Angular ball bearing

Abstract

To provide an angular ball bearing capable of being miniaturized and realizing high moment rigidity and a long service life.SOLUTION: An angular ball bearing 1 includes: inner and outer rings 2, 3; raceway surfaces 2a, 3a; an inner ring shoulder portion 2d formed on an outer diameter of the inner ring 2; an outer ring shoulder portion 3d formed on an inner diameter of the outer ring 3; and a plurality of balls 4. A ratio W / D of an assembling width W as an axial dimension from a back face 2c as an axial end face of the shoulder portion 2d of the inner ring 2 to a back face 3c as an axial end face of the shoulder portion 3d of the outer ring 3 and a diameter D of the balls 4 is 1.3 or more and 1.9 or less. A ratio H1 / D of a groove depth H1 from a groove bottom of the raceway surface 2a to an outer diameter face of the shoulder portion 2d and the diameter D of the balls 4 is 0.3 or more and 0.5 or less, and a ratio H2 / D of a groove depth H2 from a groove bottom of the raceway surface 3a to an outer diameter face of the shoulder portion 3d and the diameter D of the ball 4 is 0.3 or more and 0.5 or less. A percentage of a ratio A / B of each groove bottom thickness A and a pitch circle diameter B of the ball 4 is 1.3% or more and 2.9% or less, and a filling rate of the balls 4 is 82% or more.SELECTED DRAWING: Figure 1

Description

[Technical field]

[0001] The present invention relates to an angular contact ball bearing that can be used in industrial machinery that requires moment rigidity while being compact. [Background technology]

[0002] In general, there is a need for industrial machinery to be compact and lightweight, and the bearings used must also be compact. On the other hand, the bearings must be rigid while still being compact. Angular contact ball bearings are used in various devices and the like. Angular contact ball bearings are used in multiple row combinations of two or more rows, such as face-to-face combinations, back-to-back combinations, and parallel combinations, depending on the purpose. In Patent Document 1, angular contact ball bearings are used in back-to-back combinations to be able to support large loads and meet the demand for a long life. [Prior art documents] [Patent documents]

[0003] [Patent Document 1] Patent No. 6654123 Summary of the Invention [Problem to be solved by the invention]

[0004] Depending on the application of various devices, angular contact ball bearings with special dimensions that are relatively compact, with raceway widths and cross-sectional dimensions thinner than the standard bearing dimensions specified by the JIS standard, may be required, while still providing high moment rigidity and a long life through an increase in the rated load.

[0005] An object of the present invention is to provide an angular contact ball bearing which is compact and which achieves high moment rigidity and a long life. [Means for solving the problem]

[0006] The angular contact ball bearing of the present invention is an angular contact ball bearing comprising an inner member and an outer member, raceway surfaces formed on the outer peripheral surface of the inner member and the inner peripheral surface of the outer member, shoulders formed on the outer diameter of the inner member and the inner diameter of the outer member, and a plurality of balls interposed between the inner member and the outer member with a contact angle therebetween, a ratio W / D of an assembly width W, which is an axial dimension from an axial end face of a shoulder portion of the inner member to an axial end face of a shoulder portion of the outer member, to a diameter D of the ball is 1.3 or more and 1.9 or less; a ratio H1 / D of a groove depth H1 from a groove bottom of the raceway surface of the inner member to an outer diameter surface of a shoulder portion of the inner member to a diameter D of the ball is 0.3 or more and 0.5 or less, and a ratio H2 / D of a groove depth H2 from a groove bottom of the raceway surface of the outer member to an inner diameter surface of a shoulder portion of the outer member to a diameter D of the ball is 0.3 or more and 0.5 or less, The ratio A / B of the groove bottom thickness A of the inner member and the outer member to the pitch circle diameter B of the balls is 1.3% or more and 2.9% or less, and the packing rate of the balls is 82% or more. When the heights of the outer peripheral surfaces on both axial sides of the inner member are different, the side located radially outward is defined as the shoulder, and the depth from the outer peripheral surface to the bottom of the groove is defined as the shoulder. When the heights of the inner peripheral surface on both axial sides of the outer member are different, the side located radially inward is defined as the shoulder, and the depth from the inner peripheral surface to the bottom of the groove is defined as the shoulder. The groove bottom thickness A refers to the radial thickness of the groove bottom position of each raceway surface in the inner member and the outer member. The ball packing rate C is calculated by the following formula: Packing rate C = (ball diameter x number) / (π x pitch circle diameter).

