JP2014126195A - Angular contact ball bearing - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an angular contact ball bearing capable of improving strength of a cage and satisfying a function of the cage at the time of high-speed rotation.SOLUTION: An inner peripheral surface of an outer ring 3 has an outer ring small diameter shoulder part 3b formed at an axial one side of an outer ring raceway surface 3a and a large diameter counterbore 3c that is formed at the axial other side of the outer ring raceway surface 3a and is larger in diameter than the outer ring small diameter shoulder part 3b. A solid cage 11 comprises a one-side annular part 15a and the other-side annular part 15b each of which is arranged at one axial side and the other axial side; a plurality of columns 17 axially connecting the one-side annular part 15a and the other-side annular part 15b; and a plurality of pockets 9 defined by the one-side annular part 15a, the other-side annular part 15b and the plurality of columns 17 so as to rotatably hold a plurality of balls 7. The outer peripheral surface of the solid cage 11 is formed as a stepped shape having different outer diameters φDO2, φDO1 of the one-side annular part and the other-side annular part 15b and a relation between an inner diameter φA2 of the outer ring small diameter shoulder part 3b and the outer diameter φDO1 of the other-side annular part 15b is set as φA2<φDO1.

Description

  The present invention relates to an angular contact ball bearing.

  In recent machine tools, there is an increasing demand for high-efficiency machining, such as machining of difficult-to-cut materials such as monolithic products from materials such as aircraft parts or titanium alloy materials. In order to cope with these, the speed of machine tool spindles is increasing.

  Precision angular ball bearings are used as rolling bearings used for these high-speed rotation spindles. When a precision angular contact ball bearing rotates at a high speed, the influence of centrifugal force cannot be ignored, and an optimum internal design specification corresponding to the centrifugal force is required as a bearing. Here, a large centrifugal force also acts on the ball that revolves while rotating by the rotation of the inner ring. Therefore, as a design specification corresponding to this, a general standard especially for a spindle having a bearing dmn value of 500,000 or more. Compared to angular contact ball bearings (for example, angular contact ball bearings with a diameter series of “0” defined by ISO, see FIG. 9A), a specially designed small diameter angular contact ball bearing (see FIG. 9A). 9 (b)) is used. More specifically, as the small-diameter ball angular contact ball bearing, when the cross-sectional height of the bearing is Y and the diameter of the ball is Da, a bearing with Da / Y <0.5 is used.

In such small-diameter ball angular contact ball bearings, by reducing the ball diameter, the centrifugal force applied to the balls is smaller than that of general standard angular contact ball bearings, and the bearing internal load increases due to the centrifugal force during high-speed rotation. Can also be reduced. In addition, recently, a bearing in which the ball diameter is reduced and a ceramic material having a specific gravity smaller than that of steel (for example, silicon nitride: Si ₃ N ₄ ) is used as a ball material to further reduce centrifugal force. Has also been used. By these measures, the bearing temperature rise during high-speed rotation can be reduced, and the processing accuracy can be improved, and problems such as seizure due to oil film breakage at the rolling contact portion can be prevented.

  Moreover, in these high-speed rotation applications, the cage material is not a metal material having a large specific gravity, such as lightweight phenol, polyamide (PA), polyphenylene sulfide (PPS), polyetheretherketone (PEEK), polyimide (PI), etc. Synthetic resin materials are widely used. These synthetic resin materials have good sliding contact friction characteristics with balls and inner and outer rings, but have a lower tensile strength than metal materials.

  Here, also in the angular ball bearing described in Patent Document 1, a synthetic resin material is adopted as a material of the cage, and the weight of the cage is reduced and the sliding contact friction characteristics are improved.

JP 2008-240796 A

  However, when the ball diameter is reduced as in the small-diameter ball angular contact ball bearing shown in FIG. 9B, the radial width of the cage must be reduced accordingly. Therefore, in the case of adopting a synthetic resin as a cage material in a small-diameter ball angular contact ball bearing, it is necessary to ensure the cage strength.

