TWI620880B - Angular ball bearing - Google Patents

Abstract

The retainer (30) of the present invention includes a substantially annular ring portion (31), a plurality of column portions (32) protruding from the front side or the back side of the ring portion (31) in the axial direction at specific intervals, and Crown-shaped retainers of a plurality of recessed portions (33) formed between adjacent pillar portions (32). The spherical center position of the cavity portion (33) is offset from the radial direction intermediate position (M) of the outermost diameter portion (m1) and the innermost diameter portion (m2) of the ring portion (31) to the radial direction side. The side surface of the pillar portion (32) forming the cavity portion (33) viewed from the circumferential direction is obtained by cutting a part of the circular arc (33a) on one side of the radial direction and the other side of the radial direction of the connecting ring portion (31). In addition, the first linear shape portion (33b) is formed by cutting an end portion in the radial direction side of the circular arc (33a) and extending in the axial direction.

Description

Angular ball bearing

The present invention relates to an angular ball bearing.

NC (Numerical Control: numerical control) lathes, milling machines, automatic tool-changing digital control machine tools (machining center), composite processing machines, five-axis processing machines and other working machinery, or the spindle table or the machine tool to install the workpiece In the process, a ball screw that converts rotary motion into linear motion is used. An oblique ball bearing is adopted as a bearing that rotatably supports the ball screw shaft end (for example, refer to Patent Document 1). These bearings are based on the size of the spindle table of the working machine or the machine tool on which the workpiece is installed, and the bearing inner diameter is about Φ10mm ~ Φ100mm.

The cutting load generated during machining, or the inertial load when the spindle table and the machine tool are moved with high acceleration, are loaded to the angular ball bearing as an axial load through a ball screw. Recent work machines tend to increase the inertia load caused by cutting load or fast-forwarding based on the purpose of high-efficiency machining, and tend to increase the axial load on the angular ball bearing.

Therefore, in order to increase the rolling fatigue life of an oblique ball bearing used to support such a ball screw, it is necessary to increase the load capacity in the axial direction and to achieve high rigidity to maintain machining accuracy.

[Prior technical literature] [Patent Literature]

[Patent Document 1] Japanese Patent Laid-Open No. 2000-104742

In order to make these two stand side by side, although the bearing size needs to be increased to increase the number of combined lines, the bearing space of the ball screw shaft increases if the bearing size is increased. In addition, if the number of combined lines is excessive, When the ground is increased, the ball screw unit has a wider width. As a result, there is a limit to the increase in the size of the bearing or the increase in the number of rows due to an increase in the estimated area required for the work machine or an increase in the size in the height direction.

The present invention has been made in view of the above-mentioned circumstances, and an object thereof is to provide an oblique ball bearing that can increase both the load capacity in the axial direction and high rigidity in a limited space.

The said objective of this invention is achieved by the following structure.

(1)

An angular ball bearing is characterized by comprising: an outer ring having a track surface on an inner peripheral surface; an inner ring having a track surface on an outer peripheral surface; a plurality of balls arranged on the outer ring and the inner ring Between the track surfaces; and a retainer, which is a ball guide method, and which keeps the balls rolling freely; and in the outer peripheral surface of the inner ring, an inner ring countersink is recessed on the back side and convex on the front side Inner ring groove shoulder; in the inner peripheral surface of the outer ring, an outer ring countersink is recessed on the front side, and an outer ring groove shoulder is protruded on the back side; and the contact angle α of the balls is 45 ° ≦ α ≦ 65 °; If the radial height of the shoulder of the inner ring groove is divided by the ball diameter Is Ai, then 0.35 ≦ Ai ≦ 0.50; if the value obtained by dividing the radial height of the shoulder of the outer ring groove by the ball diameter is set to Ae, 0.35 ≦ Ae ≦ 0.50; the above-mentioned holder is a crown-type holder, which A ring portion having a substantially circular ring shape, a plurality of pillar portions protruding from the front side or the back side of the ring portion at specific intervals in the axial direction, and a plurality of recessed portions formed between the adjacent pillar portions; The spherical center position of the cavity portion is offset from the radial direction intermediate position between the outermost diameter portion and the innermost diameter portion of the ring portion to the radial direction side; the circumferential direction of the column portion forming the cavity portion The side surface to be observed is obtained by cutting out a part of an arc connecting one side of the radial direction of the ring portion and the other side of the radial direction, and includes: a first linear shape portion that cuts the radial direction of the arc The side end portion is formed so as to extend in the axial direction.

(2)

The oblique ball bearing of the technical solution (1), wherein the side surface of the column portion forming the recessed portion viewed from the circumferential direction includes a second linear shape portion that connects the arcs to the first linear shape. The portion and a portion of one side surface in the radial direction of the ring portion are cut out and formed.

(3)

An angular ball bearing is characterized by comprising: an outer ring having a track surface on an inner peripheral surface; an inner ring having a track surface on an outer peripheral surface; a plurality of balls arranged on the outer ring and the inner ring; Between the track surfaces; and a retainer, which is a ball-guided method, and which keeps the balls free to roll; and in the outer peripheral surface of the inner ring, an inner ring countersunk hole is recessed on the back side and is convexly set on the front side Ring groove shoulder On the inner peripheral surface of the outer ring, a countersink hole of the outer ring is recessed on the front side, and a shoulder of the outer ring groove is protruded on the back side; and the contact angle α of the balls is 45 ° ≦ α ≦ 65 °; The value obtained by dividing the height of the shoulder in the radial direction by the above-mentioned ball diameter is set to Ai, then 0.35 ≦ Ai ≦ 0.50; if the value obtained by dividing the height in the radial direction of the shoulder of the outer ring by the ball diameter is set to Ae, then 0.35 ≦ Ae ≦ 0.50; the above-mentioned retainer is a crown-type retainer, which has a generally annular ring portion, a plurality of column portions protruding from the front side or the back side of the ring portion at specific intervals in the axial direction, and formed A plurality of recessed portions between the adjacent pillar portions; the spherical center position of the recessed portions is offset from the radial position between the outermost diameter portion and the innermost diameter portion of the ring portion in the radial direction One side; the side surface viewed from the circumferential direction of the column portion forming the cavity portion is a portion obtained by cutting out a part of an arc connecting one side of the ring portion in the radial direction and the other side in the radial direction, and includes: a straight line The shape part connects the end part on one side in the radial direction of the arc, At least a portion of the cut-out portion of a side surface of the above-described radial direction of the ring portion is formed.

(4)

For example, the angular ball bearing of any one of the technical solutions (1) to (3), wherein the distance L between the adjacent balls and the circumference of the ball pitch circle π multiplied by the ball pitch circle diameter dm has a relationship of πdm. Meets 2.5 × 10 ^-3 ≦ L / πdm ≦ 13 × 10 ^-3 .

According to the angular ball bearing of the present invention, since the contact angle α of the balls satisfies 45 ° ≦ α ≦ 65 °, by increasing the contact angle, the load capacity of the bearing in the axial direction can be increased, and a larger preload can be achieved. Load use. As a result, the rigidity of the bearing and the ball screw system can be improved.

