TW201600750A - Angular ball bearing - Google Patents

Abstract

A retainer (30) is crown-shaped and has: a substantially annular ring (31); columns (32) arranged at predetermined intervals and axially protruding from the front face side or the rear face side of the ring (31); and pockets (33) each formed between adjacent columns (32). The center of the spherical surface of each of the pockets (33) is offset to one radial side from the radially intermediate position (M) between the outermost radial section (m1) and the innermost radial section (m2) of the ring (31). When viewed circumferentially, a side surface of each of the columns (32) which form the pockets (33) includes a first straight-shaped section (33b) formed so as to extend axially, the first straight-shaped section (33b) being formed in such a manner that: a part of a circular arc (33a) which connects one radial side surface of the ring (31) and the other radial side surface thereof is cut out; and one radial end of the circular arc (33a) is cut out.

Description

Oblique ball bearing

The present invention relates to bevel ball bearings.

In the NC (Numerical Control) lathe, milling machine, automatic tool changer (machining center), multi-tasking machine, five-axis machine, and other working machines, or the spindle table or the linear motion mechanism of the machine tool In the case, a ball screw that converts a rotary motion into a linear motion is used. A bevel ball bearing is used as a bearing that rotatably supports the shaft end of the ball screw (for example, refer to Patent Document 1). These bearings are based on the size of the machine head of the working machine used or the machine tool on which the workpiece is mounted, and the inner diameter of the bearing is about Φ10mm~Φ100mm.

The cutting load generated during machining or the inertial load in the case where the spindle table and the machine tool are moved with high acceleration are applied to the bevel ball bearing by the ball screw as an axial load. Recently, working machines have a tendency to increase the inertial load caused by cutting load or fast-forwarding for the purpose of high-efficiency machining, and to apply a large axial load to the bevel ball bearing.

Therefore, in order to increase the rolling fatigue life, the bevel ball bearing for supporting such a ball screw must increase the load capacity in the axial direction and the high rigidity to maintain the machining accuracy.

[Previous Technical Literature] [Patent Literature]

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

In order to make the two of them stand up, as long as the bearing size is increased, the number of combinations of the rows can be increased. However, if the bearing size is increased, the space of the ball screw shaft end is increased, and if the number of combinations is excessive, When the ground is increased, the ball screw unit portion has a wide 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 required floor space of the working machine or an increase in the size of the height direction.

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

The above object of the present invention is achieved by the following constitution.

(1) An oblique-angle ball bearing, comprising: an outer ring having a raceway surface on an inner circumferential surface; an inner ring having a raceway surface on an outer circumferential surface; a plurality of balls disposed on the outer ring and the above Between the orbital surfaces of the inner ring; and the retainer, which is a ball guiding method, and holds the balls to roll freely; and in the outer peripheral surface of the inner ring, an inner ring countersunk hole is recessed on the back side, on the front side The inner ring groove shoulder portion is provided on the side protrusion; in the inner circumferential surface of the outer ring, an outer ring countersunk hole 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 ball is 45° ≦65°; if the diameter of the inner ring groove shoulder is divided by the diameter of the ball, Ai is 0.35≦Ai≦0.50; if the diameter of the outer ring groove shoulder is divided by the diameter of the ball to be Ae, then 0.35≦Ae≦0.50; the above retainer crown retainer, a ring portion having a substantially annular shape, a plurality of column portions protruding from the front side or the back side of the ring portion at a predetermined interval in the axial direction, and a plurality of recess portions formed between the adjacent column portions; The spherical center position of the pocket portion is offset from the intermediate position between the outermost diameter portion and the innermost diameter portion of the ring portion to the radial direction side; and the column portion forming the recess portion is viewed from the circumferential direction The side surface is a part of a circular arc connecting one side surface of the ring portion in the radial direction and the other side surface in the radial direction, and includes a first linear shape portion for cutting the radial direction of the circular arc One end portion is formed to extend in the axial direction.

(2) The bevel ball bearing according to the first aspect of the invention, wherein the side surface of the column portion forming the recess portion viewed from a circumferential direction includes: a second linear shape portion that connects the arc A linear portion is formed by cutting a portion of the ring portion on one side in the radial direction.

(3) An oblique-angle ball bearing, comprising: an outer ring having a raceway surface on an inner circumferential surface; an inner ring having a raceway surface on an outer circumferential surface; a plurality of balls disposed on the outer ring and the above Between the track faces of the inner ring; and the retainer, which is a ball guiding method, and holds the balls to roll freely; and in the outer peripheral surface of the inner ring, an inner ring countersunk hole is recessed on the back side, on the front side Protruding the inner ring groove shoulder; In the inner circumferential surface of the outer ring, an outer ring countersunk hole 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 ball is 45° ≦α≦65°; The value obtained by dividing the diameter of the ring groove by the diameter of the ball is Ai, 0.35 ≦ Ai ≦ 0.50; and if the height of the outer ring groove shoulder is divided by the ball diameter, the value is Ae. 0.35≦Ae≦0.50; the retainer crown-type retainer having a substantially annular ring portion, a plurality of column portions protruding from the front side or the back side of the ring portion at a predetermined interval in the axial direction, and forming a plurality of recessed portions between the adjacent column portions; the spherical center position of the recessed portion is offset from the radially outermost portion and the innermost portion of the annular portion by a radial direction a side surface of the column portion forming the recess portion viewed from a circumferential direction is a portion of a circular arc connecting one side surface of the ring portion in the radial direction and the other side surface in the radial direction, and includes: a straight line a shape portion that connects the end portion of the arc in the radial direction, At least a portion of a side surface of the cutting portion above the radial direction of the ring portion is formed.

(4) The bevel ball bearing according to any one of the items (1) to (3), wherein a distance between the balls adjacent to each other is L, and a circumference ratio π is multiplied by a ball pitch diameter dm, and a circumference of the ball joint is πdm. The relationship satisfies 2.5 × 10 ^-3 ≦ L / πdm ≦ 13 × 10 ^-3 .