  The present invention has been made in view of the above-described problems, and an object thereof is to provide an angular contact ball bearing capable of improving the strength of the cage and satisfying the function of the cage during high-speed rotation. is there.

The above object of the present invention can be achieved by the following constitution.
(1) an outer ring having an outer ring raceway surface on the inner circumferential surface;
An inner ring having an inner ring raceway surface on the outer peripheral surface;
A plurality of balls disposed at predetermined intervals in the circumferential direction between the outer ring raceway surface and the inner ring raceway surface;
A cage for holding the plurality of balls in a rollable manner;
An angular contact ball bearing comprising:
The outer peripheral surface of the outer ring is formed on the outer ring small-diameter shoulder portion on one side in the axial direction of the outer ring raceway surface and on the other axial side of the outer ring raceway surface, and has a larger diameter than the outer ring small-diameter shoulder portion. An outer ring large-diameter shoulder,
The cage includes a one-side annular portion and the other-side annular portion that are respectively arranged on one side and the other side in the axial direction, and a plurality of column portions that connect the one-side annular portion and the other-side annular portion in the axial direction; The outer circumferential surface of the cage has a plurality of pocket portions defined by the one-side annular portion, the other-side annular portion, and the plurality of pillar portions, and holding the plurality of balls in a rollable manner. , The one-side annular portion and the other-side annular portion have different stepped shapes,
The inner diameter of the outer ring small diameter shoulder is φA2,
When the outer diameter of the other annular portion is φDO1,
φA2 <φDO1
Angular contact ball bearings characterized by being.
(2) When the outer diameter of the column is φDO3,
φA2 <φDO3
The angular ball bearing as set forth in (1), wherein
(3) The outer peripheral surface of the inner ring is formed on one side in the axial direction of the inner ring raceway surface, on the other side in the axial direction of the inner ring raceway surface, and on the other side in the axial direction of the inner ring raceway surface. An inner ring large-diameter shoulder having a larger diameter than the inner ring small-diameter shoulder, the inner peripheral surface of the cage being the one-side annular portion And a stepped shape having a different inner diameter of the other annular portion,
The inner diameter of the other annular portion is φdi1,
When the inner diameter of the one-side annular portion is φdi2,
φdi2 <φdi1
The angular ball bearing according to (1) or (2), characterized in that:
(4) The inner peripheral surface of the pillar portion has a protruding portion that protrudes toward the inner peripheral side and faces the inner ring raceway surface in the radial direction,
The inner diameter of the protrusion is φdi3,
The outer diameter of the inner ring large diameter shoulder is φB1,
When the inner diameter of the inner ring small diameter shoulder is φB2,
φB2 <φdi3 <φB1
The angular contact ball bearing according to (3), characterized in that:
(5) The angular ball bearing according to any one of (1) to (4), wherein the cage is a ball guide system.
(6) The angular ball bearing according to any one of (1) to (4), wherein the cage is an outer ring guide system.

According to the rolling bearing cage of the present invention, the relationship between the outer diameter φDO1 of the other-side annular portion of the cage and the inner diameter φA2 of the outer ring small-diameter shoulder is set so that φA2 <φDO1. The radial width of the annular portion can be increased, and the strength of the cage can be improved. This makes it possible to satisfy the functions of the cage during high-speed rotation (deformation suppression due to centrifugal force, prevention of breakage, and prevention of galling and noise due to changes in the cage guide gap).
Furthermore, it is possible to prevent the cage from being mistakenly assembled in the opposite axial direction with respect to the outer ring during the manufacture of the bearing.

It is sectional drawing of the angular ball bearing which concerns on 1st Embodiment of this invention. It is sectional drawing of a machined cage. It is a partial top view of a machined cage. It is a fragmentary sectional view which follows the IV-IV line in FIG. It is sectional drawing of the angular ball bearing which concerns on 2nd Embodiment. It is sectional drawing of the angular ball bearing which concerns on the modification of 2nd Embodiment. It is sectional drawing of the angular ball bearing which concerns on 3rd Embodiment. It is sectional drawing of the back combination angular contact ball bearing which concerns on 4th Embodiment. (A) is the conventional standard angular contact ball bearing, (b) is the conventional small diameter ball angular contact ball bearing.