In addition, the value obtained by dividing the height in the radial direction of the shoulder of the inner ring groove by the ball diameter is set to Ai When the value is 0.35 ≦ Ai ≦ 0.50, and the value obtained by dividing the radial height of the shoulder of the outer ring groove by the ball diameter is set to Ae, 0.35 ≦ Ae ≦ 0.50, which can prevent the bearing's axial load from being insufficient, and Grinding of the inner and outer ring groove shoulders becomes easy.

In addition, the side surface viewed from the circumferential direction of the pillar portion forming the cavity portion is obtained by cutting out a part of a circular arc on one side in the radial direction and the other side in the radial direction of the connecting ring portion, and includes: a first linear shape portion It is formed by cutting the end of one side of the radial direction of the arc and extending in the axial direction. Therefore, the contact between the retainer and the ball is a linear contact. When the retainer moves in the radial direction, the ball flexes into the recessed portion of the retainer, thereby suppressing the relative movement of the retainer in the axial direction. Thereby, a change in the radial movement amount of the cage can be suppressed, and an increase in vibration during the rotation of the bearing can be suppressed. In addition, by restricting the holder with a line-contacting portion, movement in the axial direction can be suppressed to a minimum. As a result, it is possible to eliminate problems such as retainer sounds or premature breakage of the retainer. In addition, since the pitch circle position of the pocket portion of the cage and the pitch circle position of the ball are prevented from being shifted with respect to the axial direction, it is easy to accurately measure the outer circle diameter or the inner circle diameter when the cage is manufactured.

1‧‧‧Angle Ball Bearing

3‧‧‧ball

10‧‧‧ Outer ring

11‧‧‧ orbital surface

12‧‧‧ Outer ring groove shoulder

13‧‧‧Outer ring countersunk

14‧‧‧Chamfer of outer ring

20‧‧‧ Inner Ring

21‧‧‧ orbital surface

22‧‧‧Inner ring groove shoulder

23‧‧‧Inner ring countersunk

24‧‧‧Inner ring chamfer

30‧‧‧ retainer

31‧‧‧Ring

31a‧‧‧Inner side of diameter of ring

31b‧‧‧outer side of the ring

32‧‧‧ pillar

33‧‧‧Concave

33a‧‧‧arc

33b‧‧‧The first linear shape part

33c‧‧‧The second linear shape part

33d‧‧‧Inner end in the radial direction of the cavity

33e‧‧‧Circular diameter direction inside end

33f‧‧‧outer end

33g‧‧‧The third linear shape part

34‧‧‧Gap

35‧‧‧ Corner

100‧‧‧Deep Groove Bearing

110‧‧‧outer ring

120‧‧‧ Inner Ring

130‧‧‧ retainer

A‧‧‧arrow

A‧‧‧center

A-A'‧‧‧ section

B‧‧‧ Center

C‧‧‧ intersection

D‧‧‧ intersection

D1‧‧‧ Outside diameter

D2‧‧‧ Outside diameter

D3‧‧‧Inner diameter

D4‧‧‧Inner diameter

Dw‧‧‧ball diameter

dm‧‧‧ball pitch circle diameter

E‧‧‧ Midpoint

F‧‧‧ Radial load

He‧‧‧ Radial height of outer shoulder

Hi‧‧‧Inner ring groove shoulder height in radial direction

L‧‧‧ Distance between balls

M‧‧‧ center position in radial direction

m1‧‧‧most outer diameter part

m2‧‧‧ innermost diameter

O‧‧‧ Festival Circle Center

Oi‧‧‧Ball Center

P‧‧‧Circle Center

r‧‧‧ radius

r1‧‧‧ radius

T‧‧‧Ball center distance

VI-VI‧‧‧line

Line VII-VII‧‧‧

X‧‧‧ starting point

XIII-XIII‧‧‧line

XIV-XIV‧‧‧line

XIX-XIX‧‧‧line

XV‧‧‧ direction

XXIII‧‧‧ direction

α‧‧‧ contact angle

θ‧‧‧ angle

△ A‧‧‧Axis movement

△ R‧‧‧ Radial movement

△ Re‧‧‧Radial clearance

△ Ri‧‧‧Radial clearance

△ S1‧‧‧Axis distance

△ S2‧‧‧Axis distance

FIG. 1 is a sectional view of an angular ball bearing according to an embodiment of the present invention.

FIG. 2 is a sectional view of the angular ball bearing of FIG. 1 combined side by side.

Figure 3 is a side view of the holder.

Fig. 4 is a view of the retainer viewed from one side in the axial direction.

Fig. 5 is a view of the retainer viewed from the other side in the axial direction.

FIG. 6 is a sectional view taken along the line VI-VI in FIG. 4.

FIG. 7 is a sectional view taken along the line VII-VII in FIG. 4.

Figure 8 is a sectional view of a previous deep groove ball bearing.

Fig. 9 is a view of a retainer when a load is viewed in a radial direction from a side in the axial direction.

Fig. 10 is a cross-sectional view of an angular ball bearing when a radial load is applied to a cage load.

FIG. 11 is a diagram for explaining an arrangement state of a plurality of balls.

Figure 12 is a sectional view of a conventional angular ball bearing.

FIG. 13 is a sectional view taken along the line XIII-XIII of the retainer and the ball of FIG. 12.

FIG. 14 is a cross-sectional view of the XIV-XIV when the pocket portion of the holder is moved in the axial direction by a one-point chain line in the holder and the ball of FIG. 12.

Fig. 15 is a view of the holder viewed from the XV direction in Fig. 12.

Fig. 16 is a diagram showing a holder of the present invention.

Fig. 17 is a sectional view of a beveled ball bearing according to a modification.

Fig. 18 is a view of a retainer according to a modification as viewed from one side in the axial direction.

FIG. 19 is a sectional view taken along the line XIX-XIX in FIG. 18.

Fig. 20 is a sectional view of an angular ball bearing according to an embodiment of the present invention.

Fig. 21 is a sectional view of the angular ball bearing of Fig. 20 combined in parallel.

Fig. 22 is a sectional view of an angular ball bearing when a radial load is applied to a retainer load.

Fig. 23 (a) is a side view of the holder, and (b) is a view taken along the line XXIII of the AA 'section of (a).

Fig. 24 is a sectional view of a beveled ball bearing according to a modification.

Hereinafter, the angular ball bearing according to each embodiment of the present invention will be described using drawings.

(First Embodiment)

As shown in FIG. 1, the angular ball bearing 1 of this embodiment includes an outer ring 10 having a track surface 11 on an inner peripheral surface, an inner ring 20 having a track surface 21 on an outer peripheral surface, and a plurality of balls 3 which It is arranged between the orbital surfaces 11 and 21 of the outer ring 10 and the inner ring 20; and the retainer 30, which is a ball guide method, and the ball 3 is kept to roll freely.

The inner peripheral surface of the outer ring 10 includes: an outer ring groove shoulder portion 12 which is convexly arranged on the back side (load side, left side in FIG. 1) than the track surface 11; and an outer ring countersunk hole 13 which is more than a rail The surface 11 is recessed further toward the front side (anti-load side, right side in FIG. 1).

The outer peripheral surface of the inner ring 20 has: an inner ring groove shoulder portion 22 which is convexly arranged on the front side (load side, right side in FIG. 1) than the track surface 21; and an inner ring countersink 23 which is more than the track surface 21 is recessed toward the back side (opposite load side, left side in FIG. 1).