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

Also, the value obtained by dividing the diameter of the inner ring groove shoulder by the diameter of the ball is set to Ai. When 0.35 ≦ Ai ≦ 0.50, the value obtained by dividing the diameter of the outer ring groove shoulder by the ball diameter is Ae, 0.35 ≦ Ae ≦ 0.50, thereby preventing the load capacity of the bearing in the axial direction from being insufficient, and Grinding of the inner and outer ring groove shoulders is easy.

Further, the side surface of the column portion forming the recessed portion as viewed from the circumferential direction is formed by cutting one side surface of the connecting ring portion in the radial direction and one of the arcs on the other side in the radial direction, and includes: a first straight line shape The portion is formed to cut the end portion of the circular arc in the radial direction and extend in the axial direction. Therefore, the contact between the retainer and the ball is in line contact, and when the retainer moves in the radial direction, the ball is flexibly engaged into the recessed portion of the retainer, so that the relative movement of the retainer in the axial direction can be suppressed. Thereby, it is possible to suppress a change in the amount of movement of the retainer in the radial direction, and it is possible to suppress an increase in vibration during the rotation of the bearing. Further, by restricting the holder by the portion in which the line is in contact, the movement in the axial direction can be suppressed to a minimum. As a result, problems such as the retainer sound or the premature breakage of the retainer can be eliminated. Further, since the pitch position of the pocket portion of the retainer and the pitch position of the ball are prevented from being shifted with respect to the axial direction, it is easy to accurately measure the outer diameter or the inner diameter of the retainer.

1‧‧‧Bevel ball bearings

3‧‧‧ balls

10‧‧‧Outer Ring

11‧‧‧Track surface

12‧‧‧Outer ring shoulder

13‧‧‧ outer ring countersink

14‧‧‧Outer ring chamfer

20‧‧‧ Inner Ring

21‧‧‧ Track surface

22‧‧‧ Inner ring shoulder

23‧‧‧ Inner ring countersink

24‧‧‧ Inner ring chamfer

30‧‧‧keeper

31‧‧‧ Ring Department

31a‧‧‧The inner side of the diameter of the ring

31b‧‧‧The outer side of the ring

32‧‧‧ Column Department

33‧‧‧ recesses

33a‧‧‧ arc

33b‧‧‧1st linear shape

33c‧‧‧2nd linear shape

33d‧‧‧Inside the inner end of the pocket

33e‧‧‧Inside the inner end of the circle

33f‧‧‧ The outer end of the circle

33g‧‧‧3rd linear shape

34‧‧‧Gap section

35‧‧‧ corner

100‧‧‧ deep groove bearing

110‧‧‧ outer ring

120‧‧‧ Inner Ring

130‧‧‧keeper

A‧‧‧ arrow

A‧‧‧ center point

A-A'‧‧‧ profile

B‧‧‧ Center Point

C‧‧‧ intersection

D‧‧‧ intersection

D1‧‧‧ OD

D2‧‧‧ OD

D3‧‧‧Inner diameter

D4‧‧‧Inner diameter

Dw‧‧·ball diameter

Dm‧‧‧Ball pitch diameter

E‧‧‧ midpoint

F‧‧‧ radial direction load

The height of the He‧‧‧ outer ring shoulder

Hi‧‧‧ height of the inner ring groove shoulder

L‧‧‧ Distance between balls

M‧‧‧ intermediate position in the radial direction

M1‧‧‧ outer diameter

M2‧‧‧ inner diameter

O‧‧‧Festival Center

Oi‧‧·The Ball Center

P‧‧‧ Round Center

R‧‧‧ Radius

R1‧‧‧ radius

T‧‧‧The distance between the center of the ball

VI-VI‧‧‧ line

Line VII-VII‧‧

Starting point of X‧‧

XIII-XIII‧‧‧ line

XIV-XIV‧‧‧ line

XIX-XIX‧‧‧ line

XV‧‧ Direction

XXIII‧‧ Direction

‧‧‧‧contact angle

Θ‧‧‧ angle

△A‧‧‧Axis direction movement

△R‧‧‧ radial direction movement

△Re‧‧‧diameter clearance

△Ri‧‧‧diameter clearance

△S1‧‧‧Axis direction distance

△S2‧‧‧Axis direction distance

BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a cross-sectional view showing a bevel ball bearing according to an embodiment of the present invention.

Figure 2 is a cross-sectional view of the beveled ball bearing of Figure 1 in parallel.

Figure 3 is a side view of the retainer.

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

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

Figure 6 is a cross-sectional view taken along line VI-VI of Figure 4.

Figure 7 is a cross-sectional view taken along line VII-VII of Figure 4;

Figure 8 is a cross-sectional view of a prior deep groove ball bearing.

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

Figure 10 is a cross-sectional view of the bevel ball bearing when the retainer is loaded in the radial direction.

Figure 11 is a diagram for explaining the arrangement state of a plurality of balls.

Figure 12 is a cross-sectional view of a prior beveled ball bearing.

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

Fig. 14 is a cross-sectional view showing the XIV-XIV cross-section of the retainer recessed portion in the axial direction in a retainer and a ball of Fig. 12.

Figure 15 is a view of the retainer viewed from the XV direction in Figure 12;

Figure 16 is a view showing the holder of the present invention.

Figure 17 is a cross-sectional view of a beveled ball bearing of a variation.

Fig. 18 is a view showing the retainer of the modification as seen from the side in the axial direction.

Figure 19 is a cross-sectional view taken along the line XIX-XIX of Figure 18.

Figure 20 is a cross-sectional view showing a bevel ball bearing according to an embodiment of the present invention.

Figure 21 is a cross-sectional view of the beveled ball bearing of Figure 20 in a side-by-side combination.

Figure 22 is a cross-sectional view of the bevel ball bearing when the retainer is loaded in the radial direction.

Fig. 23 (a) is a side view of the retainer, and (b) is a XXIII direction view of the A-A' cross section of the line (a).

Figure 24 is a cross-sectional view of a beveled ball bearing of a variation.

Hereinafter, the bevel ball bearing of each embodiment of the present invention will be described with reference to the drawings.