  Hereinafter, each embodiment of the angular ball bearing according to the present invention will be described in detail with reference to the drawings.

(First embodiment)
As shown in FIG. 1, the angular ball bearing 1 according to the first embodiment includes an outer ring 3 having an outer ring raceway surface 3a on an inner peripheral surface, an inner ring 5 having an inner ring raceway surface 5a on an outer peripheral surface, and an outer ring raceway surface 3a. Between the outer ring 3 and the inner ring 5 by holding a plurality of balls 7 arranged at predetermined intervals in the circumferential direction between the inner ring raceway surface 5a and the inner ring raceway surface 5a. And a machined cage 11 disposed on the machine. Further, the angular ball bearing 1 has a contact angle θ when stationary, and applies a radial load and a thrust load. Grease as a lubricant is sealed in the internal space of the angular ball bearing 1.

  Further, the angular ball bearing 1 is set so that the ball diameter is small. More specifically, when the sectional height Y of the bearing is Da and the diameter of the ball 7 is Da, Da / Y <0.5. Is a small-diameter ball angular contact ball bearing. However, if the ball diameter is made too small, the performance regarding the allowable load and fatigue life of the angular ball bearing 1 cannot be satisfied. Therefore, Da / Y ≧ 0.3, more preferably, Da / Y ≧ 0.35 can be set. desirable.

  The outer ring 3 has an outer ring small-diameter shoulder 3b on one axial side (left side in FIG. 1) of the outer ring raceway surface 3a and an outer ring small-diameter shoulder 3b on the other axial side (right side in FIG. 1). Counterbore 3c is formed as a large-diameter outer ring shoulder with a larger diameter. Here, in FIG. 1, the inner diameter of the outer ring small-diameter shoulder portion 3b is represented by φA2, and the inner diameter of the innermost circumferential portion of the counter bore 3c is represented by φA1.

  The inner ring 5 has an inner ring small-diameter shoulder 5b on one side in the axial direction of the inner ring raceway surface 5a, that is, on the side opposed to the outer ring small-diameter shoulder 3b in the radial direction, and the other side in the axial direction, that is, counter bore 3c in the radial direction. An inner ring large-diameter shoulder portion 5c having a larger diameter than the inner ring small-diameter shoulder portion 5b is formed on the opposite side. Here, in FIG. 1, the outer diameter of the inner ring small-diameter shoulder 5b is represented as φB2, and the outer diameter of the inner ring large-diameter shoulder 5c is represented as φB1.

  The machined cage 11 is a ball guide type cage made of a synthetic resin in which glass fiber (GF) is added to polyamide (PA) resin to improve the strength. 2 and 3, the machined cage 11 is arranged on one side in the axial direction, and has one side annular portion 15 a that is radially opposed to the outer ring small diameter shoulder 3 b and the inner ring small diameter shoulder 5 b, and the axial direction. The other side annular portion 15b arranged on the other side and radially opposed to the counter bore 3c and the inner ring large-diameter shoulder portion 5c of the outer ring 3, a plurality of column portions 17 connecting these annular portions 15a and 15b, and the column portion 17 Of the inner peripheral surface of the inner peripheral surface of the inner peripheral surface of the inner peripheral surface of the inner peripheral surface of the inner peripheral surface. A plurality of pocket portions 9 for holding the balls 7 so as to roll freely are constituted by the portions 18.