Here, if the outer diameter of the inner ring countersink 23 is D1 and the outer diameter of the inner ring groove shoulder 22 is D2, then D1 <D2, and if the inner diameter of the outer ring countersink 13 is set Let D3, and if the inner diameter of the outer ring groove shoulder 12 is D4, then D3> D4. In this way, since the outer diameter D2 of the inner ring groove shoulder portion 22 is increased and the inner diameter D4 of the outer ring groove shoulder portion 12 is reduced, the contact angle α of the ball 3 can be set to be large. More specifically, by setting the outer diameter D2 and the inner diameter D4 as described above, the contact angle α can be set to about 45 ° ≦ α ≦ 65 °, and even if the variation of the contact angle α at the time of bearing production is considered, It is set to about 50 ° ≦ α ≦ 60 °, and the contact angle α can be increased.

In addition, if the value obtained by dividing the height Hi in the radial direction of the shoulder 22 of the inner ring groove by the diameter Dw of the ball 3 is set to Ai (Ai = Hi / Dw), then 0.35 ≦ Ai ≦ 0.50 is set, and if The value obtained by dividing the height He of the shoulder 12 of the outer ring in the radial direction by the diameter Dw of the ball 3 is set to Ae (Ae = He / Dw), and it is set to satisfy 0.35 ≦ Ae ≦ 0.50.

In the case of 0.35> Ai or 0.35> Ae, the contact angle α is less than 45 because the radial heights Hi and He of the inner ring groove shoulder 22 or the outer ring groove shoulder 12 are too small relative to the diameter Dw of the ball 3. °, the load capacity of the bearing in the axial direction is insufficient. In the case of 0.50 <Ai or 0.50 <Ae, since the track surfaces 11 and 21 of the outer ring 10 and the inner ring 20 are formed to exceed the pitch circle diameter dm of the ball 3, the outer ring groove shoulder 12 and the inner ring groove The grinding of the shoulder 22 is difficult and undesirable.

A tapered outer ring chamfer 14 is formed on the back side end portion of the outer ring groove shoulder portion 12 toward the outer side in the radial direction as it faces the back side, and the front side end portion of the inner ring groove shoulder portion 22 is provided. A tapered inner ring chamfer 24 is provided toward the inside in the radial direction as it faces the front side. The radial widths of the outer ring chamfers 14 and the inner ring chamfers 24 are larger than one and a half of the radial heights He and Hi of the outer ring groove shoulders 12 and the inner ring groove shoulders 22, and are set to larger values.

This type of angular ball bearing 1 is shown in Fig. 2 and can be used in combination. Since the real The oblique angle ball bearing 1 in the configuration is provided with the outer ring groove shoulder portion 12 and the inner ring groove shoulder portion 22 near the pitch circle diameter dm of the ball 3. Therefore, it is assumed that the outer ring chamfer 14 and the inner ring chamfer are not provided. 24, the inner ring 20 of one oblique ball bearing 1 and the outer ring 10 of the other oblique ball bearing 1 interfere with each other, resulting in a poor condition in the rotation of the bearing. In the case of oil lubrication, it is assumed that the outer ring chamfer 14 and the inner ring chamfer 24 are not provided, and the oil does not pass between the angled ball bearings 1 and the oil flow becomes poor, the lubrication is poor, or the oil is not provided. A large amount remains in the bearing and causes a temperature rise. In this way, by providing the outer ring chamfer 14 and the inner ring chamfer 24, it is possible to prevent the inner ring 20 and the outer ring 10 from interfering with each other, and improve the oil flowability. In addition, the outer ring chamfer 14 and the inner ring chamfer 24 are not necessarily both provided, as long as at least one is provided.

Next, the configuration of the holder 30 will be described in detail with reference to FIGS. 3 to 7. The retainer 30 is a ball-guided plastic retainer including a synthetic resin, and the base resin of the retainer 30 is a polyamide resin. In addition, the type of the polyamide resin is not limited, and in addition to the polyamide, other synthetic resins such as polyacetal resin, polyetheretherketone, and polyimide may also be used. Further, as the reinforcing material, glass fibers, carbon fibers, aromatic polyamide fibers, and the like are added to the base resin. The retainer 30 is manufactured by injection molding or cutting.

The retainer 30 is a crown-shaped retainer, and has a substantially annular ring portion 31 (refer to FIG. 1) arranged coaxially with the inner ring 20 and the outer ring 10. A plurality of pillar portions 32 protruding in the axial direction, and a plurality of recessed portions 33 formed between adjacent pillar portions 32.

Here, in the angular ball bearing 1 of this embodiment, in order to achieve a high load capacity in the axial direction, the radial heights He and Hi of the outer ring groove shoulder portion 12 and the inner ring groove shoulder portion 22 are increased. Reduced bearing internal space. Therefore, when the retainer 30 disposed in the bearing internal space is a crown-type retainer (single-side ring structure), the ring portion 31 is arranged between the outer ring countersunk hole 13 and the inner ring groove shoulder portion 22, A structure in which a pillar portion 32 is arranged between the track surfaces 11 and 21 of the outer ring 10 and the inner ring 20 and is connected to the ring portion 31 at the radially outer end of the pillar portion 32.

That is, as shown in FIG. 7, it is assumed that the spherical center position of the recessed portion 33 is shifted to the inner side in the radial direction (radial direction) from the radial direction intermediate position M between the outermost diameter portion m1 and the innermost diameter portion m2 of the ring portion 31. Side). Here, the spherical center position of the pocket portion 33 is a position that coincides with the center Oi of the ball 3. The outermost diameter portion m1 of the ring portion 31 is an outer surface 31b in the radial direction, and the innermost diameter portion m2 is an inner surface 31a in the radial direction. In the example shown in the figure, the spherical center position of the recessed portion 33 is shifted to the inner side in the radial direction from the innermost diameter portion m2 of the ring portion 31.

As shown in FIG. 7, the side surface of the pillar portion 32 forming the cavity portion 33 as viewed from the circumferential direction is the inner side surface (one side in the radial direction) 31 a of the radial direction and the outer side surface (the other side in the radial direction) connecting the ring portion 31. A part of the arc 33a of the side surface 31b is cut out. The center of the arc 33a is represented by P, and the radius is represented by r.

More specifically, the side surface of the pillar portion 32 viewed from the circumferential direction includes a first linear shape portion 33b which is a radial-direction inner end portion (radial-direction-side end portion) cut away from the arc 33a and extends in the axial direction. Way of forming. The first linear shape portion 33b is disposed closer to the back side than the center P of the arc 33a. The first linear shape portion 33b overlaps the center Oi of the ball 3 (the spherical surface center of the cavity portion 33) in the axial direction.

In addition, the side surface of the pillar portion 32 viewed from the circumferential direction includes a second linear shape portion 33c, which is an end portion on the front side that connects the arc 33a to the first linear shape portion 33b, and the radial direction of the ring portion 31. A part of the end portion on the back side of the inner surface 31a is cut out and formed. Therefore, the second linear shape portion 33c has a linear shape that faces outward in the radial direction as it goes toward the front side (the ring portion 31 side).

In addition, the side surface of the pillar portion 32 viewed from the circumferential direction includes a third linear shape portion 33g which is formed by cutting out the radial end portion (the other end portion in the radial direction) of the radial direction of the arc 33a and extending in the axial direction. form. The third linear shape portion 33g is formed on the same plane as the radial outer surface 31b of the ring portion 31, and is connected to the radial outer surface 31b without a step.