[0007] The upper limit of the ratio W / D, where W is the assembly width and D is the ball diameter, is set at 1.9, making the bearing lighter and more compact in the axial direction than standard angular contact ball bearings, and enabling the compactification of devices that use this angular contact ball bearing. The lower limit of W / D is set at 1.3, ensuring the moment rigidity required for an angular contact ball bearing.

[0008] H1 / D and H2 / D are set to 0.3 or more and 0.5 or less, respectively. In this case, the groove depth is deeper than that of a standard angular contact ball bearing, so shoulder riding can be prevented when a large moment load is applied. This prevents the raceway surfaces of the inner and outer members from peeling off, and extends the life of the angular contact ball bearing. In this way, it is possible to achieve a compact design while also achieving high moment rigidity and a long life.

[0009] If the groove depths H1 / D and H2 / D relative to the ball diameter are less than 0.3, there is a risk of shoulder-riding when a large moment load is applied.If H1 / D and H2 / D exceed 0.5, the radial thickness of the inner member and outer member becomes too thin, making it impossible to support a moment load large enough to exceed a specified load, and the angular contact ball bearing is less versatile in its applications.

[0010] By setting the ratio A / B of each groove bottom thickness A to pitch circle diameter B at a percentage between 1.3% and 2.9%, the ball diameter can be set large while maintaining bearing rigidity. If A / B is less than 1.3%, it may be difficult to maintain bearing rigidity. If A / B exceeds 2.9%, it becomes difficult to achieve radial compactness. By setting the ball packing rate at 82% or more, a large number of balls can be secured, and the rated load can be increased, thereby extending the life of the angular contact ball bearing.

[0011] The ratio R / D of the groove curvature R of each raceway surface of the inner member and the outer member to the diameter D of the ball may be 1.01 or more and 1.07 or less. By setting R / D to 1.01 or more and 1.07 or less, the bearing rigidity can be more reliably ensured. If R / D is less than 1.01, the rolling resistance becomes undesirably large. If R / D exceeds 1.07, there is a risk of shoulder riding when a large moment load is applied, and the conditions of use are limited.

[0012] The ratio d / B of the inner diameter d of the inner member to the pitch circle diameter B of the balls may be 0.84 or more and 0.93 or less. In this case, the radial thickness of the inner member can be thinned, making devices using the angular ball bearing more compact and space-saving. If d / B is less than 0.84, the effect of thinning the inner member is low. If d / B exceeds 0.93, it may be difficult to ensure the rigidity of the inner member.

[0013] The ratio D1 / B of the outer diameter D1 of the outer member to the pitch circle diameter B of the balls may be 1.07 or more and 1.16 or less. In this case, the radial thickness of the outer member can be thinned, and devices using the angular ball bearing can be made more compact and space-saving. If D1 / B is less than 1.07, it may be difficult to ensure the rigidity of the outer member. If D1 / B is more than 1.16, the effect of thinning the outer member is reduced.

[0014] The contact angle may be 30° or more and 45° or less. A comparison was made of the effect of the contact angle α of an angular ball bearing on moment rigidity and shoulder riding when a moment load is applied within the dynamic load rating range of the angular ball bearing. The comparison showed that by setting the contact angle α in the range of 30° or more and 45° or less, high moment rigidity is obtained and shoulder riding does not occur, thereby extending the life of the angular ball bearing. If the contact angle α is less than 30°, the desired moment rigidity may not be obtained. If the contact angle α exceeds 45°, there is a risk of shoulder riding. Effect of the Invention

[0015] The angular contact ball bearing of the present invention has a ratio W / D of assembled width W to ball diameter D of 1.3 or more and 1.9 or less, a ratio of each groove depth to the ball diameter of 0.3 or more and 0.5 or less, a ratio A / B of each groove bottom thickness A of the inner member and outer member to the pitch circle diameter B of the balls of 1.3% or more and 2.9% or less, and a ball filling rate of 82% or more, thereby achieving a compact design while also achieving high moment rigidity and a long life. [Brief description of the drawings]