(First embodiment)

As shown in Fig. 1, the bevel ball bearing 1 of the present embodiment includes an outer ring 10 having a raceway surface 11 on an inner circumferential surface, an inner ring 20 having a raceway surface 21 on an outer peripheral surface, and a plurality of balls 3, And the like is disposed between the outer ring 10 and the track faces 11 and 21 of the inner ring 20; and the retainer 30 is a ball guiding method, and the balls 3 are kept to roll freely.

The inner circumferential surface of the outer ring 10 has an outer ring groove shoulder portion 12 which is protruded from the track surface 11 to the back side (load side, left side in FIG. 1); and the outer ring countersunk hole 13 is relatively orbital. The face 11 is recessed on the side closer to the front side (reverse load side, right side in Fig. 1).

The outer circumferential surface of the inner ring 20 has an inner ring groove shoulder portion 22 which is protruded from the track surface 21 toward the front side (load side, right side in FIG. 1); and inner ring countersunk hole 23, which is more than the track surface. The 21 recess is placed on the back side (the opposite load side, the left side in Figure 1).

Here, if the outer diameter of the inner ring countersunk hole 23 is D1, and the outer diameter of the inner ring groove shoulder portion 22 is D2, D1 < D2, and if the outer ring countersunk hole 13 is inside diameter When D3 is set and the inner diameter of the outer ring groove shoulder portion 12 is D4, D3>D4 is set. Thus, 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 ? of the balls 3 can be set large. More specifically, by setting the outer diameter D2 and the inner diameter D4 in the above-described manner, the contact angle α can be set to about 45° ≦ α ≦ 65°, and even if the contact angle α during the bearing production is changed, It is set to 50° ≦α≦60°, and the contact angle α can be increased.

When the value of the radial height Hi of the inner ring groove shoulder portion 22 is divided by the diameter Dw of the ball 3 as Ai (Ai = Hi / Dw), it is set so as to satisfy 0.35 ≦ Ai ≦ 0.50, and if The height of the outer ring groove shoulder portion 12, divided by the diameter Dw of the ball 3, is set to Ae (Ae = He / Dw), and is set so as to satisfy 0.35 ≦ Ae ≦ 0.50.

In the case of assuming 0.35>Ai or 0.35>Ae, since the radial heights Hi and He of the inner ring groove shoulder 22 or the outer ring groove shoulder 12 are too small with respect to the diameter Dw of the ball 3, the contact angle α is less than 45. °, the bearing capacity of the bearing in the axial direction is insufficient. Further, in the case of 0.50 < Ai or 0.50 < Ae, since the raceway faces 11 and 21 of the outer ring 10 and the inner ring 20 are formed to exceed the pitch diameter dm of the ball 3, the outer ring groove shoulder portion 12 and the inner ring groove Grinding of the shoulder 22 is more difficult and undesirable.

Further, at the end portion on the back side of the outer ring groove shoulder portion 12, a ring-shaped chamfer 14 is formed in a tapered shape toward the outer side in the radial direction toward the back side, and the front end portion of the inner ring groove shoulder portion 22 is provided. An inner ring chamfer 24 having a tapered shape toward the inner side in the radial direction toward the front side is provided. The radial width of the outer ring chamfer 14 and the inner ring chamfer 24 is greater than one half of the heights He and Hi of the outer ring groove shoulder portion 12 and the inner ring groove shoulder portion 22, and is set to a larger value.

Such a bevel ball bearing 1 is shown in Fig. 2 and can be used in combination. Due to this reality The oblique-angle ball bearing 1 of the embodiment has the outer ring groove shoulder portion 12 and the inner ring groove shoulder portion 22 disposed near the pitch diameter dm of the ball 3, so it is assumed that the outer ring chamfer 14 and the inner ring chamfer are not provided. 24, the inner ring 20 of the bevel ball bearing 1 and the outer ring 10 of the other bevel ball bearing 1 interfere with each other, resulting in a poor condition in the rotation of the bearing. Further, in the case of oil lubrication, it is assumed that the outer ring chamfer 14 and the inner ring chamfer 24 are not provided, the oil does not pass between the respective bevel ball bearings 1, and the oil flow is deteriorated, the lubrication is poor, or the oil A large amount remains in the inside of the bearing and causes a temperature rise. Thus, 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 to improve the fluidity of the oil. In addition, the outer ring chamfer 14 and the inner ring chamfer 24 are not necessarily provided with two, 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 holder 30 is a plastic holder that includes a ball guiding method of synthetic resin, and constitutes a base resin polyamine resin of the holder 30. Further, the type of the polyamide resin is not limited, and other synthetic resins such as polyacetal resin, polyether ether ketone, and polyamidiene may be used in addition to polyamine. Further, glass fibers, carbon fibers, aromatic polyamide fibers, and the like are added as a reinforcing material to the base resin. Further, the holder 30 is manufactured by injection molding or cutting.

The retainer 30 is a crown type retainer having a substantially annular ring portion 31 (see FIG. 1) disposed coaxially with the inner ring 20 and the outer ring 10, and a specific interval from the back side of the ring portion 31. A plurality of column portions 32 projecting in the axial direction and a plurality of recess portions 33 formed between the adjacent column portions 32.

Here, in the bevel ball bearing 1 of the present embodiment, in order to achieve high load capacity in the axial direction load, the heights He and Hi in the radial direction of the outer ring groove shoulder portion 12 and the inner ring groove shoulder portion 22 are increased. The internal space of the bearing is reduced. Therefore, when the retainer 30 disposed in the inner space of the bearing is a crown retainer (single-sided ring structure), the ring portion 31 is disposed between the outer ring counterbore 13 and the inner ring groove shoulder 22, Further, a column portion 32 is disposed between the outer ring 10 and the raceway surfaces 11 and 21 of the inner ring 20, and the ring portion 31 is connected to the radially outer end portion of the column portion 32.