  The outer peripheral surface of the machined cage 11 has a stepped shape in which the outer diameter φDO2 of the one-side annular portion 15a, the outer diameter φDO1 of the other-side annular portion 15b, and the outer diameter φDO3 of the column portion 17 are different. More specifically, the outer diameter of the outer peripheral surface of the machined cage 11 is set so as to change in accordance with the inner diameter of the outer ring 3, and “the inner diameter φA1 of the innermost peripheral portion of the counterbore 3c> the other side The outer diameter φDO1 of the annular portion 15b = the outer diameter φDO3 of the column portion 17> the inner diameter φA2 of the outer ring small-diameter shoulder portion 3b> the outer diameter φDO2 of the one-side annular portion 15a ”.

  Accordingly, the radial width of the other annular portion 15b and the column portion 17 can be increased while preventing the contact between the machined cage 11 and the counter bore 3c of the outer ring 3, and the strength of the machined cage 11 can be improved. Is possible. Further, when the machined cage 11 is assembled to the outer ring 3, it can be prevented that the machined cage 11 is mistakenly assembled in the opposite axial direction.

  If the above relationship is not satisfied and a cage having an asymmetric shape in the axial direction is mistakenly assembled in the opposite direction in the axial direction, an appropriate gap between the outer ring and the cage cannot be secured, and the ball guide system is also used. Regardless, contact failure between the outer ring and the cage may occur.

  Further, the inner peripheral surface of the machined cage 11 has a stepped shape in which the inner diameter φdi2 of the one-side annular portion 15a, the inner diameter φdi1 of the other-side annular portion 15b, and the inner diameter φdi3 of the protrusion 18 of the column portion 17 are different. It is said that. More specifically, the inner diameter of the inner peripheral surface of the machined cage 11 is set so as to change in accordance with the outer diameter of the inner ring 5, and “the inner diameter φdi1 of the other-side annular portion 15b> one-side annular portion. The inner diameter φdi2 of the inner ring 15a> the outer diameter φB1 of the inner ring large-diameter shoulder 5c> the inner diameter φdi3 of the protrusion 18 of the column part 17> the outer diameter φB2 of the inner ring small-diameter shoulder 5b ”.

Thus, according to the outer diameter of the inner ring 5, “the inner diameter φdi1 of the other-side annular portion 15b> the inner diameter φdi2 of the one-side annular portion 15a” is set, so the one-side annular portion 15a and the other-side annular portion 15b. It is possible to increase the thickness of the machined cage 11 in the radial direction.
Further, by setting so that “the outer diameter φB1 of the inner ring large-diameter shoulder portion 5c> the inner diameter φdi3 of the protrusion 18 of the pillar portion 17> the outer diameter φB2 of the inner ring small-diameter shoulder portion 5b,” It is possible to increase the radial width of the column portion 17 while allowing the punch holder 11 to be incorporated, and to further improve the strength of the punch holder 11.

  In the above-described embodiment, the configuration is such that “the inner diameter φdi1 of the other-side annular portion 15b> the inner diameter φdi2 of the one-side annular portion 15a> the outer diameter φB1 of the inner ring large-diameter shoulder portion 5c”. The inner diameter φdi1 of 15b> the outer diameter φB1 of the inner ring large-diameter shoulder 5c> the inner diameter φdi2 of the one-side annular portion 15a ”may be satisfied.

  As shown in FIGS. 2 to 4, the pocket portion 9 of the machined cage 11 includes a cylindrical surface 9 a formed by a cylindrical shape having a center line G extending in the radial direction, and an inner diameter side of the cylindrical surface 9 a. It has a pair of taper surfaces 9b which continue to the cylindrical surface 9a and extend toward the center line G as it is away from the cylindrical surface 9a, and are formed so as to penetrate in the radial direction.

  The pair of tapered surfaces 9b are provided on the adjacent column portions 17 and 17, respectively, and are formed by the cylindrical surface 9a and the inner diameter side convex portions 19 and 19 extending from the pair of protrusions 18 and 18 toward the center line G. The pocket portion 9 is arranged on both sides in the circumferential direction. Thus, since the inner diameter side convex part 19 which forms the taper surface 9b is not provided in the axial direction both sides in the pocket part 9, a clearance gap is made between the ball | bowl 7 and the pocket part 9, and it is lubricant from the said clearance gap. Can be supplied. In addition, it is good also as a structure which provides the internal-diameter side convex part 19 so that the cylindrical surface 9a whole periphery of the pocket part 9 may be followed as needed.