[0016] [Figure 1] 1 is a vertical sectional view of an angular ball bearing according to a first embodiment of the present invention. [Diagram 2] FIG. 4 is a vertical cross-sectional view showing an example of a back-to-back assembly of the angular ball bearings. [Diagram 3] This is an example in which a moment load is applied to an angular contact ball bearing. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0017] [First embodiment] An angular contact ball bearing according to an embodiment of the present invention will be described with reference to Figures 1 and 2. In this specification, the angular contact ball bearing may be simply referred to as a "bearing". As shown in Fig. 1, an angular contact ball bearing 1 includes an inner ring 2 as an inner member, an outer ring 3 as an outer member, raceway surfaces 2a, 3a formed on the outer peripheral surface of the inner ring 2 and the inner peripheral surface of the outer ring 3, an inner ring shoulder 2d formed on the outer diameter of the inner ring 2, an outer ring shoulder 3d formed on the inner diameter of the outer ring 3, a plurality of balls 4 interposed between the raceway surfaces 2a, 3a of the inner and outer rings 2, 3, and a cage 5 that holds these balls 4. The inner and outer rings 2, 3 are made of, for example, high carbon chromium bearing steel such as SUJ2 or martensitic stainless steel. The balls 4 are made of, for example, steel balls or ceramics.

[0018] The cage 5 holds a plurality of balls 4 in pockets Pt provided at a plurality of positions in the circumferential direction. The cage 5 in this example is made of an iron plate made of cold-rolled steel or the like, and the pockets Pt for holding the balls 4 are formed at equal intervals around the circumference of the roughly conical annular main part 5a. The inner and outer rings 2, 3, balls 4, and cage 5 are not limited to the materials mentioned above.

[0019] The raceway surface 3a is connected to the front surface 3b of the outer ring 3 via a counterbore. An outer ring shoulder 3d, which is the inner peripheral surface on the back side of the outer ring 3, is located radially inward of the counterbore of the outer ring 3. The raceway surface 2a is connected to the front surface 2b of the inner ring 2 via a counterbore. An inner ring shoulder 2d, which is the outer peripheral surface on the back side of the inner ring 2, is formed between the raceway surface 2a of the inner ring 2 and the back surface 2c of the inner ring 2. The inner ring shoulder 2d is located radially outward of the counterbore of the inner ring 2. The front surfaces 2b and 3b of the inner and outer rings 2 and 3 refer to the side surfaces that do not support axial loads, and the back surfaces 2c and 3c of the inner and outer rings 2 and 3 refer to the side surfaces that support axial loads.

[0020] <Regarding groove depth, assembly width, etc.> The ratio H1 / D of the groove depth H1 from the groove bottom of the raceway surface 2a of the inner ring 2 to the outer diameter surface of the shoulder portion 2d to the diameter D of the balls 4 is set to be 0.3 or more and 0.5 or less, and the ratio H2 / D of the groove depth H2 from the groove bottom of the raceway surface 3a of the outer ring 3 to the outer diameter surface of the shoulder portion 3d to the diameter D of the balls 4 is set to be 0.3 or more and 0.5 or less. The ratio W / D of the assembled width W, which is the axial dimension from the back surface 2c, which is the axial end face of the shoulder portion 2d of the inner ring 2, to the back surface 3c, which is the axial end face of the shoulder portion 3d of the outer ring 3, to the diameter D of the balls is 1.3 or more and 1.9 or less.

[0021] <Groove bottom thickness, filling rate> The ratio A / B of the groove bottom thickness A of the inner and outer rings 2, 3 to the pitch circle diameter B of the balls 4 is 1.3% or more and 2.9% or less, and the packing rate of the balls 4 is 82% or more and 91% or less. The packing rate C of the balls 4 is calculated by the following formula: Packing rate C = (ball diameter x number) / (π x pitch circle diameter)

[0022] <Inner / Outer Diameter PCD Ratio> The inner diameter of the inner ring of the angular contact ball bearing used is, for example, φ80 mm to φ500 mm, but is not limited to this inner diameter dimension. The ratio d / B of the inner diameter d of the inner ring 2 to the pitch circle diameter B of the balls 4 is set to 0.84 or more and 0.93 or less, and the ratio D1 / B of the outer diameter D1 of the outer ring 3 to the pitch circle diameter B of the balls 4 is set to 1.07 or more and 1.16 or less.

[0023] <Rear combination, etc.> Moment loads are often applied to industrial machinery. Under operating conditions where moment loads are applied by angular contact ball bearings, as shown in Fig. 2, by arranging angular contact ball bearings 1 in a back-to-back arrangement, the distance between the bearing load points can be increased, so that the allowable radial load and allowable moment load can be increased even if the angular contact ball bearing 1 is made smaller, i.e., more compact. Furthermore, by arranging the angular contact ball bearings 1 in a back-to-back arrangement, it is possible to receive axial loads in both directions, and in addition, the rigidity of the bearing portion can be increased by adding preload. In the example shown in Fig. 2, an inner ring spacer 6 and an outer ring spacer 7 are interposed between the angular contact ball bearings 1, 1 adjacent to each other in the axial direction, but it is also possible to omit these spacers 6, 7 and arrange the angular contact ball bearings 1, 1 in a back-to-back arrangement.