In this way, the side surface of the pillar portion 32 viewed from the circumferential direction has a shape in which the third linear shape portion 33g, the arc 33a, the first linear shape portion 33b, and the second linear shape portion 33c are connected.

As shown in FIG. 6, both sides in the circumferential direction of the pillar portion 32 forming the cavity portion 33 and the side surfaces on the back side (pillar portion 32 side) of the ring portion 31 are formed similar to the ball 3 when viewed from the radial direction. Spherical shape. Here, the top end of the pillar portion 32 is provided with a notch portion 34 at the middle in the circumferential direction and is branched. Accordingly, when the retainer 30 is manufactured by injection molding, the corner portion 35 on the side of the recessed portion 33 of the pillar portion 32 caused by forcibly pulling out the mold member forming the recessed portion 33 can be prevented.

The proportion of the reinforcing material of the synthetic resin added to the material of the holder 30 is preferably 5 to 30% by weight. Assuming that the proportion of the reinforcing material in the synthetic resin component exceeds 30% by weight, the flexibility of the retainer 30 is reduced. Therefore, when the retainer 30 is formed, the ball 3 is forcibly pulled out of the mold from the cavity 33 or the bearing is assembled. When the recessed portion 33 is pushed in, the corner portion 35 of the pillar portion 32 is damaged. In addition, the thermal expansion of the retainer 30 depends on the linear expansion coefficient of the base material, that is, the resin material. Therefore, if the proportion of the reinforcing material is less than 5% by weight, the thermal expansion of the retainer 30 during bearing rotation relative to the pitch of the ball 3 The expansion of the diameter dm becomes larger, causing the ball 3 to collide with the recessed portion 33 of the retainer 30, causing an unfavorable condition such as burning. Therefore, by setting the proportion of the reinforcing material in the synthetic resin component within the range of 5 to 30% by weight, it is possible to prevent the above-mentioned bad situation.

In addition, as the synthetic resin material of the holder 30, resins such as polyamine, polyetheretherketone, polyphenylene sulfide, polyimide, and the like, and glass fiber, carbon fiber, and aromatic polyamidine are used as the reinforcing material. Fiber, etc.

Here, as shown in FIG. 8, the deep groove ball bearing 100 having the previous crown-shaped cage 100 is a cage 130 and the inner ring 120 or the outer ring 110 does not overlap in the radial direction. Therefore, even if the retainer 130 exceeds the design value due to the inertia at the start or stop of the rotation of the deep groove ball bearing 100, the retainer 130 and the inner ring 120 or the inner ring 120 or the outer ring 110 move relative to the axial direction. The outer rings 110 also do not interfere with each other.

However, as in the angular ball bearing 1 of this embodiment, when the retainer 30 overlaps with the inner ring 20 or the outer ring 10 in the radial direction, the retainer 30 exceeds the design value, and the inner ring 20 Or when the outer ring 10 moves relative to the axial direction, there is a possibility that the retainer 30 and the inner ring 20 or the outer ring 10 interfere with each other. It is assumed that the axial direction distance ΔS1 between the retainer 30 and the inner ring 20 when the side surface of the pillar portion 32 viewed from the circumferential direction is not in the shape of the second linear shape portion 33c (see FIG. 7) (see FIG. 1) ) Becomes narrower, and the possibility that the retainer 30 and the inner ring 20 interfere with each other becomes high. If the retainer 30 and the inner ring 20 interfere with each other, the torque changes when the retainer 30 and the inner ring 20 interfere, and cannot be positioned correctly as a ball screw system, and the retainer 30 is worn due to friction during the interference, resulting in the retainer 30 Broken. In addition, the abrasion powder generated when the retainer 30 is worn becomes a foreign substance, which causes the lubrication state of the bearing to deteriorate, and as a result, the life of the bearing is shortened.

Therefore, like the angular ball bearing 1 of this embodiment, the second linear shape portion 33c is provided on the side surface of the column portion 32 when viewed from the circumferential direction, and the axial distance Δ between the retainer 30 and the inner ring 20 can be further increased. S1, and the possibility that the retainer 30 and the inner ring 20 interfere with each other can be reduced.

In addition, like the angular ball bearing 1 of this embodiment, in order to maintain a large contact angle α, the radial heights He and Hi of the outer ring groove shoulder portion 12 and the inner ring groove shoulder portion 22 are increased to those of the ball 3, respectively. When the pitch circle diameter is near dm, the radial direction space between the outer ring 10 and the inner ring 20 becomes narrow, and the radial thickness of the ring portion 31 of the retainer 30 located in the space between the outer ring 10 and the inner ring 20 cannot be achieved. Thicker than standard bearings. In particular, in the case of a crown-shaped retainer, since the ring portion 31 exists only on one side in the axial direction of the retainer 30, the wall thickness may be insufficient to cause the strength of the ring portion 31 to decrease.

In addition, the material of the holder 30 is synthetic resin such as polyamide resin, polyacetal resin, polyetheretherketone, and polyimide, and the content of reinforcing fibers in the base resin is also set to 30% by weight or less. Therefore, the strength of the ring portion 31 of the retainer 30 tends to be low, and when the impact load or vibration load in the radial direction increases, the retainer 30 bends in the radial direction. An example of a shape in which the radial load F is applied to the retainer 30 and the radial load F is shown by a dotted line in FIG. 9 and a one-dot chain line in FIG. 10 is shown. Because the retainer 30 bends in the radial direction This causes the radial position of the retainer 30 to be closer to the inner ring 20 side or the outer ring 10 side. Therefore, the axial distance ΔS1 between the retainer 30 and the inner ring 20 becomes narrow, and the possibility that the retainer 30 and the inner ring 20 interfere with each other becomes high. When it is assumed that the side surface of the pillar portion 32 viewed from the circumferential direction is not the shape of the second linear shape portion 33c, the axial direction distance ΔS1 between the retainer 30 and the inner ring 20 becomes narrow, and the retainer 30 and The possibility that the inner rings 20 interfere with each other becomes high. Therefore, like the angular ball bearing 1 of this embodiment, the second linear shape portion 33c is provided on the side surface of the column portion 32 when viewed from the circumferential direction, and the axial distance Δ between the retainer 30 and the inner ring 20 can be further increased. S1, and the possibility that the retainer 30 and the inner ring 20 interfere with each other can be reduced.

In addition, since the wall thickness in the radial direction of the ring portion 31 of the retainer 30 located in the space between the outer ring 10 and the inner ring 20 cannot be thickened relative to a standard bearing, the bending rigidity of the ring portion 31 may be insufficient. In this case, as shown by arrow A in FIG. 6, due to the centrifugal force acting on the column portion 32 of the retainer 30 when the bearing is used, the front end of the column portion 32 expands outward in the radial direction, and the corner portion 35 is easy to The direction of the week has expanded. Therefore, the movement amount ΔA in the axial direction of the holder 30 becomes large. When the movement amount ΔA in the axial direction of the retainer 30 becomes large, the axial distance ΔS1 between the retainer 30 and the inner ring 20 becomes narrower, and the possibility that the retainer 30 and the inner ring 20 interfere with each other becomes higher. . When it is assumed that the side surface of the pillar portion 32 viewed from the circumferential direction is not the shape of the second linear shape portion 33c, the axial direction distance ΔS1 between the retainer 30 and the inner ring 20 becomes narrow, and the retainer 30 and The possibility that the inner rings 20 interfere with each other becomes high. Therefore, as in the angular ball bearing 1 of this embodiment, the second linear shape portion 33c is formed on the side surface of the column portion 32 when viewed from the circumferential direction, so that the axial distance Δ between the retainer 30 and the inner ring 20 can be further increased. S1, and the possibility that the retainer 30 and the inner ring 20 interfere with each other can be reduced.