In other words, as shown in Fig. 7, the spherical center position of the pocket portion 33 is shifted from the outermost diameter portion m1 of the ring portion 31 to the intermediate position M in the radial direction of the innermost diameter portion m2, and is shifted to the radially inner side (diameter direction). The construction of one side). Here, the spherical center position of the pocket portion 33 is at a position coincident with the center Oi of the ball 3. Further, the outermost diameter portion m1 of the ring portion 31 is the outer side surface 31b in the radial direction, and the innermost diameter portion m2 is the inner side surface 31a in the radial direction. Further, in the illustrated example, the spherical center position of the pocket portion 33 is shifted from the innermost diameter portion m2 of the ring portion 31 to the inner side in the radial direction.

As shown in Fig. 7, the side surface of the column portion 32 forming the recessed portion 33 as viewed from the circumferential direction is the inner side surface (one side surface in the radial direction) 31a and the outer side surface in the radial direction of the connecting ring portion 31 (the other side in the radial direction) One of the arcs 33a of the side surface 31b is cut. The center of the arc 33a is denoted by P, and the radius is denoted by r.

More specifically, the side surface of the column portion 32 viewed from the circumferential direction includes a first linear portion 33b that cuts the radially inner end portion (the end portion in the radial direction) of the circular arc 33a and is in the axial direction. The way of extension is formed. The first linear shape portion 33b is disposed closer to the back side than the center P of the circular arc 33a. Further, the first linear shape portion 33b overlaps with the center Oi of the ball 3 (the spherical center of the pocket portion 33) in the axial direction.

Further, the side surface of the column portion 32 viewed from the circumferential direction includes a second linear portion 33c that connects the end portion of the arc portion 33a on the front side of the first linear portion 33b and the radial direction of the ring portion 31. A portion of the end portion on the back side of the inner side surface 31a is cut and formed. Therefore, the second linear portion 33c has a linear shape that faces outward in the radial direction toward the front side (the side of the ring portion 31).

In addition, the side surface of the column portion 32 viewed from the circumferential direction includes a third linear portion 33g that cuts the radially outer end portion (the other end portion in the radial direction) of the circular arc 33a and extends in the axial direction. The way is formed. The third linear portion 33g and the radially outer side surface 31b of the ring portion 31 are formed on the same plane, and are connected to the radial outer surface 31b without a step.

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

Further, as shown in Fig. 6, the side faces in the circumferential direction of the column portion 32 forming the recessed portion 33 and the side faces on the back side (the column portion 32 side) of the ring portion 31 are formed to be similar to the ball 3 when viewed in the radial direction. The shape of the spherical surface. Here, the tip end of the column portion 32 is provided with a notch portion 34 in the middle in the circumferential direction, and is branched. Thereby, when the holder 30 is manufactured by injection molding, it is possible to prevent breakage of the corner portion 35 on the side of the pocket portion 33 of the column portion 32 due to the forcible extraction of the mold member forming the recess portion 33.

Further, the ratio of the reinforcing material of the synthetic resin added to the material of the holder 30 is preferably 5 to 30% by weight. When the ratio of the reinforcing material in the synthetic resin component exceeds 30% by weight, the flexibility of the retainer 30 is lowered. Therefore, when the retainer 30 is forcibly pulled out from the recessed portion 33, or when the bearing is assembled, the ball 3 is assembled. When the recessed portion 33 is pressed, the corner portion 35 of the column portion 32 is broken. Further, 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 in the bearing rotation is relative to the pitch circle of the ball 3. The expansion of the diameter dm becomes larger, causing the balls 3 to interfere with the pocket portions 33 of the retainer 30, causing poor conditions such as scorching. Therefore, by setting the ratio of the reinforcing material in the synthetic resin component to the range of 5 to 30% by weight, the above-mentioned undesirable condition can be prevented.

Further, as the synthetic resin material of the retainer 30, a resin such as polyamine, polyetheretherketone, polyphenylene sulfide, or polyimine is used, and as a reinforcing material, glass fiber, carbon fiber, and aromatic polyamine are used. Fiber, etc.

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

However, in the case of the bevel ball bearing 1 of the present embodiment, when the retainer 30 overlaps the inner ring 20 or the outer ring 10 in the radial direction, the retainer 30 exceeds the design value, and for the inner ring 20 When the outer ring 10 is relatively moved in 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. When the side surface of the column portion 32 viewed from the circumferential direction does not have the shape of the second linear portion 33c (see FIG. 7), the axial distance ΔS1 between the retainer 30 and the inner ring 20 (refer to FIG. 1) The possibility of narrowing and the holder 30 and the inner ring 20 interfere with each other becomes high. When the retainer 30 and the inner ring 20 interfere with each other, the torque fluctuates when the retainer 30 interferes with the inner ring 20, and cannot be correctly positioned as the ball screw system, and the retainer 30 is worn due to the friction during the interference, resulting in the retainer 30. Broken. Further, the wear powder generated when the retainer 30 is worn becomes a foreign matter, which causes the lubrication state of the bearing to deteriorate, and as a result, the life of the bearing is shortened.

Therefore, in the bevel ball bearing 1 of the present embodiment, since the side surface of the column portion 32 viewed from the circumferential direction has the second linear portion 33c, the axial distance Δ between the retainer 30 and the inner ring 20 can be further increased. S1, and the possibility that the holder 30 and the inner ring 20 interfere with each other can be reduced.

Further, the bevel ball bearing 1 of the present embodiment increases the radial heights He and Hi of the outer ring groove shoulder portion 12 and the inner ring groove shoulder portion 22 to the balls 3 in order to maintain a large contact angle α. In the case of the pitch diameter dm, the radial direction between the outer ring 10 and the inner ring 20 is narrowed, and the diameter 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 made in the radial direction. Thickened relative to standard bearings. In particular, in the case of the crown retainer, since the ring portion 31 exists only on one side in the axial direction of the retainer 30, the wall thickness is insufficient to cause the strength of the ring portion 31 to decrease.