[0024] <Contact angle, etc.> In order to withstand large moment loads, the contact angle α of the angular ball bearing 1 is set to 30° or more and 45° or less, and the groove depths H1, H2 of the inner and outer rings 2, 3 shown in FIG. 1 are set to 30-50% of the ball diameter ratio as described above. In this case, since the groove depth is deeper than that of a standard angular ball bearing, shoulder riding can be prevented when a large moment load is applied, and peeling of the raceway surfaces 2a, 3a can be prevented. In other words, the life of the bearing can be extended. Moment load refers to a load that tilts (bends) the rotating shaft or gives an angle to the rotating shaft. 1, the groove curvature R of each raceway surface 2a, 3a of the inner and outer rings 2, 3 is set to a ball diameter ratio of 101 to 107% based on the contact angle α and the conditions of use. In other words, the ratio R / D of the groove curvature R of each raceway surface 2a, 3a to the diameter D of the ball 4 is 1.01 or more and 1.07 or less.

[0025] <Relationship between contact angle, moment stiffness, and shoulder riding> Table 1 shows a comparison of the effect of the contact angle on moment stiffness and shouldering when a moment load is applied within the dynamic load rating range of the angular contact ball bearing. When an angular contact ball bearing receives an external load and a moment load is applied, the output shaft tilts in proportion to the load moment. Moment stiffness represents the stiffness of an angular contact ball bearing and is expressed as the load moment value required to tilt a unit angle. Figure 3 shows an example of a state in which a moment load is applied to a combination angular contact ball bearing 1,1 by applying a radial load W1 to a position along the output shaft center C2 at a position a predetermined distance l away from the output shaft mounting surface Sa on one side C1 in the axial direction, and applying an axial load W2 to a position a predetermined distance l3 away from the output shaft center C2 downward in the radial direction. The bearing sizes were angular contact ball bearings used in devices that require compactness, with an inner ring inner diameter of φ80 mm to φ500 mm, an inner ring inner diameter of 84% to 93% of the PCD ratio, and an outer ring outer diameter of 107% to 116% of the PCD ratio. Nine types of angular contact ball bearings (Comparative Examples 1-3, 8, 9 and Examples 4-7) were evaluated with H1 / D and H2 / D both in the range of 0.3 to 0.5, W / D in the range of 1.3 to 1.9, and contact angle α in the range of 15° to 55°.

[0026] Each of Examples 4 to 7 also satisfies the requirements that the percentage of A / B is 1.3% or more and 2.9% or less, and the ball packing rate C is 82% or more. In each of the Comparative Examples and Examples, as shown in Figure 2, angular contact ball bearings 1 are arranged in back-to-back combination, and an inner ring spacer 6 and an outer ring spacer 7 of specified width dimensions are interposed between axially adjacent angular contact ball bearings 1, 1.

[0027] [Table 1]

[0028] Table 1 shows the evaluation of moment stiffness and shoulder riding for contact angles α in the range of 15° to 55°. In Table 1, ◎ indicates that it is possible to implement and has a high effect, ◯ indicates that it is inferior in performance to ◎ but is possible to implement, △ indicates that it is inferior in performance to ◯ but is possible to implement, and × indicates that it is less effective.

[0029] When a back-to-back combination angular contact ball bearing equipped with the inner and outer ring spacers described above of a bearing size used in a specified industrial machine fully satisfies the required moment rigidity when an external load is applied and is suitably operable, it is judged as ◎. When it is slightly inferior to ◎ but satisfies the required moment rigidity and is operable, it is judged as 〇. When it is inferior to 〇 but is operable, it is judged as △. When it does not meet the required moment rigidity, it is judged as ×. From Table 1, it is confirmed that when the contact angle α is less than 30°, there is a decrease in moment rigidity. The judgment criteria for moment rigidity explained above are also applicable to Table 2 described later.

[0030] When an external load is applied to the angular contact ball bearing, if the effect on the shoulder riding of the balls is high, taking into account the contact surface pressure between the balls and the raceway surface, and it is feasible, it is judged as ◎. If the shoulder riding effect is slightly inferior to ◎, but feasible, it is judged as ◯. If the shoulder riding effect is inferior to ◯, but feasible, it is judged as △. If the shoulder riding effect is low, it is judged as ×. From Table 1, it is confirmed that the shoulder riding characteristic deteriorates when the contact angle α exceeds 45°. The criteria for judging shoulder riding explained above are also applicable to Table 2. The results in Table 1 show that by setting the contact angle α in the range of 30° to 45°, high moment rigidity can be obtained and the shoulder does not ride up, resulting in a longer life.