In addition, the angular ball bearing 1 of this embodiment is set so as to increase the number of balls 3 (the number of balls Z) in order to increase the axial load capacity. More specifically, it demonstrates using FIG. 11. In FIG. 11, two balls 3 arranged on a pitch circle with a diameter of dm are shown. The diameter of the balls 3 is set to Dw, the centers of the balls 3 are set to A and B, and the line segments AB and the balls 3 are shown. The intersection of the surface is set to C, D, the midpoint of the line segment AB is set to E, and the node The center of the circle is set to O. In addition, the distance between the centers A and B of the adjacent balls 3 (the distance between the line segments AB), that is, the distance between the center of the balls is set to T, and the distance between the adjacent balls 3 (the distance of the line CD), that is, the distance between the balls is set. Is L, and the angle formed by the line segment EO and the line segment BO (the angle formed by the line segment EO and the line segment AO) is set to θ. In this way, the distance between the line segment AO and the line segment BO is (dm / 2), the distance T between the centers of the balls is (dm × sinθ), the distance L between the balls is (T-Dw), and the angle θ is (180 ° / Z).

The distance L between the balls and the circumference πdm of the ball pitch obtained by multiplying the π by the ball pitch circle diameter dm is designed so that the relationship of 2.5 × 10 ^-3 ≦ L / πdm ≦ 13 × 10 ^-3 is established. . Assuming that L / πdm is less than 2.5 × 10 ^-3 , the wall thickness in the circumferential direction of the pillar portion 32 of the retainer 30 becomes too thin, resulting in perforation during forming or cutting. In particular, when a large amount of reinforcing material is contained, the fluidity of the synthetic resin, that is, the material of the holder 30 during molding is deteriorated, and perforation is easy. In addition, if L / πdm is larger than 13 × 10 ^-3 , the number of balls Z becomes small, and the axial load capacity and rigidity of the bearing become low.

In this way, the angular ball bearing 1 is designed to satisfy 2.5 × 10 ^-3 ≦ L / πdm ≦ 13 × 10 ^-3 , that is, designed so that the number of balls Z is large, and the size of the column portion 32 of the retainer 30 The circumferential wall thickness cannot be thickened compared to standard bearings. Therefore, as the wall thickness in the circumferential direction of the pillar portion 32 becomes thinner, the wall thickness in the corner portion 35 becomes thinner. Therefore, as shown by arrow A in FIG. 6, when the ball 3 collides with the corner portion 35 of the retainer 30, the corner portion 35 tends to expand in the circumferential direction, and as a result, the axial movement amount ΔA of the retainer becomes large. Thereby, the axial direction distance ΔS1 between the retainer 30 and the inner ring 20 becomes narrow, and the possibility that the retainer 30 and the inner ring 20 interfere with each other becomes high. When it is assumed that the side surface of the pillar portion 32 viewed from the circumferential direction is not the shape of the second linear shape portion 33c, the axial direction distance ΔS1 between the retainer 30 and the inner ring 20 becomes narrow, and the retainer 30 and The possibility that the inner rings 20 interfere with each other becomes high. Therefore, like the angular ball bearing 1 of this embodiment, the second linear shape portion 33c is provided on the side surface of the column portion 32 when viewed from the circumferential direction, and the axial distance Δ between the retainer 30 and the inner ring 20 can be further increased. S1, and the possibility that the retainer 30 and the inner ring 20 interfere with each other can be reduced.

As shown in FIG. 12, even when the side surface of the column portion 32 viewed from the circumferential direction is set to a circular shape with an arbitrary radius r1 of the previous type, it is the same as the retainer 30 of this embodiment described above. In the middle, the relative movement amount ΔA in the axial direction of the holder 30 becomes larger. In addition, when the side surface of the pillar portion 32 viewed from the circumferential direction is round, as shown in FIG. 15, the radial direction inner end portion 33 d of the recessed portion 33 that guides the ball 3 is in point contact with the ball 3. In this case, as shown in FIG. 13, the radial distance between the radial inner end portion 33 d of the pocket portion 33 and the ball 3 is the radial movement amount ΔR of the retainer 30.

In this case, since the retainer 30 is in point contact with the ball 3, during the bearing rotation, the retainer 30 is relatively easy to move relative to the axial direction of the inner ring 20 or the outer ring 10, and as a result, the diameter of the cavity portion 33 is also reduced. The position of the direction inner end portion 33d moves in the axial direction. In FIG. 12, the concave portion 33 (the pillar portion 32) that moves in the axial direction is indicated by a one-dot chain line. In this way, the radial distance between the inner end portion 33d in the radial direction of the pocket portion 33 and the ball 3 becomes larger after the movement than before the movement in the axial direction. Therefore, the radial movement amount ΔR of the retainer 30 and Compared with the movement in the axial direction (see FIG. 13), the movement is also larger after the movement (see FIG. 14).

Since this phenomenon occurs each time the retainer 30 moves relative to the inner ring 20 or the outer ring 10 in the axial direction, the ball 3 cannot be guided stably when the side surface of the column portion 32 viewed from the circumferential direction is round. Moreover, the vibration of the holder 30 increases, which causes problems such as a holder sound or the holder 30 being damaged in advance.

Therefore, as in the present embodiment, the first linear shape portion 33b is provided because the side surface of the pillar portion 32 is viewed from the circumferential direction, so as shown in FIG. 16, the first linear portion is the portion that guides the ball 3 of the cavity portion 33. The shape portion 33b is configured to make linear contact with the ball 3 in an arc shape. In this way, by making the contact portion between the retainer 30 and the ball 3 in line contact, when the retainer 30 moves in the radial direction, the ball 3 flexibly engages in the recessed portion 33, and the relative movement of the retainer 30 in the axial direction can be suppressed. . Therefore, a change in the radial movement amount ΔR of the retainer 30 can be prevented, and an increase in vibration during bearing rotation can be suppressed. In addition, the axial movement of the holder 30 is suppressed, and as a result, problems such as the holder sound or the damage of the holder 30 in advance can be suppressed.

When the side surface of the pillar portion 32 viewed from the circumferential direction is rounded (see FIG. 12), in addition to the problems caused during the rotation of the bearing described above, there may be problems. This problem refers to the fact that the pitch circle position of the recessed portion 33 of the retainer 30 and the pitch circle position of the ball 3 are relatively offset from each other in the axial direction, so the radial movement amount ΔR of the retainer 30 varies from the designed range. , And it is difficult to accurately measure the outer diameter of the ball and the inner diameter of the ball when the cage is manufactured.

