CN117662606A - Bearing device for wheel - Google Patents

Abstract

The invention provides a bearing device for a wheel, which can inhibit interference between an outer member and a retainer of a rolling element and increase of torque, and can improve service life. A bearing device (1) for a wheel is provided with: an outer ring (2) having double-row outer raceway surfaces (23, 24); an inner member (hub wheel (3) and inner ring (4)) having double-row inner raceway surfaces (33, 41) opposed to the double-row outer raceway surfaces (23, 24); double row ball rows (5, 6) which are accommodated between the outer ring (2) and the two raceway surfaces of the inner member so as to be freely rotatable; and a cage (8) for holding the balls (7) of the ball rows (5, 6), wherein the distances (h 1, h 2) between the bottoms (23 a, 24 a) and the shoulders (23 b, 24 b) of the outer track surfaces (23, 24) in the radial direction satisfy the relation of h.gtoreq.0.7xr (h=h1, h 2) with the radius (r) of the balls (7), and the shortest distances (d 1, d 2) between the annular part (81) of the cage (8) and the inner peripheral surface (28) of the outer ring (2) are 0.2mm or more and 2mm or less.

Description

Bearing device for wheel

Technical Field

The present invention relates to a bearing device for a wheel.

Background

Conventionally, a wheel bearing device for rotatably supporting a wheel in a suspension device of a vehicle such as an automobile is known.

In vehicles using wheel bearing devices, it is desired to expand the popularity of electric vehicles, but there is a tendency that the weight of the electric vehicle is increased due to the mounting of a battery, and the wheel bearing devices used in the electric vehicles are also required to be increased in size and rigidity. However, simply increasing the size of the wheel bearing apparatus causes a problem that the weight of the wheel bearing apparatus increases.

Accordingly, as disclosed in patent document 1, in a bearing device for a wheel including a double row rolling element group interposed between an outer ring raceway surface of an outer ring member and an inner ring raceway surface of an inner ring member, the pitch circle diameter of the rolling element group on the outer ring side is set to be larger than the pitch circle diameter of the rolling element group on the inner ring side, thereby realizing an increase in size while suppressing an increase in weight.

Prior art literature

Patent literature

Patent document 1: japanese patent No. 4206716

On the other hand, in the wheel bearing device, the radial dimension is made larger and the axial dimension is made smaller, so that the rigidity can be improved, and the weight and space can be reduced.

However, if the wheel bearing apparatus is miniaturized in the axial direction, rigidity and lifetime tend to be reduced. For example, when the wheel bearing apparatus is subjected to a rotational load, an elliptical contact surface formed when the outer raceway surface of the outer member contacts the rolling elements protrudes toward the shoulder of the outer raceway surface, and there is a concern that stress concentrates on the shoulder of the outer raceway surface and is broken in advance.

In order to suppress the protrusion of the contact surface of the rolling element toward the shoulder portion of the outer raceway surface, it is considered to increase the distance between the bottom portion of the outer raceway surface and the shoulder portion, but if the distance between the bottom portion of the outer raceway surface and the shoulder portion is excessively increased, the inner peripheral surface of the outer member interferes with the cage holding the rolling element, and there is a possibility that the torque increases due to the shearing resistance of the grease.

Disclosure of Invention

Problems to be solved by the invention

The present invention has been made in view of the above circumstances, and provides a bearing device for a wheel capable of improving the life while suppressing interference between an outer member and a cage of a rolling element and an increase in torque.

Means for solving the problems

Specifically, the wheel bearing device includes: an outer member having a double-row outer raceway surface on an inner periphery thereof; an inner member having a double-row inner raceway surface opposed to the double-row outer raceway surface; a double row rolling element housed between both raceway surfaces of the outer member and the inner member so as to be freely rolling; and a cage that holds the rolling elements, the cage having: a circular ring portion formed in a ring shape; a plurality of column portions extending from the annular portion in the axial direction and arranged at regular intervals in the circumferential direction; and a groove formed by the annular portion and the adjacent pillar portion and holding the rolling element, wherein, in at least one of the outer raceway surface on one axial side and the outer raceway surface on the other axial side of the double-row outer raceway surface, a distance h in a radial direction between a bottom portion of the outer raceway surface and a shoulder portion thereof satisfies a relation of h.gtoreq.0.7xr with a radius r of the rolling element, and a shortest distance d between the annular portion of the cage and an inner peripheral surface of the outer member opposed to the annular portion is 0.2mm or more and 2mm or less.