Further, the material of the retainer 30 is a synthetic resin such as a polyamide resin, a polyacetal resin, a polyether ether ketone or a polyimine, and the reinforcing fiber content of the base resin is also 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 the vibration load in the radial direction increases, the retainer 30 bends in the radial direction. In addition, in FIG. 9, the shape of the case where the load direction load F of the retainer 30 is load|transformed, and the radial direction bending is shown by the dotted line in FIG. Because the retainer 30 is bent in the radial direction The curvature causes the position of the retainer 30 in the radial direction to be close to the inner ring 20 side or the outer ring 10 side. Therefore, the axial direction distance ΔS1 between the retainer 30 and the inner ring 20 is narrowed, 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 column portion 32 viewed from the circumferential direction does not have the shape of the second linear shape portion 33c, the axial direction distance ΔS1 between the retainer 30 and the inner ring 20 is narrowed, and the retainer 30 and The possibility that the inner rings 20 interfere with each other becomes high. Therefore, in the bevel ball bearing 1 of the present embodiment, since the side surface of the column portion 32 viewed from the circumferential direction has the second linear portion 33c, the axial distance Δ between the retainer 30 and the inner ring 20 can be further increased. S1, and the possibility that the holder 30 and the inner ring 20 interfere with each other can be reduced.

Further, since the 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 thickened with respect to the standard bearing, the bending rigidity of the ring portion 31 may be insufficient. In this case, as shown by the arrow A in FIG. 6, the centrifugal force acting on the column portion 32 of the retainer 30 when the bearing is used causes the front end of the column portion 32 to expand outward in the radial direction, and the corner portion 35 is easy to be used. The direction of the week is expanding. Therefore, the axial movement amount ΔA of the retainer 30 becomes large. When the amount of movement ΔA in the axial direction of the retainer 30 is increased, the axial distance ΔS1 between the retainer 30 and the inner ring 20 is narrowed, 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 column portion 32 viewed from the circumferential direction does not have the shape of the second linear shape portion 33c, the axial direction distance ΔS1 between the retainer 30 and the inner ring 20 is narrowed, and the retainer 30 and The possibility that the inner rings 20 interfere with each other becomes high. Therefore, in the oblique-angle ball bearing 1 of the present embodiment, the axial direction distance Δ between the retainer 30 and the inner ring 20 can be further increased by forming the second linear portion 33c on the side surface of the column portion 32 as viewed from the circumferential direction. S1, and the possibility that the holder 30 and the inner ring 20 interfere with each other can be reduced.

Further, the bevel ball bearing 1 of the present embodiment is set so as to increase the number of balls 3 (the number of balls Z) in order to increase the axial load carrying capacity. More specifically, it demonstrates using FIG. In Fig. 11, two balls 3 arranged on the pitch circle of the diameter dm are shown, and the diameters of the balls 3 are set to Dw, and the centers of the balls 3 are set to A, B, line segments AB and balls 3 The intersection point of the surface is set to C, D, and the point in the line segment AB is set to E, the section The center of the circle is set to O. Further, 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 centers of the balls is T, and the distance between the adjacent balls 3 (the distance between the line segments CD), that is, the distance between the balls is set to L. 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. Thus, the distance between the line segment AO and the line segment BO is (dm/2), the distance T between the center of the balls is (dm × sin θ), the distance L between the balls is (T-Dw), and the angle θ is (180°/Z).

Further, the ball-to-ball distance L is multiplied by the circumference ratio π by the ball pitch circle diameter dm, and the ball joint circumference is πdm, so that the relationship of 2.5 × 10 ^-3 ≦L / πdm ≦ 13 × 10 ^-3 is established. . Assuming L/πdm is less than 2.5 × 10 ^-3 , the circumferential wall thickness of the column 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, which is a material of the retainer 30 at the time of molding, is deteriorated, and perforation is easy. Further, when I/πdm is larger than 13 × 10 ^-3 , the number of balls Z is small, and the axial load carrying capacity and rigidity of the bearing are lowered.

Thus, the bevel ball bearing 1 is designed to satisfy 2.5 × 10 ^-3 ≦L / πdm ≦ 13 × 10 ^-3 , that is, in such a manner that the number of balls Z is large, and the column portion 32 of the holder 30 is The wall thickness in the circumferential direction cannot be thickened relative to the standard bearing. Therefore, as the wall thickness of the column portion 32 in the circumferential direction becomes thinner, the wall thickness of the corner portion 35 becomes thin. Therefore, when the ball 3 collides with the corner portion 35 of the retainer 30 as shown by the arrow A in Fig. 6, the corner portion 35 is easily enlarged in the circumferential direction, and as a result, the amount of movement ΔA in the axial direction of the retainer is increased. Thereby, the axial direction distance ΔS1 between the retainer 30 and the inner ring 20 is narrowed, 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 column portion 32 viewed from the circumferential direction does not have the shape of the second linear shape portion 33c, the axial direction distance ΔS1 between the retainer 30 and the inner ring 20 is narrowed, and the retainer 30 and The possibility that the inner rings 20 interfere with each other becomes high. Therefore, in the bevel ball bearing 1 of the present embodiment, since the side surface of the column portion 32 viewed from the circumferential direction has the second linear portion 33c, the axial distance Δ between the retainer 30 and the inner ring 20 can be further increased. S1, and the possibility that the holder 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 a circular shape having an arbitrary radius r1 of the prior type, the rotation of the bearing is the same as that of the holder 30 of the above-described embodiment. In the middle, the relative movement amount ΔA of the retainer 30 in the axial direction becomes large. Further, when the side surface of the column portion 32 viewed from the circumferential direction is round, as shown in FIG. 15, the radially inner end portion 33d which is the portion of the guide portion 3 of the pocket portion 33 is in point contact with the ball 3. In this case, as shown in FIG. 13, the radial direction distance between the radially inner end portion 33d of the pocket portion 33 and the ball 3 is the radial direction movement amount ΔR of the retainer 30.

In this case, since the retainer 30 is in point contact with the ball 3, the retainer 30 is relatively easy to move in the axial direction with respect to the inner ring 20 or the outer ring 10 during the rotation of the bearing, and as a result, the diameter of the recess portion 33 is also made. The position of the direction inner end portion 33d moves in the axial direction. In Fig. 12, the pocket portion 33 (column portion 32) that moves in the axial direction is indicated by a dotted line. As described above, since the radial direction between the radially inner end portion 33d of the pocket portion 33 and the ball 3 is larger than that before moving in the axial direction, the amount of movement ΔR of the retainer 30 in the radial direction is Compared with before moving in the axial direction (see Fig. 13), the movement (see Fig. 14) is also larger.