As one of the measuring methods of the outer diameter of the ball and the inner diameter of the ball in the cage 30, there is a state in which the ring portion 31 of the cage 30 is set down, and the ball is fixed with a lighter measurement load on the inner side in the radial direction. 3 Method of measurement. At this time, the ball 3 in the cavity portion 33 approaches the ring portion 31 side in the cavity portion 33 due to gravity. As a result, the pitch circle position of the pocket portion 33 and the pitch circle position of the ball 3 are relatively shifted in the axial direction. In addition, the radial movement amount ΔR of the retainer 30 is larger than that before the movement in the axial direction (see FIG. 13) after the movement (see FIG. 14). As a result, the radial movement amount ΔR becomes larger and Beyond the scope of design. In this case, it is difficult to accurately measure the outer diameter of the ball and the inner diameter of the ball of the cage 30.

Therefore, in this embodiment, the first linear shape portion 33b is provided on the side surface of the pillar portion 32 as viewed from the circumferential direction. As shown in FIG. 16, the ball 3 is engaged with the first linear shape portion 33b by the measurement load. In this way, the ball 3 does not shift in the axial direction, and it is easy to accurately measure the outer diameter of the ball and the inner diameter of the ball.

In addition, the spherical center position of the cavity portion 33 is not limited to the radial direction intermediate position M of the outermost diameter portion m1 and the innermost diameter portion m2 of the ring portion 31, and the structure is shifted to the inner side in the radial direction, as shown in FIG. 17 ~ 19 shows the structure shifted to the outside in the radial direction. That is, it is also possible to arrange the ring portion 31 between the outer ring groove shoulder portion 12 and the inner ring countersunk hole 23, and arrange the post portion 32 between the track surfaces 11, 21 of the outer ring 10 and the inner ring 20, and place the post portion The structure in which the inner end portion in the radial direction of 32 is connected to the ring portion 31. In the example shown in the figure, the spherical center position of the recessed portion 33 is shifted to the outside in the radial direction from the outermost diameter portion m1 of the ring portion 31. In this case, because the front end of the column 32 is in the periphery A notch portion 34 is provided in the middle of the direction and is bifurcated. Therefore, when the retainer 30 is manufactured by injection molding, it can prevent the cavity portion 33 side of the column portion 32 caused by the forced extraction of the mold part forming the cavity portion 33. The corner 35 is damaged.

Here, the side surface viewed from the circumferential direction of the pillar portion 32 forming the cavity portion 33 connects the radial outer surface (radial side surface) 31 b and the radial inner surface (radial direction side surface) 31 a of the connecting ring portion 31. A part of the arc 33a is cut out. The center of the arc 33a is represented by P, and the radius is represented by r.

More specifically, the side surface of the pillar portion 32 viewed from the circumferential direction includes a first linear shape portion 33b which is a radial direction outer end portion (radial direction side end portion) which is cut away from the arc 33a and extends in the axial direction. Way of forming. The first linear shape portion 33b is disposed closer to the front side (the counter-load side, the left side in FIG. 19) than the center P of the circle. The first linear shape portion 33b overlaps the center Oi of the ball 3 (the spherical surface center of the cavity portion 33) in the axial direction.

In addition, the side surface of the pillar portion 32 viewed from the circumferential direction includes a second linear shape portion 33c, which is an end of the back side (load side, right side in FIG. 19) connecting the arc 33a to the first linear shape portion 33b. The portion and the end portion on the front side of the radially outer side surface 31 b of the ring portion 31 are cut out and formed. Therefore, the second linear shape portion 33c has a linear shape toward the inner side in the radial direction as it goes toward the back side (the ring portion 31 side).

In addition, the side surface of the column portion 32 viewed from the circumferential direction includes a third linear shape portion 33g which is formed by cutting the inner end portion (the other end portion in the radial direction) of the radial direction of the arc 33a and extending in the axial direction. form. The third linear shape portion 33 g is formed on the same plane as the radial inner surface 31 a of the ring portion 31 and is connected to the radial inner surface 31 a without a step.

In this way, the side surface of the pillar portion 32 viewed from the circumferential direction has a shape in which the third linear shape portion 33g, the arc 33a, the first linear shape portion 33b, and the second linear shape portion 33c are connected.

In the case of such a configuration, the same effects as those of the above embodiment can be obtained.

Next, each embodiment in which a plurality of parameters of the angular ball bearing 1 of the first embodiment is changed will be described.

(Example 1-1)

In the angular ball bearing 1 of this embodiment, the inner diameter is set to Φ15mm, the contact angle α is set to 50 °, and Ai (the height in the radial direction of the inner ring groove shoulder portion 22 divided by the diameter Dw of the ball 3) is a value The value is set to 0.38, and the value of Ae (the height He in the radial direction of the outer ring groove shoulder portion 12 divided by the diameter Dw of the ball 3) is set to 0.38. The material of the holder 30 is a polyamide resin. The relationship between the distance L between the balls and the circumference πdm of the three balls obtained by multiplying the pi by the ball pitch circle diameter dm satisfies L / πdm = 12 × 10 ^-3 .

By setting each parameter in this way, it was confirmed that the same effect as that of the above embodiment can be obtained.

(Example 1-2)

In the angular ball bearing 1 of this embodiment, the inner diameter is set to Φ60mm, the contact angle α is set to 60 °, and Ai (the height in the radial direction of the inner ring groove shoulder portion 22 divided by the diameter Dw of the ball 3) is a value The value is set to 0.47, and the value of Ae (the height He in the radial direction of the outer ring groove shoulder portion 12 divided by the diameter Dw of the ball 3) is set to 0.47. The material of the holder 30 is a polyacetal resin, and 10% by weight of carbon fiber is added as a reinforcing material. The relationship between the distance L between the balls and the circumference πdm of the three balls obtained by multiplying the pi by the ball pitch circle diameter dm satisfies L / πdm = 2.3 × 10 ^-3 .

By setting each parameter in this way, it was confirmed that the same effect as that of the above embodiment can be obtained.

(Examples 1-3)

In the angular ball bearing 1 of this embodiment, the inner diameter is set to Φ40mm, the contact angle α is set to 55 °, and the value of Ai (the height in the radial direction of the inner ring groove shoulder portion 22 divided by the diameter Dw of the ball 3) is The value is set to 0.43, and the value of Ae (the radial height He of the outer ring groove shoulder portion 12 divided by the diameter Dw of the ball 3) is set to 0.43. The material of the holder 30 is a polyamide resin, and 20% by weight of glass fiber is added as a reinforcing material. The relationship between the distance L between the balls and the circumference π dm of the three balls obtained by multiplying the pi by the ball pitch circle diameter dm satisfies L / πdm = 7.0 × 10 ^-3 .

By setting each parameter in this way, it was confirmed that the same effect as that of the above embodiment can be obtained.

(Second Embodiment)

Next, an angular ball bearing according to a second embodiment of the present invention will be described. Compared with the first embodiment, the angular ball bearing 1 of this embodiment differs in the configuration in which the holder 30 does not form the first linear shape portion 33b, and other basic configurations are substantially the same. Therefore, by adding the same symbols to the same or equivalent parts and omitting or simplifying the description, the different parts will be described in detail below.

As shown in FIG. 20, the side surface viewed from the circumferential direction of the pillar portion 32 forming the cavity portion 33 in this embodiment connects the inner side surface (radial side surface) 31a in the radial direction of the ring portion 31 and the outer side surface in the radial direction ( The other side of the radial direction) 31b is partially cut off.