Effects of the invention

According to the present invention, it is possible to improve the life of the wheel bearing device while suppressing interference between the outer member and the retainer of the rolling element and an increase in torque.

Drawings

Fig. 1 is a side sectional view showing a bearing device for a wheel.

Fig. 2 is a side cross-sectional view showing an outer raceway surface portion on the inner disc side in the bearing device for a wheel.

Fig. 3 is a schematic view showing the contact surface between the balls and the outer raceway surface.

Fig. 4 is a side cross-sectional view showing an outer raceway surface portion on the inner disc side in the case where the outer peripheral surface of the annular ring portion and the inner peripheral surface of the outer ring are tapered surfaces inclined with respect to the axial direction.

Fig. 5 is a side cross-sectional view showing an outer raceway surface portion on the outer disc side in the bearing device for a wheel.

Reference numerals illustrate:

1. bearing device for wheel

2. Outer ring

3. Hub wheel

4. Inner ring

5. Inner disc side ball row

6. Outer disk side rolling ball row

7. Ball bearing

8. Retainer

23 Outer track surface (of inner disc side)

23a bottom

23b shoulder

24 Outer track surface (of outer disk side)

24a bottom

24b shoulder

28. An inner peripheral surface

33 Inner track surface (of outer disk side)

41 Inner track surface (of inner disk side)

81. Circular ring part

81a outer peripheral surface

82. Column part

83. Groove

a ball space distance

b (ball) pitch diameter

d1, d2 shortest distance (between the annular portion of the retainer and the inner peripheral surface of the outer ring)

Distance of h1, h2 (bottom of outer raceway surface to shoulder)

radius of r (of ball)

Contact angles α1, α2 (of the rolling bodies relative to the outer raceway surface).

Detailed Description

Hereinafter, a specific embodiment of the present invention will be described with reference to the drawings.

[ bearing device for wheel ]

The wheel bearing apparatus 1 shown in fig. 1 is an embodiment of the wheel bearing apparatus of the present invention, and is an apparatus for rotatably supporting a wheel in a suspension apparatus of a vehicle such as an automobile.

In the following description, the axial direction indicates a direction along the rotation axis X of the wheel bearing apparatus 1. The outer disc side represents one side in the axial direction, that is, the wheel side of the wheel bearing device 1 when mounted on the vehicle body, and the inner disc side represents the other side in the axial direction, that is, the vehicle body side of the wheel bearing device 1 when mounted on the vehicle body.

The wheel bearing apparatus 1 has a structure called a third generation, and includes an outer ring 2 as an outer member, a hub wheel 3 and an inner ring 4 as inner members, two rows of inner-disc-side bead rows 5 and outer-disc-side bead rows 6 as rolling rows, an outer-disc-side seal member 9, and an inner-disc-side seal member 10.

An inner-disc-side opening 21 into which the inner-disc-side seal member 10 can be fitted is formed at an inner-disc-side end portion of the outer ring 2. An outer-disc-side opening 22 into which the outer-disc-side seal member 9 can be fitted is formed at an outer-disc-side end portion of the outer ring 2.

The inner disc side opening 21 is fitted with the inner disc side sealing member 10, so that the inner disc side opening end of the annular space S formed by the outer ring 2 as the outer member and the hub wheel 3 and the inner ring 4 as the inner member is closed. The outer-disk-side opening 22 is fitted with the outer-disk-side sealing member 9, so that the outer-disk-side opening end of the annular space S is closed.

The inner-disk-side seal member 10 and the outer-disk-side seal member 9 are sealing devices that seal the open ends of the annular space S. In this way, the inner disc side and outer disc side opening ends of the annular space S are closed by the inner disc side seal member 10 and the outer disc side seal member 9, whereby penetration of foreign matter such as muddy water into the interior of the wheel bearing apparatus 1 is suppressed.

An outer raceway surface 23 on the inner disc side and an outer raceway surface 24 on the outer disc side are formed on the inner peripheral surface 28 of the outer ring 2. A vehicle body mounting flange 25 for mounting the outer ring 2 to a vehicle body side member is integrally formed on the outer peripheral surface 27 of the outer ring 2. The body mounting flange 25 is provided with bolt holes 26 into which fastening members (bolts in this case) for fastening the body-side member and the outer ring 2 are inserted.

A small diameter step 31 having a smaller diameter than the outer disk side end is formed at the inner disk side end of the outer peripheral surface of the hub wheel 3. A wheel mounting flange 32 for mounting a wheel is integrally formed at an outer disc side end portion of the hub wheel 3.