Since this phenomenon occurs each time the holder 30 relatively moves in the axial direction with respect to the inner ring 20 or the outer ring 10, when the side surface of the column portion 32 viewed from the circumferential direction is round, the ball 3 cannot be stably guided. And the vibration of the holder 30 is increased to cause a problem that the holder sound or the holder 30 is broken in advance.

Therefore, in the present embodiment, the first straight-shaped portion 33b is provided on the side surface of the column portion 32 as viewed from the circumferential direction, and as shown in Fig. 16, the first straight line which is the portion of the guide portion 3 of the pocket portion 33 is formed. The shape portion 33b is configured to be in line contact with the balls 3 in an arc shape. Thus, by making the contact portion of the retainer 30 and the ball 3 into line contact, when the retainer 30 is moved in the radial direction, the balls 3 are flexibly engaged with the recessed portion 33, and the relative movement of the retainer 30 in the axial direction can be suppressed. . Therefore, the change in the radial direction movement amount ΔR of the retainer 30 can be prevented, and the increase in the vibration in the bearing rotation can be suppressed. Further, the movement of the retainer 30 in the axial direction is suppressed, and as a result, problems such as the retainer sound or the retainer 30 being damaged in advance can be suppressed.

When the side surface of the column portion 32 viewed from the circumferential direction is rounded (see FIG. 12), there is a problem that may occur in addition to the problem occurring in the above-described bearing rotation. This problem is caused by the fact that the pitch position of the pocket portion 33 of the retainer 30 is relatively offset from the pitch circle position of the ball 3 in the axial direction, so that the radial movement amount ΔR of the retainer 30 is changed from the design range. It is difficult to accurately measure the round diameter of the ball and the diameter of the ball inscribed during the manufacture of the retainer.

One of the measuring methods of the ball outer diameter and the ball inner diameter of the retainer 30 is that the ring portion 31 of the retainer 30 is placed below, and a light measuring load is applied to the inner side in the radial direction to fix the ball. 3 method of measurement. At this time, the balls 3 in the pocket portion 33 are closer to the ring portion 31 side in the pocket 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 direction movement amount ΔR of the retainer 30 is larger than that before the movement in the axial direction (see FIG. 13), and the movement (see FIG. 14) is large, and as a result, the radial direction movement amount ΔR is increased. More than the design range. In this case, it is difficult to accurately measure the round diameter of the ball of the retainer 30 and the diameter of the ball inscribed.

Therefore, in the present embodiment, the first linear portion 33b is provided on the side surface of the column portion 32 as viewed from the circumferential direction, and as shown in FIG. 16, the ball 3 is engaged with the first linear portion 33b by the measurement load. In part, the balls 3 are not offset in the axial direction, and it is easy to measure the round diameter of the balls and the in-line diameter of the balls.

Further, the spherical center position of the pocket portion 33 is not limited to the intermediate position M between the outermost diameter portion m1 and the innermost diameter portion m2 of the ring portion 31, and is shifted to the inner side in the radial direction, as shown in FIG. As shown in ~19, it is a configuration shifted to the outer side in the radial direction. In other words, the ring portion 31 may be disposed between the outer ring groove shoulder portion 12 and the inner ring countersunk hole 23, and the column portion 32 may be disposed between the outer ring 10 and the track faces 11 and 21 of the inner ring 20, and may be disposed at the column portion. The inner end portion of the radial direction of 32 is connected to the structure of the ring portion 31. Further, in the illustrated example, the spherical center position of the pocket portion 33 is shifted to the outer side in the radial direction from the outermost diameter portion m1 of the ring portion 31. In this case, also because the front end of the column portion 32 is in the week Since the notch portion 34 is provided in the middle of the direction and bifurcated, when the holder 30 is manufactured by injection molding, the side of the recess portion 33 of the column portion 32 due to the forced extraction of the mold member forming the recess portion 33 can be prevented. The corners 35 are broken.

Here, the side surface of the column portion 32 forming the recessed portion 33 as viewed from the circumferential direction is a radially outer side surface (one side surface) 31b of the connecting ring portion 31 and a radially inner side surface (the other side surface in the radial direction) 31a. One of the arcs 33a is cut. The center of the arc 33a is denoted by P, and the radius is denoted by r.

More specifically, the side surface of the column portion 32 viewed from the circumferential direction includes a first linear portion 33b that cuts the radially outer end portion (the end portion in the radial direction) of the circular arc 33a and is in the axial direction. The way of extension is formed. The first linear shape portion 33b is disposed on the front side (reverse load side, left side in FIG. 19) on the center P of the circle. Further, the first linear shape portion 33b overlaps with the center Oi of the ball 3 (the spherical center of the pocket portion 33) in the axial direction.

Further, the side surface of the column portion 32 viewed from the circumferential direction includes a second linear portion 33c that connects the end of the arc portion 33a on the back side (load side, right side in FIG. 19) of the first linear portion 33b. The portion is formed by cutting off a portion of the end portion on the front side of the radially outer side surface 31b of the ring portion 31. Therefore, the second linear portion 33c has a linear shape that faces the inner side in the radial direction toward the back side (the side of the ring portion 31).

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

In this manner, the side surface of the column portion 32 viewed from the circumferential direction has a shape in which the third linear portion 33g, the circular arc 33a, the first linear portion 33b, and the second linear 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 bevel ball bearing 1 of the first embodiment are changed will be described.

(Example 1-1)

In the bevel ball bearing 1 of the present embodiment, the inner diameter is set to Φ15 mm, the contact angle α is set to 50°, and the value of Ai (the height of the inner ring groove portion 22 in the radial direction divided by the diameter Dw of the ball 3) is set. The value is set to 0.38, and the value of Ae (the height He of the outer ring groove shoulder 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 ball-to-ball distance L and the circumference πdm of the ball 3 obtained by multiplying the circumference ratio π by the ball pitch circle diameter dm satisfies L/πdm = 12 × 10 ^-3 .

