped outer ring 10 is pressed into the shell H. At these points, an angle α of 25° or more and less than 35° is also preferred.

[0042] In the implementation method, such as Figure 2B As shown, the inner surface 16a of the plate thickness variation section 16 makes the connecting portion 16b towards the outer ring section 13 and the connecting portion 16c towards the inner surface 19 of the bending section 14 arc-shaped to make them smooth, but the shape of these connecting portions 16b and 16c can be appropriately changed. For example, the radii rb and rc of the arcs of each connecting portion 16b and 16c can be made more than... Figure 2B The state shown is small; conversely, the radii rb and rc of the arcs of each connecting part 16b and 16c can also be made smaller than those of the connecting parts 16b and 16c. Figure 2B The state shown is large. Alternatively, the connecting parts 16b and 16c can be combinations of multiple arcs with different radii. Alternatively, it can be as follows... Figure 2B The inner surface 16a of the thickness variation section 16 shown has a straight inclined surface (conical surface) with a single slope sandwiched in the middle. Alternatively, the inner surface 16a of the thickness variation section 16 can be without such a straight inclined surface. When the inner surface 16a of the thickness variation section 16 does not have a straight inclined surface sandwiched in it, the maximum angle among the angles (acute angles) of each part of the inner surface 16a of the thickness variation section 16 relative to the axial direction can be the aforementioned angle α.

[0043] Furthermore, in this embodiment, the outer surface 18 and inner surface 19 of the curved portion 14 are concentric circles formed by arcs with a single radius, but the shape of the curved portion 14 is not limited to this embodiment. Alternatively, for example, a tapered surface may be provided at one axial end of the outer surface 17 of the outer ring portion 13, smoothly connecting from the outer surface 17 side of the outer ring portion 13 to the outer surface 18 side of the curved portion 14. In this case, the angle of the tapered surface relative to the axial direction of the roller bearing 1 in any longitudinal section including the axis O of the roller bearing 1 can, for example, be set to gradually move towards the inner diameter side at an angle of 0.5 degrees or more and less than 5 degrees as it moves towards the first flange portion 11 side.

[0044] The second flange portion 12 also stands up from the other axial end of the cylindrical outer ring portion 13 toward the inner diameter side. The structure of the curved portion 14 is the same as that of the first flange portion 11. Further, the side surface 12b of the second flange portion 12 extends linearly along the radial direction of the roller bearing 1 from the inner diameter side end of the curved portion 14. The axial width A of the shell-shaped outer ring 10 is equivalent between the side surface 12b of the second flange portion 12 and the side surface 11b of the first flange portion 11. Further, the second flange portion 12 side is the rear end side at the time of press-fitting, and the plate thickness t12 of the second flange portion 12 is less likely to become a cause of seizure at the time of press-fitting. In addition, the outer ring portion 13 that forms the raceway surface 15 is subjected to deep drawing, and thus the plate thickness t12 of the second flange portion 12 can also be set to be greater than the plate thickness t13 of the outer ring portion 13.

[0045] Further, in the present embodiment, regarding Figure 1 the outer diameter R of the shell-shaped outer ring 10 shown in the drawing, by adopting the following structure, the effect of preventing seizure at the time of press-fitting into the housing H is further improved. That is, as shown in the drawing, Figure 3 within the axial width A of the shell-shaped outer ring 10, between the outer diameter Ra at the other axial end 13a of the opposing range B of the rolling surface 31 of the roller 30 in the outer ring portion 13, the outer diameter Rb at the axial center 13b of the opposing range B, and the outer diameter Rc at the one axial end 13c of the opposing range B, it is preferable that Rb > Ra ≥ Rc or Rb > Rc > Ra be satisfied. In addition, it is preferable that the difference between Rb and Ra, and the difference between Rb and Rc each be about 10 to 30 μm. In Figure 3 the drawing, the shell-shaped outer ring 10 in a state of being press-fitted into the housing H is shown, but the values of the outer diameter Ra, the outer diameter Rb, and the outer diameter Rc indicated by each of the above Rb > Ra ≥ Rc and Rb > Rc > Ra are applied to the values of the outer diameters at each position of the shell-shaped outer ring 10 before press-fitting.

[0046] Figure 4 The shell-shaped outer ring 10 in a state of being press-fitted into the inner diameter of the housing H is schematically shown, and the pressing force in the inner diameter direction with the axis O as the center indicated by reference numeral X and the pressing force in the outer diameter direction indicated by reference numeral Y are each suppressed to be smaller than in the past.

[0047] It should be understood that the embodiments disclosed this time are illustrative and not restrictive in all points. The scope of the present application is not the explanation described above, but is shown by the scope of the present application as claimed, and is intended to include all modifications within the meaning and the scope equivalent to the scope of the present application as claimed.

Claims

1. A roller bearing, characterized by, Possessing: a shell-shaped outer ring (10) in a ring shape; a retainer (20) incorporated into the shell-shaped outer ring (10); and a roller (30) held by the retainer (20), the shell-shaped outer ring (10) possesses: an outer ring portion (13) that forms a raceway surface (15) that opposes a rolling surface (31) of the roller (30); a first flange portion (11) that protrudes from an axial one end of the outer ring portion (13) toward an inner diameter side; a second flange portion (12) that protrudes from an axial other end of the outer ring portion (13) toward the inner diameter side; and a bent portion (14) that is provided between the outer ring portion (13) and the first flange portion (11) and between the outer ring portion (13) and the second flange portion (12), an inner diameter (r11) of an inner diameter side end (11a) of the first flange portion (11) is set to be 80% or more and less than 95% of an outer diameter (r20) of a maximum diameter portion of the retainer (20).

2. The roller bearing according to claim 1, characterized in that the shell-shaped outer ring (10) is pressed into an inner diameter of a housing, and the first flange portion (11) is set to be a front end side at the time of being pressed into the inner diameter of the housing.

3. The roller bearing according to claim 1 or 2, characterized in that a plate thickness (t11) of the first flange portion (11) is set to be 45% or more and less than 70% of a plate thickness (t13) of the outer ring portion (13).

4. The roller bearing according to claim 1 or 2, characterized in that an end portion on an axial one end side of the outer ring portion (13) has a plate thickness varying portion (16) whose plate thickness gradually decreases from the plate thickness (t13) of the outer ring portion (13) to the plate thickness (t11) of the first flange portion (11), and an inner surface (16a) of the plate thickness varying portion (16) is an inclined surface that faces an outer diameter side at an angle of 25° or more and less than 35° with respect to an axial direction as it approaches the first flange portion (11).

5. The roller bearing according to claim 1 or 2, characterized in that a hardness of at least the first flange portion (11) of the shell-shaped outer ring (10) is 600 HV or less.

6. The roller bearing according to claim 1 or 2, characterized in that between an outer diameter Ra at an axial other end (13a) of the outer ring portion (13) in an opposing range of the rolling surface (31), an outer diameter Rb at an axial center (13b) of the outer ring portion (13) in the opposing range of the rolling surface (31), and an outer diameter Rc at an axial one end (13c) of the outer ring portion (13) in the opposing range of the rolling surface (31), Rb > Ra ≥ Rc or Rb > Rc > Ra holds.

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