More specifically, the side surface of the pillar portion 32 viewed from the circumferential direction includes a second linear shape portion 33c, which connects the radial inner end portion (radial side end portion, bottom portion) 33e of the circular arc 33a, and At least a part of the portion of the inner surface 31 a in the radial direction of the ring portion 31 is cut out and formed. In this embodiment, the second linear shape portion 33c is connected in a straight line to the starting point X (the intersection point of the second linear shape portion 33c and the arc 33a) closer to the ring portion 31 side than the inner end portion 33e in the radial direction of the arc 33a. ), And the inner side surface 31a of the radial direction of the ring part 31 is comprised. In addition, the second linear shape portion 33c may be formed so as to connect the radially inner end portion 33e of the circular arc 33a and the radially inner side surface 31a of the ring portion 31. That is, a configuration in which the starting point X of the second linear shape portion 33c coincides with the radially inner end portion 33e of the arc 33a may be adopted.

As described above, the side surface of the pillar portion 32 in the present embodiment viewed from the circumferential direction has a shape in which the arc 33 a and the second linear shape portion 33 c are connected.

By forming the second linear shape portion 33c on the side surface viewed from the circumferential direction of the pillar portion 32 as described above, the axial direction distance ΔS1 between the retainer 30 and the inner ring 20 can be further increased (see FIG. 20), and the retention can be reduced. Possibility that the device 30 and the inner ring 20 interfere with each other. That is, you get The same effect is obtained in the first embodiment. For example, in FIG. 10 and FIG. 22, an example of a shape in the case where the radial load F is applied to the retainer 30 and the radial direction load is shown with a one-dot chain line is shown. Since the retainer 30 is bent in the radial direction, the radial position of the retainer 30 is closer to the inner ring 20 side or the outer ring 10 side. Therefore, the axial distance ΔS1 between the retainer 30 and the inner ring 20 becomes narrow, and the possibility that the retainer 30 and the inner ring 20 interfere with each other becomes high. When it is assumed that, as shown in FIG. 12, the side surface of the pillar portion 32 viewed from the circumferential direction is circular without the second linear shape portion 33 c, the axial direction distance ΔS1 between the retainer 30 and the inner ring 20 changes. It is narrow, and the possibility that the retainer 30 and the inner ring 20 interfere with each other becomes high. Therefore, as in the angular ball bearing 1 of this embodiment, the second linear shape portion 33c is formed on the side surface of the column portion 32 when viewed from the circumferential direction, so that the axial distance Δ between the retainer 30 and the inner ring 20 can be further increased. S1, and the possibility that the retainer 30 and the inner ring 20 interfere with each other can be reduced.

The starting point X of the second linear shape portion 33c is located closer to the ring portion 31 side than the center Oi of the ball 3 (the spherical center of the cavity portion 33). With this configuration, since the inner diameter of the column portion of the retainer 30 can be ensured, that is, the inner diameter of the contact point between the ball 3 and the cavity portion 33, the radial movement amount ΔR of the retainer 30 can be limited to an appropriate value. Here, as shown in FIG. 23, the radial movement amount ΔR of the cage 30 of the ball guide method is the radial direction gap ΔRi between the ball 3 on the inner side in the radial direction of the pocket portion 33 and the pocket portion 33, or The smaller the radial clearance ΔRe between the ball 3 on the outer side of the direction and the cavity portion 33 is determined as {ΔR = min (ΔRe, ΔRi)}. Thereby, the radial movement amount ΔR of the retainer 30 is not increased, and the contact between the retainer 30 and the inner ring 20 can be suppressed.

In addition, as shown in FIG. 21, the angular ball bearing 1 of this embodiment can be used side by side, and the outer ring chamfer 14 and the inner ring chamfer 24 are provided in the same manner as the first embodiment, thereby realizing the inner ring 20 Prevention of interference with the outer ring 10 and improvement of oil flowability.

In addition, the spherical center position of the cavity portion 33 is not limited to the radial direction intermediate position M of the outermost diameter portion m1 and the innermost diameter portion m2 of the ring portion 31, and the structure is offset to the inner side in the radial direction, as shown in FIG. 24. Shown is a configuration shifted to the outside in the radial direction. That is, it can also be used on the outer ring groove shoulder A ring portion 31 is arranged between the portion 12 and the inner ring countersunk hole 23, and a column portion 32 is arranged between the track surfaces 11 and 21 of the outer ring 10 and the inner ring 20, and the ring portion is connected to the inner end of the radial direction of the column portion 32 31 的 结构。 Structure of 31. In the example shown in the figure, the spherical center position of the pocket portion 33 is shifted to the outside in the radial direction from the outermost diameter portion m1 of the ring portion 31. In this case, the front end of the pillar portion 32 is also provided with a notch portion 34 in the middle in the circumferential direction and is bifurcated. Therefore, when the retainer 30 is manufactured by injection molding, it is possible to prevent forced extraction of the mold parts that form the cavity portion 33. The corner portion 35 on the side of the recessed portion 33 of the pillar portion 32 is caused by the damage.

Here, the side surface viewed from the circumferential direction of the pillar portion 32 forming the cavity portion 33 is the radial outer surface (radial direction one side) 31 b and the radial inner surface (radial direction other side) 31 a of the connecting ring portion 31. A part of the arc 33a is cut out. The center of the arc 33a is the same as the center Oi of the ball 3 (the center of the spherical surface of the concave portion 33), and the radius is represented by r.

More specifically, the side surface of the pillar portion 32 viewed from the circumferential direction includes a second linear shape portion 33c, which connects the radial outer end portion (radial side end portion) 33f of the circular arc 33a and the ring portion. At least a part of the portion of the 31-direction radial outer surface 31b is cut out. In this embodiment, the second linear shape portion 33c is connected in a straight line to the starting point X (the intersection point of the second linear shape portion 33c and the arc 33a) closer to the ring portion 31 side than the outer end portion 33f in the radial direction of the arc 33a. ), And the radial outer surface 31b of the ring portion 31 is configured. The second linear shape portion 33c may be formed so as to connect the radially outer end portion 33f of the circular arc 33a and the radially outer side surface 31b of the ring portion 31. That is, the starting point X of the second linear shape portion 33c and the radial end portion 33f in the radial direction of the arc 33a may be configured.

As described above, the side surface of the pillar portion 32 in the present embodiment viewed from the circumferential direction has a shape in which the arc 33 a and the second linear shape portion 33 c are connected.

In this way, by forming the second linear shape portion 33c by the recessed portion 33, the axial distance ΔS2 between the retainer 30 and the outer ring 10 can be further increased, and the possibility of interference between the retainer 30 and the outer ring 10 can be reduced. .

In addition, the starting point X of the second linear shape portion 33c is arranged at the outer end portion in the radial direction. 33f is closer to the ring portion 31 side, because the outer diameter of the pillar portion of the retainer 30 can be ensured, that is, the outer diameter of the contact point between the ball 3 and the cavity portion 33, the radial movement amount ΔR of the retainer 30 can be limited Is an appropriate value. Thereby, the radial movement amount ΔR of the holder 30 is not increased, and the contact between the holder 30 and the outer ring 10 can be suppressed.