By setting each parameter as described above, it was confirmed that the same effects as those of the above-described embodiment were obtained.

(Example 1-2)

In the bevel ball bearing 1 of the present embodiment, the inner diameter is set to Φ60 mm, the contact angle α is set to 60°, and the value of Ai (the height of the inner ring groove portion 22 in the radial direction divided by the diameter Dw of the ball 3) is set. 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 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 fibers are added as a reinforcing material. The relationship between the ball-to-ball distance L and the circumference πdm of the ball 3 obtained by multiplying the circumference ratio π by the ball pitch diameter dm satisfies L/πdm = 2.3 × 10 ^-3 .

By setting each parameter as described above, it was confirmed that the same effects as those of the above-described embodiment were obtained.

(Example 1-3)

In the bevel ball bearing 1 of the present embodiment, the inner diameter is set to Φ40 mm, the contact angle α is set to 55°, and the value of Ai (the height of the inner ring groove portion 22 in the radial direction divided by the diameter Dw of the ball 3) is set. The value is set to 0.43, and the value of Ae (the height He in the radial direction of the outer ring groove portion 12 divided by the diameter Dw of the ball 3) is set to 0.43. The material of the holder 30 is a base resin which is a polyamide resin, and 20% by weight of glass fiber is added as a reinforcing material. The relationship between the ball-to-ball distance L and the circumference πdm of the ball 3 obtained by multiplying the circumference ratio π by the ball pitch circle diameter dm satisfies L/πdm = 7.0 × 10 ^-3 .

By setting each parameter as described above, it was confirmed that the same effects as those of the above-described embodiment were obtained.

(Second embodiment)

Next, a bevel ball bearing according to a second embodiment of the present invention will be described. The angled ball bearing 1 of the present embodiment differs from the first embodiment in that the configuration of the retainer 30 in which the first linear portion 33b is not formed is different, and the other basic configurations are substantially the same. Therefore, the description of the same or equivalent parts is omitted or simplified, and the different parts will be described in detail below.

As shown in Fig. 20, the side surface of the column portion 32 forming the recessed portion 33 of the present embodiment in the circumferential direction is the inner side surface (one side surface in the radial direction) 31a and the outer side surface in the radial direction of the connecting ring portion 31. One of the arcs 33a of the other side surface 31b of the radial direction is cut.

More specifically, the side surface of the column portion 32 viewed from the circumferential direction includes a second linear shape portion 33c that connects the radially inner end portion (the radial direction side end portion, the bottom portion) 33e of the circular arc 33a, and At least a part of the portion of the inner surface 31a of the ring portion 31 in the radial direction is cut and formed. In the present embodiment, the second linear portion 33c is linearly connected to the starting point X of the radially inner end portion 33e of the circular arc 33a toward the ring portion 31 (the intersection of the second linear portion 33c and the circular arc 33a) And the inner side 31a of the radial direction of the ring part 31 is comprised. Further, the second linear portion 33c may be formed 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. In other words, the starting point X of the second linear portion 33c and the radially inner end portion 33e of the circular arc 33a may be matched.

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

By forming the second linear portion 33c on the side surface of the column portion 32 as viewed from the circumferential direction, the axial distance ΔS1 between the retainer 30 and the inner ring 20 can be further increased (see FIG. 20), and the retention can be reduced. The possibility of the device 30 and the inner ring 20 interfering with each other. That is, you can get The same effects as in the first embodiment. For example, in FIGS. 10 and 22, an example in which the load F in the radial direction direction of the retainer 30 is applied and the shape is curved in the radial direction is schematically shown by a one-dot chain line. Since the retainer 30 is bent in the radial direction, the radial direction of the retainer 30 is close to the inner ring 20 side or the outer ring 10 side. Therefore, the axial direction distance ΔS1 between the retainer 30 and the inner ring 20 is narrowed, and the possibility that the retainer 30 and the inner ring 20 interfere with each other becomes high. As shown in FIG. 12, when the side surface of the column portion 32 viewed from the circumferential direction is a circular shape without the second linear shape portion 33c, the axial distance ΔS1 between the retainer 30 and the inner ring 20 is changed. It is narrow, and the possibility that the holder 30 and the inner ring 20 interfere with each other becomes high. Therefore, in the oblique-angle ball bearing 1 of the present embodiment, the axial direction distance Δ between the retainer 30 and the inner ring 20 can be further increased by forming the second linear portion 33c on the side surface of the column portion 32 as viewed from the circumferential direction. S1, and the possibility that the holder 30 and the inner ring 20 interfere with each other can be reduced.

Further, the starting point X of the second linear shape portion 33c is located closer to the center Oi of the ball 3 (the spherical center of the pocket portion 33), and further to the ring portion 31 side. According to this configuration, since the inner diameter of the column portion of the retainer 30, that is, the inner diameter of the contact point between the ball 3 and the recess portion 33, can be ensured, the radial movement amount ΔR of the retainer 30 can be restricted to an appropriate one. value. Here, the radial direction movement amount ΔR of the ball guide type retainer 30 is as shown in FIG. 23, and the radial direction gap ΔRi or the diameter of the ball 3 and the pocket portion 33 on the inner side in the radial direction of the recessed portion 33 is as shown in FIG. The smaller of the radial direction clearance ΔRe between the ball 3 on the outer side and the recessed portion 33 is determined to be {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.

Further, the bevel ball bearing 1 of the present embodiment can be used in parallel as shown in Fig. 21, and the outer ring chamfer 14 and the inner ring chamfer 24 are provided in the same manner as in the first embodiment, thereby realizing the inner ring 20 The interference between the outer ring 10 and the outer ring 10 and the improvement of the oil flowability.