[0031] <Overall rating> Table 2 shows the results of evaluating angular ball bearings from the viewpoints of moment rigidity, shoulder riding, compactness, and weight reduction. The results are also used to evaluate the bearing life and to comprehensively evaluate whether they function as bearings. Seven types of angular ball bearings of the same bearing size as described above (Comparative Examples 1 and 2, Examples 1 to 5) were evaluated. Furthermore, the angular ball bearings 1 were arranged in a back-to-back combination, and an inner ring spacer 6 and an outer ring spacer 7 of a specified width were interposed between the angular ball bearings 1, 1 adjacent to each other in the axial direction. The conditions under which a moment load is applied to the combined angular ball bearings are the same as those shown in FIG. 3 above. [Table 2]

[0032] In Table 2, ◎ indicates that it is possible to implement, highly effective, and most suitable, ◯ indicates that it is slightly inferior in performance to ◎ but is possible to implement, △ indicates that it is inferior in performance to ◯ but is possible to implement, and × indicates that it is less effective. Taking into consideration the evaluation of each item, such as moment rigidity, shoulder riding, compactness, weight reduction, and bearing life, Examples 1 to 5, in which all items are ◎ or ◯ or better, are considered possible to implement. When an external load is applied to the back-to-back angular contact ball bearing, the bearing life is calculated based on the calculated rated load, etc.

[0033] The results in Table 1 show that shoulder riding can be prevented by satisfying the requirements of a contact angle α of 30° or more and 45° or less, and H1 / D and H2 / D of both 0.3 or more and 0.5 or less, as in Examples 4 to 7.Furthermore, considering the results in Table 2, it can be seen that by satisfying the requirements of an A / B of 1.3% or more and 2.9% or less, a W / D of 1.3 or more and 1.9 or less, and a ball packing ratio C of 82% or more, as in Examples 1 to 5, it is possible to achieve compactness, increase moment rigidity and rated load, and extend the bearing life, while also satisfying the bearing's functions.

[0034] <Action and effect> The ratio W / D of the assembled width W to the diameter D of the balls 4 mainly contributes to the weight reduction, compactness, and moment rigidity in Table 2. With the angular contact ball bearing 1 described above, the upper limit of the ratio W / D of the assembled width W to the diameter D of the balls 4 is set to 1.9, making it lighter and more compact in the axial direction than a standard angular contact ball bearing, and enabling the compactification of devices and the like that use this angular contact ball bearing 1. With the lower limit of W / D set to 1.3, the moment rigidity required for an angular contact ball bearing can be ensured.

[0035] The ratios H1 / D and H2 / D of the groove depth H1 of the inner ring 2 and the groove depth H2 of the outer ring 3 to the diameter D of the balls 4 in Table 2 mainly contribute to shoulder riding and therefore to the bearing life. H1 / D and H2 / D are set to 0.3 or more and 0.5 or less, respectively. In this case, since the groove depth is deeper than that of a standard angular contact ball bearing, shoulder riding can be prevented from occurring when a large moment load is applied. This prevents the raceway surfaces 2a, 3a of the inner and outer rings 2, 3 from peeling, and extends the life of the angular contact ball bearing 1. In this way, shoulder riding can be prevented and a long life can be achieved. If the groove depths H1 / D and H2 / D relative to the ball diameter are less than 0.3, there is a risk of shoulder-riding when a large moment load is applied. If H1 / D and H2 / D exceed 0.5, it becomes difficult to machine the grooves of the inner and outer rings 2 and 3, resulting in poor productivity.

[0036] The ratio A / B of each groove bottom thickness A to pitch circle diameter B mainly contributes to compactness in Table 2. It also contributes to bearing rigidity. By setting the ratio A / B of each groove bottom thickness A to pitch circle diameter B to a percentage of 1.3% or more and 2.9% or less, it is possible to set a large ball diameter while ensuring bearing rigidity. If A / B is less than 1.3%, it may be difficult to ensure bearing rigidity. If A / B exceeds 2.9%, it becomes difficult to achieve radial compactness. The filling rate C mainly contributes to the rated load, and therefore to the bearing life in Table 2. By setting the filling rate C of the balls 4 to be between 82% and 91%, a large number of balls can be secured, increasing the rated load and thereby extending the life of the angular contact ball bearing 1. If the filling rate C of the balls 4 exceeds 91%, the circumferential width between the pockets of the cage 5 becomes thin, causing strength problems.