A plurality of bolt holes 35 are formed in the wheel mounting flange 32. Hub bolts 36 for fastening the hub wheel 3 to the wheel or the brake member can be pressed into the bolt holes 35.

In the hub wheel 3, a sliding contact surface 34 for sliding contact of the outer disc side seal member 9 is formed on the base side of the wheel mounting flange 32. An outer-disc-side inner raceway surface 33 is provided on the outer circumferential surface of the hub wheel 3 so as to face the outer-disc-side outer raceway surface 24 of the outer ring 2. That is, the hub wheel 3 forms the inner raceway surface 33 on the outer disc side of the inner member.

A shaft hole 37 formed in the axial direction is formed in the inner diameter portion of the hub wheel 3. The shaft hole 37 penetrates the hub wheel 3 in the axial direction, and a shaft portion of the constant velocity universal joint can be coupled to the shaft hole 37.

An inner ring 4 is provided at the small diameter step 31 of the hub wheel 3. The inner ring 4 is fixed to the small diameter step 31 of the hub wheel 3 by press fitting. An inner raceway surface 41 on the inner disk side is provided on the outer peripheral surface of the inner ring 4 so as to face the outer raceway surface 23 on the inner disk side of the outer ring 2. That is, the inner raceway surface 41 is formed by the inner ring 4 on the inner disc side of the inner member.

The inner-disk-side ball row 5 and the outer-disk-side ball row 6 as rolling rows are configured by a plurality of balls 7 as rolling elements being held by a cage 8. The inner-disc-side ball row 5 is held between the inner raceway surface 41 of the inner ring 4 and the outer raceway surface 23 of the inner ring 2 so as to be freely rotatable. The outer-disc-side bead row 6 is held between the inner raceway surface 33 of the hub wheel 3 and the outer raceway surface 24 of the outer disc side of the outer ring 2 so as to be freely rotatable. That is, the inner bead row 5 and the outer bead row 6 are housed so as to be freely rotatable between both raceway surfaces of the outer member and the inner member.

In the wheel bearing apparatus 1, a double row angular ball bearing is constituted by an outer ring 2, a hub wheel 3, an inner ring 4, an inner disc side ball row 5, and an outer disc side ball row 6. The wheel bearing apparatus 1 may be configured as a double row tapered roller bearing instead of a double row angular contact ball bearing.

[ relation between pitch diameter of balls and ball-to-ball distance in bearing device for wheel ]

The balls 7 constituting the inner-disc-side ball row 5 and the balls 7 constituting the outer-disc-side ball row 6 are arranged so that the ball-to-ball distance therebetween in the axial direction becomes a. The inter-ball distance a is the distance in the axial direction between the center P1 of the ball 7 in the inner-disc-side ball row 5 and the center P2 of the ball 7 in the outer-disc-side ball row 6. The ball-to-ball distance a is an example of the rolling element-to-rolling element distance a.

The pitch diameter of the balls 7 constituting the inner-disc-side ball row 5 and the pitch diameter of the balls 7 constituting the outer-disc-side ball row 6 are set to be the same, and the pitch diameter of the balls 7 constituting the inner-disc-side ball row 5 and the outer-disc-side ball row 6 is set to b.

The pitch diameter b is a diameter of a circle passing through the center P1 of the balls 7 in the inner ball row 5 about the rotation axis X. The pitch diameter b is a diameter of a circle passing through the center P2 of the balls 7 in the outer ball row 6 about the rotation axis X. The pitch diameter b of the ball 7 is an example of the pitch diameter b of the rolling element.

In the wheel bearing apparatus 1, the ratio (b/a) of the pitch diameter b to the inter-ball distance a is set to 2.0 or more. That is, the pitch diameter b and the ball-to-ball distance a are set so as to satisfy the relationship that b/a is not less than 2.0.

By setting the pitch diameter b and the ball-to-ball distance a so that b/a is equal to or greater than 2.0, the radial dimension of the wheel bearing apparatus 1 is made large, interference between the retainers 8 of the inner disc side ball row 5 and the retainers 8 of the outer disc side ball row 6 can be prevented, and the axial dimension of the wheel bearing apparatus 1 can be made small. This can optimize the radial size and the axial size of the wheel bearing device 1, and can reduce the weight of the wheel bearing device 1 while improving the rigidity and the life of the wheel bearing device 1.