  Further, the inner diameter side convex portion 19 has a straight surface 9c formed substantially parallel to the center line G by chamfering at the inner diameter side end portion of the tapered surface 9b. The straight surface 9c prevents the occurrence of defects such as burrs and whiskers when the machined cage 11 is cut or injection molded. The inner diameter side convex portion 19 may be formed with an R-shaped curved surface instead of the straight surface 9c described above.

  Here, the radial displacement of the machined cage 11 is defined by the ball 7 coming into contact with the ball locking portion P of the tapered surface 9 b of the inner diameter side convex portion 19. That is, when the machined cage 11 is moved outward in the radial direction by the radial gap (radial guide gap 2 × F) between the ball 7 and the ball locking portion P of the tapered surface 9b, that is, the ball 7 is relatively moved. Is moved radially inward, the machined cage 11 is configured such that contact with the ball 7 is restricted by the ball locking portion P of the tapered surface 9b.

  When the position of the ball locking portion P is determined in order to set the radial movement amount of the machined cage 11 to an optimum value in design, as described above, in the present embodiment, “the inner ring large-diameter shoulder portion 5c”. The outer diameter φB1> the inner diameter φdi3 of the protrusion 18 of the column portion 17> the outer diameter φB2 of the inner ring small diameter shoulder portion 5b ”is satisfied, so that the inner diameter φdi3 of the protrusion 18 of the column portion 17 can be reduced. . That is, since the radial width R of the straight surface 9c of the inner diameter side convex portion 19 extending from the protrusion 18 can be increased, the strength of the straight surface 9c can be improved.

  Such a cage 11 can be manufactured by various methods. For example, the cage 11 may be manufactured by cutting or may be manufactured by injection molding.

As described above, according to the angular ball bearing 1 of the present embodiment, since the outer diameter φDO1 of the other-side annular portion 15b> the inner diameter φA2 of the outer ring small-diameter shoulder portion 3b ”is set, the other-side annular portion The radial width of 15b can be increased, and the strength of the machined cage 11 can be improved. As a result, it is possible to satisfy the functions of the machined cage 11 during high-speed rotation (deformation suppression, breakage prevention due to centrifugal force, prevention of galling and abnormal noise due to changes in the cage guide gap 2 × F).
Furthermore, it is possible to prevent the machined cage 11 from being mistakenly assembled in the axially opposite direction with respect to the outer ring 3 during the manufacture of the bearing.

  Further, since the outer diameter φDO3 of the pillar portion 17 is set to satisfy the inner diameter φA2 of the outer ring small diameter shoulder portion 3b, the radial width of the pillar portion 17 can be increased, and the strength of the machined cage 11 is further improved. It is possible.

  Further, the inner ring 5 is set so that “the inner diameter φdi1 of the other-side annular portion 15b> the inner diameter φdi2 of the one-side annular portion 15a” according to the outer diameter of the inner ring 5, the diameters of the one-side annular portion 15a and the other-side annular portion 15b. The direction width can be increased, and the strength of the machined cage 11 can be improved.

  Furthermore, the radial direction of the column portion 17 is set by satisfying “the outer diameter φB1 of the inner ring large-diameter shoulder portion 5c> the inner diameter φdi3 of the protrusion 18 of the column portion 17> the outer diameter φB2 of the inner ring small-diameter shoulder portion 5b”. The width can be increased, and the strength of the machined cage 11 can be further improved.

(Second Embodiment)
Next, an angular ball bearing according to the second embodiment will be described. Since the angular ball bearing of the present embodiment has the same basic configuration as that of the first embodiment, the same or corresponding parts are denoted by the same reference numerals, the description thereof will be omitted or simplified, and the different parts will be described in detail. .