[0037] By setting R / D to 1.01 or more and 1.07 or less, it is possible to more reliably ensure the bearing rigidity and prevent shoulder riding. If R / D is less than 1.01, the rolling resistance becomes undesirably large. If R / D exceeds 1.07, there is a risk of shoulder riding when a large moment load is applied, limiting the conditions of use. If d / B is 0.84 or more and 0.93 or less, the radial thickness of the inner ring 2 can be thinned, making devices using the angular ball bearing 1 more compact and space-saving. If d / B is less than 0.84, the effect of thinning the inner ring 2 is low. If d / B exceeds 0.93, it may be difficult to ensure the rigidity of the inner ring 2.

[0038] When D1 / B is 1.07 or more and 1.16 or less, the radial thickness of the outer ring 3 can be thinned, making it possible to make devices that use the angular ball bearing 1 more compact and space-saving. When D1 / B is less than 1.07, it may be difficult to ensure the rigidity of the outer ring 3. When D1 / B exceeds 1.16, the effect of thinning the outer ring 3 is reduced.

[0039] The angular ball bearing 1 can also be used in a face-to-face combination, a parallel combination, etc. The angular ball bearing 1 can also be used in a multi-row combination of three or more rows. The cage 5 may be, for example, a comb-type cage made of resin or the like, or may be a cylindrical cage made of resin or the like with each pocket formed as a round hole along the radial direction.

[0040] The inner member includes, for example, one in which the inner ring and shaft are integrated, and one in which a gear is formed on the inner peripheral surface of the inner ring, etc. The outer member includes one in which the outer ring and housing are integrated, and one in which a gear, flange, etc. are formed on the outer peripheral surface of the outer ring, etc. The term "integral" means that the raceway ring and the object are not formed by combining multiple elements, but are formed as part or the whole of a single object from a single material by, for example, forging or machining.

[0041] Although the embodiment of the present invention has been described above, the disclosed embodiment is illustrative in all respects and is not restrictive. The scope of the present invention is indicated by the claims, not by the above description, and is intended to include all modifications within the meaning and scope of the claims. [Explanation of symbols]

[0042] 1...Angular contact ball bearing 2...Inner ring (inner component) 3...Outer ring (outer component) 4…ball

Claims

1. An angular ball bearing comprising an inner member, an outer member, raceway surfaces formed on the outer peripheral surface of the inner member and the inner peripheral surface of the outer member, shoulders formed on the outer diameter of the inner member and the inner diameter of the outer member, and a plurality of balls interposed between the inner member and the outer member with a contact angle, wherein the ratio W / D of the axial dimension W, which is the axial dimension from the axial end face of the shoulder of the inner member to the axial end face of the shoulder of the outer member, to the diameter D of the ball is 1.3 or more and 1.9 or less, the ratio H1 / D of the groove depth H1 from the groove bottom of the raceway surface of the inner member to the outer diameter surface of the shoulder of the inner member to the diameter D of the ball is 0.3 or more and 0.5 or less, and the ratio H2 / D of the groove depth H2 from the groove bottom of the raceway surface of the outer member to the inner diameter surface of the shoulder of the outer member to the diameter D of the ball is 0.3 or more and 0.5 or less, and the percentage of the ratio A / B of the groove bottom wall thickness A of each of the inner member and the outer member to the pitch circle diameter B of the ball is 1.3% or more and 2.9% or less, and the filling rate of the balls is 82% or more. An angular ball bearing.

2. The angular ball bearing according to claim 1, wherein the ratio R / D of the groove curvature R of each raceway surface of the inner member and the outer member to the diameter D of the ball is 1.01 or more and 1.07 or less. An angular ball bearing.

3. The angular ball bearing according to claim 1 or claim 2, wherein the ratio d / B of the inner diameter d of the inner member to the pitch circle diameter B of the ball is 0.84 or more and 0.93 or less. An angular ball bearing.

4. The angular ball bearing according to claim 1 or claim 2, wherein the ratio D1 / B of the outer diameter D1 of the outer member to the pitch circle diameter B of the ball is 1.07 or more and 1.16 or less. An angular ball bearing.

5. The angular ball bearing according to claim 1 or claim 2, wherein the contact angle is 30° or more and 45° or less. An angular ball bearing.

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