[ relationship between the outer raceway surface and the inner peripheral surface of the outer race and the balls and the cage ]

As shown in fig. 2, the holder 8 in the inner-disk-side bead row 5 has: a circular ring portion 81 formed in a ring shape; a plurality of column portions 82 extending from the annular portion 81 toward the inner disk side in the axial direction and arranged at regular intervals along the circumferential direction; and a groove 83 formed by the annular portion 81 and the adjacent pillar portion 82 and holding the ball 7. The radius of the ball 7 held by the cage 8 is r.

The outer raceway surface 23 on the inner disk side of the outer ring 2 has a bottom portion 23a and a shoulder portion 23b. The bottom 23a is a portion located on the outermost diameter side of the outer raceway surface 23. The shoulder 23b is a boundary portion between the outer raceway surface 23 and the inner peripheral surface 28 of the outer ring 2, and is located at the outer disk side end portion of the outer raceway surface 23. The shoulder 23b is located on the innermost diameter side of the outer raceway surface 23.

The distance between the bottom 23a and the shoulder 23b of the radially outer raceway surface 23 is h1. The distance h1 is an example of the distance h. In the wheel bearing apparatus 1, the distance h1 is set to be 0.7 times or more the radius r of the ball 7. That is, the distance h1 and the radius r are set so as to satisfy the relationship that h1 is equal to or greater than 0.7×r.

The balls 7 in the inner-disc-side ball row 5 are in contact with the outer raceway surface 23 at contact points 23c, and the contact angle of the balls 7 in the inner-disc-side ball row 5 with respect to the outer raceway surface 23 is α1. The contact angle α1 is an example of the contact angle α. The contact angle α1 is an inclination angle of a straight line connecting the center P1 of the ball 7 in the inner ball row 5 and the contact point 23c with respect to the radial direction. In the wheel bearing apparatus 1, the contact angle α1 is set so as to be greater than 35 ° and equal to or less than 45 ° (35 ° < α1+.ltoreq.45°).

As shown in fig. 3, when the balls 7 in the inner ball row 5 contact the outer raceway surface 23 at the contact point 23C, an elliptical contact surface C that spreads around the contact point 23C is generated on the outer raceway surface 23.

By setting the distance h1 and the radius r so as to satisfy the relationship that h1 is equal to or greater than 0.7xr, the distance h1 can be ensured to be large, and for example, even when the wheel bearing apparatus 1 is loaded with a large load such as a turning load, the contact surface C does not protrude to the shoulder 23b of the outer raceway surface 23. This can suppress concentration of stress on the shoulder portion 23b of the outer raceway surface 23, and can improve the life of the wheel bearing apparatus 1.

In a typical wheel bearing device, the contact angle of the balls with respect to the outer raceway surface is about 35 °, whereas in the wheel bearing device 1, the contact angle α1 of the balls 7 with respect to the outer raceway surface 23 is set to be greater than 35 ° and 45 ° or less.

In this way, by setting the contact angle α1 to a large angle satisfying 35 ° < α1+.ltoreq.45°, even when the wheel bearing apparatus 1 is miniaturized in the axial direction, the reduction in rigidity of the wheel bearing apparatus 1 can be suppressed.

The annular portion 81 of the retainer 8 in the inner disc-side bead row 5 has an outer peripheral surface 81a. The outer peripheral surface 81a of the annular portion 81 faces the inner peripheral surface 28 of the outer ring 2 adjacent to the outer disk side of the outer raceway surface 23. The shortest distance between the outer peripheral surface 81a of the annular portion 81 and the inner peripheral surface 28 of the outer ring 2 facing the annular portion 81 is d1. The shortest distance d1 is an example of the shortest distance d.

As shown in fig. 2, for example, when the outer peripheral surface 81a and the inner peripheral surface 28 are surfaces along the axial direction, the shortest distance d1 between the outer peripheral surface 81a of the annular portion 81 and the inner peripheral surface 28 of the outer ring 2 is a distance between the outer peripheral surface 81a and the inner peripheral surface 28 in the radial direction.

In the case where one of the outer peripheral surface 81a and the inner peripheral surface 28 is a surface along the axial direction and the other is a tapered surface inclined with respect to the axial direction, the shortest distance d1 may be set to be the closest distance in the radial direction between the opposing outer peripheral surface 81a and the inner peripheral surface 28.