  As shown in FIG. 5, the machined cage 11 of the angular ball bearing 1 according to the present embodiment is made of a synthetic resin in which strength is improved by adding glass fiber (GF) to polyphenylene sulfide (PPS) resin, This is an outer ring guide type cage in which the one-side annular portion 15a is guided by the outer ring small-diameter shoulder 3b. Here, the radial guide clearance is represented by a difference (φA2−φDO2 = 2 × E) between the inner diameter φA2 of the outer ring small-diameter shoulder 3b of the outer ring 3 and the outer diameter φDO2 of the one-side annular portion 15a.

  Thus, even when the machined cage 11 is the outer ring guide system, “the inner diameter φA1 of the innermost peripheral portion of the counter bore 3c> the outer diameter φDO1 of the other annular portion 15b = the outer diameter of the column portion 17”. Since it is formed so as to satisfy the relationship of “φDO3> the inner diameter φA2 of the outer ring small-diameter shoulder portion 3b> the outer diameter φDO2 of the one-side annular portion 15a”, the radial width of the other-side annular portion 15b and the column portion 17 can be increased. It is possible to improve the strength of the machined cage 11. Further, when the machined cage 11 is assembled to the outer ring 3, it can be prevented that the machined cage 11 is mistakenly assembled in the opposite axial direction.

  If the above relationship is not satisfied and a cage having an asymmetric shape in the axial direction is mistakenly assembled in the opposite direction in the axial direction, an appropriate radial guide clearance (2 × E) between the outer ring and the cage is secured. It is not possible, and there is a risk that the guide surface will be galled or seized.

  Further, since the relationship of “the outer diameter φB1 of the inner ring large-diameter shoulder portion 5c> the inner diameter φdi3 of the protrusion 18 of the column portion 17> the outer diameter φB2 of the inner ring small-diameter shoulder portion 5b” is satisfied, the radial width of the column portion 17 is increased. It is possible to further improve the strength of the machined cage 11.

  Other configurations and effects are the same as those of the first embodiment.

(Modification)
As shown in FIG. 6, the angular ball bearing 1 of the present embodiment does not necessarily need to be provided with the protrusion 18 on the inner peripheral surface of the column portion 17. In this case, “the inner diameter φdi1 of the other-side annular portion 15 b”. > The inner diameter φdi3 ′ of the column portion 17 = the inner diameter φdi2 of the one-side annular portion 15a ”may be satisfied.

(Third embodiment)
Next, an angular ball bearing according to the third embodiment will be described. Since the angular ball bearing of the present embodiment has the same basic configuration as that of the first embodiment, the same or corresponding parts are denoted by the same reference numerals, the description thereof will be omitted or simplified, and the different parts will be described in detail. .

  As shown in FIG. 7, the angular ball bearing 1 according to the present embodiment is formed in an annular shape with a cored bar 12 covered with an elastic body 13 such as rubber at openings on both axial sides of the outer ring 3 and the inner ring 5. A pair of sealing members 14 are provided to prevent grease from flowing out from the inside. The machined cage 11 is a ball guide type cage made of a synthetic resin in which carbon fiber (CF) is added to polyamide (PA) resin to improve the strength.

  Further, the inner peripheral surface of the outer ring 3 is not formed with a counter bore on the other axial side of the outer ring raceway surface 3a (right side in FIG. 7), and has a larger diameter and a planar shape than the outer ring small-diameter shoulder 3b. The outer ring large-diameter shoulder 3c 'is formed. On the other hand, a counter bore 5b ′ is formed on the outer peripheral surface of the inner ring 5 on one side in the axial direction of the inner ring raceway surface 5a (left side in FIG. 7).

  Even when configured as described above, the same effects as those of the first embodiment can be obtained by setting the dimensional relationship similar to that of the first embodiment.

(Fourth embodiment)
Moreover, you may use the angular contact ball bearing 1 which concerns on the above-mentioned embodiment combining two backs. FIG. 8 illustrates a state in which the additive material of the machined cage 11 is changed to carbon fiber (CF) in the angular ball bearing 1 according to the first embodiment, and the back surface is combined in two rows. It goes without saying that the angular ball bearings 1 of the embodiment or the third embodiment may be combined in two rows on the back.