Next, each embodiment in which a plurality of parameters of the angular ball bearing 1 of the second embodiment is changed will be described.

(Example 2-1)

In the angular ball bearing 1 of this embodiment, the inner diameter is set to Φ15mm, the contact angle α is set to 50 °, and Ai (the height in the radial direction of the inner ring groove shoulder portion 22 divided by the diameter Dw of the ball 3) is a value The value is set to 0.38, and the value of Ae (the height He in the radial direction of the outer ring groove shoulder portion 12 divided by the diameter Dw of the ball 3) is set to 0.38. The material of the holder 30 is a polyamide resin. The relationship between the distance L between the balls and the circumference πdm of the three balls obtained by multiplying the pi by the ball pitch circle diameter dm satisfies L / πdm = 12 × 10 ^-3 .

By setting the parameters in this way, it is confirmed that the holder 30 is prevented from coming into contact with the inner ring 20 or the outer ring 10.

(Example 2-2)

In the angular ball bearing 1 of this embodiment, the inner diameter is set to Φ60mm, the contact angle α is set to 60 °, and Ai (the height in the radial direction of the inner ring groove shoulder portion 22 divided by the diameter Dw of the ball 3) is a value The value is set to 0.47, and the value of Ae (the height He in the radial direction of the outer ring groove shoulder portion 12 divided by the diameter Dw of the ball 3) is set to 0.47. The material of the holder 30 is a polyacetal resin, and 10% by weight of carbon fiber is added as a reinforcing material. The relationship between the distance L between the balls and the circumference πdm of the three balls obtained by multiplying the pi by the ball pitch circle diameter dm satisfies L / πdm = 2.3 × 10 ^-3 .

By setting the parameters in this way, it is confirmed that the holder 30 is prevented from coming into contact with the inner ring 20 or the outer ring 10.

(Example 2-3)

In the angular ball bearing 1 of this embodiment, the inner diameter is set to Φ40mm, the contact angle is set to 55 °, and the value of Ai (the height in the radial direction of the inner ring groove shoulder portion 22 divided by the diameter Dw of the ball 3) is set. It is 0.43, and the value of Ae (the radial height He of the outer ring groove shoulder portion 12 divided by the diameter Dw of the ball 3) is set to 0.43. The material of the holder 30 is a polyamide resin, and 20% by weight of glass fiber is added as a reinforcing material. The relationship between the distance L between the balls and the circumference π dm of the three balls obtained by multiplying the pi by the ball pitch circle diameter dm satisfies L / πdm = 7.0 × 10 ^-3 .

By setting the parameters in this way, it is confirmed that the holder 30 is prevented from coming into contact with the inner ring 20 or the outer ring 10.

The present invention is not limited to those described in the above embodiments, and can be appropriately changed, improved, and the like.

Also, this application is based on the Japanese Patent Application 2014-56627 filed on March 19, 2014, the Japanese Patent Application 2014-56628 filed on March 19, 2014, and the patent based on July 17, 2014 For the international application PCT / JP2014 / 069091 of the cooperation treaty, the contents thereof are incorporated herein by reference.

Claims (7)

An angular ball bearing is characterized by comprising: an outer ring having a track surface on an inner peripheral surface; an inner ring having a track surface on an outer peripheral surface; a plurality of balls arranged on the outer ring and the inner ring; Between the track surfaces; and a retainer, which is a ball-guided type and keeps the balls rolling freely; and in the outer peripheral surface of the inner ring, an inner ring countersink is recessed on the back side and convex on the front side Ring groove shoulder; in the inner peripheral surface of the outer ring, an outer ring countersink is recessed on the front side, and an outer ring groove shoulder is protruding on the back side; and the contact angle α of the balls is 45 ° ≦ α ≦ 65 ° ; If the value obtained by dividing the radial height of the shoulder of the inner ring groove by the ball diameter is set to Ai, then 0.35 ≦ Ai ≦ 0.50; if the value of the radial height of the shoulder of the outer ring groove is divided by the ball diameter When Ae is set, 0.35 ≦ Ae ≦ 0.50; and the retainer has a generally annular ring portion, a plurality of column portions protruding from the front side or the back side of the ring portion at specific intervals in the axial direction, and formed Crown-shaped protection of a plurality of recessed portions between the adjacent pillar portions The spherical center position of the cavity portion is offset from the radial position between the outermost diameter portion and the innermost diameter portion of the ring portion to the radial direction side; The side surface viewed in the circumferential direction is obtained by cutting out a part of an arc connecting one side of the ring portion in the radial direction and the other side in the radial direction, and includes a first linear shape portion to cut off the diameter of the circular arc. The end portion on one side is formed so as to extend in the axial direction, and the center of the ball is offset from the center of the arc. For example, the angular ball bearing of claim 1, wherein the side surface of the column portion forming the recessed portion viewed from the circumferential direction includes a second linear shape portion that connects the arc to the first linear shape portion, A part of one side surface of the ring portion in the radial direction is cut out and formed. For example, the angular ball bearing of claim 1, wherein the center of the ball and the first linear shape portion overlap in the axial direction. For example, the angular ball bearing of claim 2, wherein the center of the ball and the first linear shape portion overlap in the axial direction. An angular ball bearing is characterized by comprising: an outer ring having a track surface on an inner peripheral surface; an inner ring having a track surface on an outer peripheral surface; a plurality of balls arranged on the outer ring and the inner ring; Between the track surfaces; and a retainer, which is a ball-guided type and keeps the balls rolling freely; and in the outer peripheral surface of the inner ring, an inner ring countersink is recessed on the back side and convex on the front side Ring groove shoulder; in the inner peripheral surface of the outer ring, an outer ring countersink is recessed on the front side, and an outer ring groove shoulder is protruding on the back side; and the contact angle α of the balls is 45 ° ≦ α ≦ 65 ° ; If the value obtained by dividing the radial height of the shoulder of the inner ring groove by the ball diameter is set to Ai, then 0.35 ≦ Ai ≦ 0.50; if the value of the radial height of the shoulder of the outer ring groove is divided by the ball diameter Set to Ae, then 0.35 ≦ Ae ≦ 0.50; The retainer includes a substantially annular ring portion, a plurality of column portions protruding from the front side or the back side of the ring portion at specific intervals in the axial direction, and a plurality of column portions formed between the adjacent column portions. Crown-shaped retainer of the recessed portion; the spherical center position of the recessed portion is offset from the radial direction intermediate position between the outermost diameter portion and the innermost diameter portion of the ring portion to the radial direction side; forming the recessed portion The side surface of the column part viewed from the circumferential direction is obtained by cutting out a part of an arc connecting one side surface in the radial direction and the other side surface in the radial direction of the ring portion, and includes: a linear shape part that connects the At least a part of one end portion in the radial direction side of the arc and a portion in the radial direction side surface of the ring portion is formed by cutting out, and the center of the ball is offset from the center of the arc. The angular ball bearing of claim 5, wherein the center of the ball and the linear shape portion overlap in the axial direction. The oblique ball bearing of any one of claims 1 to 6, wherein the relationship between the distance L between adjacent balls and the ball pitch circle diameter dm obtained by multiplying the pi by the ball pitch circle diameter dm satisfies 2.5 × 10 ^-3 ≦ L / πdm ≦ 13 × 10 ^-3 .