As shown in fig. 4, when the outer peripheral surface 81a and the inner peripheral surface 28 are tapered surfaces inclined with respect to the axial direction, the shortest distance d1 may be the shorter one of the distance closest to the inner peripheral surface 28 between the outer peripheral surface 81a facing in the direction orthogonal to the inner peripheral surface 28 and the distance closest to the inner peripheral surface 28 between the outer peripheral surface 81a facing in the direction orthogonal to the outer peripheral surface 81a (in fig. 4, the distance in the direction orthogonal to the inner peripheral surface 28 is shown).

In the wheel bearing apparatus 1, the shortest distance d1 between the outer peripheral surface 81a of the annular ring portion 81 and the inner peripheral surface 28 of the outer ring 2 is set to be 0.2mm or more (d1+.0.2 mm).

By providing a gap of 0.2mm or more between the outer peripheral surface 81a of the annular portion 81 and the inner peripheral surface 28 of the outer ring 2 in this way, it is possible to suppress interference between the annular portion 81 of the retainer 8 and the inner peripheral surface 28 of the outer ring 2 and to suppress an increase in torque due to shearing resistance of grease applied between the outer peripheral surface 81a of the annular portion 81 and the inner peripheral surface 28 of the outer ring 2.

The shortest distance d1 is set so as to be 2mm or less (2 mm. Gtoreq.d1). By setting the shortest distance d1 to 2mm or less in this way, it is possible to suppress the shoulder portion 23b of the outer raceway surface 23 from climbing up when the ball 7 receives a load. In order to further suppress the ball 7 from climbing up the shoulder 23b of the outer raceway surface 23, the shortest distance d1 is preferably set to 1mm or less (1 mm. Gtoreq.d1).

Further, by setting the shortest distance d1 between the outer peripheral surface 81a of the annular portion 81 and the inner peripheral surface 28 of the outer ring 2 to 0.2mm or more and 2mm or less, a clearance can be ensured between the balls 7 and the cage 8, and the balls 7 can smoothly rotate, and an increase in torque due to the shearing resistance of the grease applied between the balls 7 and the cage 8 can be suppressed.

As described above, in the wheel bearing apparatus 1, the distance h1 and the radius r are set so as to satisfy the relationship of h1 being equal to or greater than 0.7×r, and the shortest distance d1 between the outer peripheral surface 81a of the annular portion 81 and the inner peripheral surface 28 of the outer ring 2 is set so as to be equal to or greater than 0.2mm and equal to or less than 2mm, whereby the life of the wheel bearing apparatus 1 can be improved while suppressing interference between the outer ring 2 and the retainer 8 and increase in torque due to grease.

As shown in fig. 5, the outer raceway surface 24 on the outer disc side of the outer ring 2 has a bottom 24a and a shoulder 24b. The bottom 24a is a portion located on the outermost diameter side of the outer raceway surface 24. The shoulder 24b is a boundary portion between the outer raceway surface 24 and the inner peripheral surface 28 of the outer ring 2, and is located at an inner disk side end portion of the outer raceway surface 24. The shoulder 24b is located on the innermost diameter side of the outer raceway surface 24.

The holder 8 in the outer-disc-side bead row 6 has: a circular ring portion 81 formed in a ring shape; a plurality of column portions 82 extending from the annular portion 81 toward the outer disk side in the axial direction and arranged at regular intervals along the circumferential direction; and a groove 83 formed by the annular portion 81 and the adjacent pillar portion 82 and holding the ball 7.

The relationship between the outer raceway surface 24 and the inner peripheral surface 28 of the outer ring 2 and the balls 7 and the cage 8 in the outer disc side ball row 6 is the same as the relationship between the outer raceway surface 23 and the inner peripheral surface 28 of the outer ring 2 and the balls 7 and the cage 8 in the inner disc side ball row 5.

Specifically, the distance h2 between the bottom 24a and the shoulder 24b of the radially outer raceway surface 24 is set to be 0.7 times or more the radius r of the ball 7. That is, the distance h2 and the radius r are set so as to satisfy the relationship that h2 is equal to or greater than 0.7×r. The distance h2 is an example of the distance h.

The contact angle α2 of the balls 7 in the outer ball row 6 with respect to the outer raceway surface 24 is set to be greater than 35 ° and equal to or less than 45 ° (35 ° < α1+.ltoreq.45°). The contact angle α2 is an inclination angle of a straight line connecting the center P2 of the ball 7 in the outer-disc-side ball row 6 and the contact point 24c with respect to the radial direction. The contact angle α2 is an example of the contact angle α.