In addition, this invention is not limited to embodiment mentioned above, A deformation | transformation, improvement, etc. are possible suitably.
For example, the rolling bearing of the present invention may be suitably used for supporting a main shaft in a main shaft device such as a machine tool, or may be applied to support a motor shaft of a high-speed motor.

  In addition to the synthetic resin described in the above embodiment, the cage material may be polyimide (PI), phenol resin, or the like as a base material, or aramid fiber as a reinforcing material.

1 Angular contact ball bearing 3 Outer ring 3a Outer ring raceway surface 3b Outer ring small diameter shoulder 3c Counter bore (outer ring large diameter shoulder)
3c 'outer ring large diameter shoulder 5 inner ring 5a inner ring raceway surface 5b inner ring small diameter shoulder 5b' counter bore (inner ring small diameter shoulder)
5c Inner ring large diameter shoulder 7 Ball 9 Pocket 9a Cylindrical surface 9b Tapered surface 9c Straight surface 11 Machined cage (Cage)
12 Core metal 13 Elastic body 14 Seal member 15a One side annular portion 15b The other side annular portion 17 Column portion 18 Projection portion 19 Inner diameter side convex portion

Claims (6)

An outer ring having an outer ring raceway surface on the inner circumferential surface;
An inner ring having an inner ring raceway surface on the outer peripheral surface;
A plurality of balls disposed at predetermined intervals in the circumferential direction between the outer ring raceway surface and the inner ring raceway surface;
A cage for holding the plurality of balls in a rollable manner;
An angular contact ball bearing comprising:
The outer peripheral surface of the outer ring is formed on the outer ring small-diameter shoulder portion on one side in the axial direction of the outer ring raceway surface and on the other axial side of the outer ring raceway surface, and has a larger diameter than the outer ring small-diameter shoulder portion. An outer ring large-diameter shoulder,
The cage includes a one-side annular portion and the other-side annular portion that are respectively arranged on one side and the other side in the axial direction, and a plurality of column portions that connect the one-side annular portion and the other-side annular portion in the axial direction; The outer circumferential surface of the cage has a plurality of pocket portions defined by the one-side annular portion, the other-side annular portion, and the plurality of pillar portions, and holding the plurality of balls in a rollable manner. , The one-side annular portion and the other-side annular portion have different stepped shapes,
The inner diameter of the outer ring small diameter shoulder is φA2,
When the outer diameter of the other annular portion is φDO1,
φA2 <φDO1
Angular contact ball bearings characterized by being. When the outer diameter of the column portion is φDO3,
φA2 <φDO3
The angular ball bearing according to claim 1, wherein: The outer peripheral surface of the inner ring is formed on one side in the axial direction of the inner ring raceway surface, and is formed on the other side in the axial direction of the inner ring raceway surface. And an inner ring large-diameter shoulder portion that is radially opposed to the other-side annular portion and is larger in diameter than the inner ring small-diameter shoulder portion, and the inner peripheral surface of the cage includes the one-side annular portion and the other It is a stepped shape with a different inner diameter of the side annular part,
The inner diameter of the other annular portion is φdi1,
When the inner diameter of the one-side annular portion is φdi2,
φdi2 <φdi1
The angular ball bearing according to claim 1 or 2, wherein The inner peripheral surface of the column portion is provided to protrude toward the inner peripheral side, and has a protrusion that faces the inner ring raceway surface in the radial direction,
The inner diameter of the protrusion is φdi3,
The outer diameter of the inner ring large diameter shoulder is φB1,
When the inner diameter of the inner ring small diameter shoulder is φB2,
φB2 <φdi3 <φB1
The angular ball bearing according to claim 3, wherein: The angular ball bearing according to claim 1, wherein the cage is a ball guide system. The angular ball bearing according to claim 1, wherein the cage is an outer ring guide system.

Images