The annular portion 81 of the retainer 8 in the outer bead row 6 has an outer peripheral surface 81a. The shortest distance d2 between the outer peripheral surface 81a of the annular portion 81 in the outer-disc-side bead row 6 and the inner peripheral surface 28 of the outer ring 2 facing the annular portion 81 in the outer-disc-side bead row 6 is set to 0.2mm or more (d 2. Gtoreq.0.2 mm). The shortest distance d2 is an example of the shortest distance d.

The shortest distance d2 is set so as to be 2mm or less (2 mm. Gtoreq.d2). This can prevent the shoulder 24b of the outer raceway surface 24 from climbing up when the ball 7 receives a load. In order to further suppress the ball 7 from climbing up the shoulder 24b of the outer raceway surface 24, the shortest distance d2 is preferably set to 1mm or less (1 mm. Gtoreq.d2).

In this way, by setting the distance h2 and the radius r so as to satisfy the relationship that h2 is equal to or greater than 0.7×r and setting the shortest distance d2 so as to be equal to or greater than 0.2mm and equal to or less than 2mm, it is possible to improve the life of the wheel bearing apparatus 1 while suppressing interference between the outer ring 2 and the retainer 8 and increase in torque due to grease.

In addition, by setting the contact angle α2 to a large angle satisfying 35 ° < α2+.ltoreq.45°, even when the wheel bearing apparatus 1 is miniaturized in the axial direction, the reduction in rigidity of the wheel bearing apparatus 1 can be suppressed.

In the wheel bearing apparatus 1, at least one of the distance h1 and the shortest distance d1 and the distance h2 and the shortest distance d2 may be configured to satisfy a relationship in which h is equal to or greater than 0.7×r (h=h1, h 2) and a relationship in which 2mm is equal to or greater than d is equal to or greater than 0.2mm (d=d1, d 2).

In the wheel bearing apparatus 1, at least one of the contact angles α1 and α2 may be configured to satisfy the relationship of 35 ° < α+.ltoreq.45 ° (α=α1, α2).

In the present embodiment, the wheel bearing apparatus 1 of the third generation structure in which the inner raceway surface 33 of the outer disc-side bead row 6 is directly formed on the outer periphery of the hub wheel 3 has been described, but the wheel bearing apparatus is not limited to this, and may be of a second generation structure in which a pair of inner rings are press-fitted and fixed to the hub wheel, or of a first generation structure in which an outer ring serving as an outer member and a pair of inner rings serving as an inner member are not provided.

The embodiments of the present invention have been described above, but the present invention is not limited to the embodiments described above, but is merely illustrative, and the present invention can be implemented in various forms within a scope not departing from the gist of the present invention, and it is needless to say that the scope of the present invention is shown by the scope of the claims and includes the meaning equivalent to the meaning described in the claims and all modifications within the scope.

Claims (4)

1. A bearing device for a wheel, comprising:

an outer member having a double-row outer raceway surface on an inner periphery thereof;

an inner member having a double-row inner raceway surface opposed to the double-row outer raceway surface;

a double row rolling element housed between both raceway surfaces of the outer member and the inner member so as to be freely rolling; and

a cage which holds the rolling elements,

the retainer has: a circular ring portion formed in a ring shape; a plurality of column portions extending from the annular portion in the axial direction and arranged at regular intervals in the circumferential direction; and a groove formed by the annular portion and the adjacent column portion and holding the rolling element,

it is characterized in that the method comprises the steps of,

at least one of the outer raceway surface on one side in the axial direction and the outer raceway surface on the other side in the axial direction of the double-row outer raceway surfaces,

the distance h between the bottom of the outer track surface and the radial direction of the shoulder and the radius r of the rolling body satisfy the relation that h is more than or equal to 0.7 xr,

and, in addition, the processing unit,

the shortest distance d between the annular portion of the retainer and the inner peripheral surface of the outer member facing the annular portion is 0.2mm or more and 2mm or less.

2. The wheel bearing apparatus according to claim 1, wherein,

the shortest distance d is 1mm or less.

3. The wheel bearing apparatus according to claim 1, wherein,

the pitch circle diameter b of the double-row rolling bodies and the interval a between the rolling bodies of the rolling bodies on one axial side and the rolling bodies on the other axial side in the double-row rolling bodies meet the relation that b/a is more than or equal to 2.0.

4. A bearing device for a wheel according to any one of claims 1 to 3,

at least one of the outer raceway surface on one side in the axial direction and the outer raceway surface on the other side in the axial direction of the double-row outer raceway surfaces,

the contact angle alpha of the rolling element relative to the outer raceway surface is greater than 35 DEG and 45 DEG or less.