Further, the spherical center position of the pocket portion 33 is not limited to the intermediate position M between the outermost diameter portion m1 and the innermost diameter portion m2 of the ring portion 31, and is shifted to the inner side in the radial direction, as shown in FIG. As shown, it is a configuration that is shifted to the outer side in the radial direction. That is, it can also be used on the outer ring shoulder The ring portion 31 is disposed between the portion 12 and the inner ring counterbore 23, and the column portion 32 is disposed between the outer ring 10 and the track faces 11 and 21 of the inner ring 20, and the ring portion is connected to the radially inner end portion of the column portion 32. The construction of 31. Further, in the illustrated example, the spherical center position of the pocket portion 33 is shifted to the outer side in the radial direction from the outermost diameter portion m1 of the ring portion 31. In this case, since the front end of the column portion 32 is provided with the notch portion 34 in the middle of the circumferential direction and is bifurcated, when the holder 30 is manufactured by injection molding, the forced pulling of the mold part due to the formation of the recess portion 33 can be prevented. The corner portion 35 on the side of the pocket portion 33 of the column portion 32 is broken.

Here, the side surface of the pillar portion 32 forming the recessed portion 33 as viewed from the circumferential direction is an outer surface (one side in the radial direction) 31b and a radially inner side surface (the other side in the radial direction) 31a of the connecting ring portion 31. One of the arcs 33a is cut. The center of the circular arc 33a coincides with the center Oi of the ball 3 (the spherical center of the recessed portion 33), and the radius is represented by r.

More specifically, the side surface of the column portion 32 viewed from the circumferential direction includes a second linear portion 33c that connects the radially outer end portion (the radial direction side end portion) 33f and the ring portion of the circular arc 33a. At least a part of the portion of the outer surface 31b in the radial direction of 31 is cut and formed. In the present embodiment, the second linear portion 33c is linearly connected to the starting point X of the radially outer end 33f of the circular arc 33a toward the ring portion 31 (the intersection of the second linear portion 33c and the circular arc 33a) And the outer side surface 31b of the ring part 31 in the radial direction is comprised. Further, the second linear portion 33c may be formed 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. In other words, the starting point X of the second linear portion 33c and the radially outer end portion 33f of the circular arc 33a may be matched.

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

Thus, by forming the second linear portion 33c by the recess portion 33, the axial direction distance ΔS2 between the retainer 30 and the outer ring 10 can be further enlarged, and the possibility that the retainer 30 and the outer ring 10 interfere with each other can be reduced. .

Moreover, the starting point X of the second linear shape portion 33c is disposed at the outer end portion in the radial direction. Further, 33f is closer to the side of the ring portion 31, since the outer diameter of the column portion of the retainer 30, that is, the outer diameter of the contact point between the ball 3 and the recess portion 33, can be ensured, so that the radial movement amount ΔR of the retainer 30 can be restricted. Is the appropriate value. Thereby, the radial movement amount ΔR of the retainer 30 is not increased, and the contact between the retainer 30 and the outer ring 10 can be suppressed.

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

(Example 2-1)

In the bevel ball bearing 1 of the present embodiment, the inner diameter is set to Φ15 mm, the contact angle α is set to 50°, and the value of Ai (the height of the inner ring groove portion 22 in the radial direction divided by the diameter Dw of the ball 3) is set. The value is set to 0.38, and the value of Ae (the height He of the outer ring groove shoulder 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 ball-to-ball distance L and the circumference πdm of the ball 3 obtained by multiplying the circumference ratio π by the ball pitch circle diameter dm satisfies L/πdm = 12 × 10 ^-3 .

By setting the parameters as described above, it is confirmed that the contact of the holder 30 with the inner ring 20 or the outer ring 10 is prevented.

(Example 2-2)

In the bevel ball bearing 1 of the present embodiment, the inner diameter is set to Φ60 mm, the contact angle α is set to 60°, and the value of Ai (the height of the inner ring groove portion 22 in the radial direction divided by the diameter Dw of the ball 3) is set. 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 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 fibers are added as a reinforcing material. The relationship between the ball-to-ball distance L and the circumference πdm of the ball 3 obtained by multiplying the circumference ratio π by the ball pitch diameter dm satisfies L/πdm = 2.3 × 10 ^-3 .

By setting the parameters as described above, it is confirmed that the contact of the holder 30 with the inner ring 20 or the outer ring 10 is prevented.

(Example 2-3)

In the bevel ball bearing 1 of the present embodiment, the inner diameter is set to Φ40 mm, the contact angle is set to 55°, and the value of Ai (the height of the inner ring groove portion 22 in the radial direction Hi divided by the diameter Dw of the ball 3) is set. The value of 0.43, Ae (the height He of the outer ring groove shoulder 12 divided by the diameter Dw of the ball 3) is set to 0.43. The material of the holder 30 is a base resin which is a polyamide resin, and 20% by weight of glass fiber is added as a reinforcing material. The relationship between the ball-to-ball distance L and the circumference πdm of the ball 3 obtained by multiplying the circumference ratio π by the ball pitch circle diameter dm satisfies L/πdm = 7.0 × 10 ^-3 .

By setting the parameters as described above, it is confirmed that the contact of the holder 30 with the inner ring 20 or the outer ring 10 is prevented.

Further, the present invention is not limited to the above-described embodiments, and can be appropriately modified, improved, and the like.

The present application is based on Japanese Patent Application No. 2014-56627, filed on March 19, 2014, and Japanese Patent Application No. 2014-56628, filed on March 19, 2014, and patents filed on July 17, 2014 The contents of the International Patent Application No. PCT/JP2014/069091, the disclosure of which is incorporated herein by reference.

30‧‧‧keeper

31‧‧‧ Ring Department

31a‧‧‧Inside the inner side of the ring

31b‧‧‧ outer side of the ring

32‧‧‧ Column Department

33‧‧‧ recesses

33a‧‧‧ arc

33b‧‧‧1st linear shape

33c‧‧‧2nd linear shape

33g‧‧‧3rd linear shape

M‧‧‧ intermediate position in the radial direction

M1‧‧‧ outer diameter

M2‧‧‧ inner diameter

Oi‧‧·The Ball Center

P‧‧‧ Round Center

R‧‧‧ Radius

Claims (4)

An oblique angle ball bearing, comprising: an outer ring having a raceway surface on an inner circumferential surface; an inner ring having a raceway surface on an outer circumferential surface; a plurality of balls disposed on the outer ring and the inner ring And a retainer, which is a ball guiding method, and holds the ball to roll freely; and in the outer peripheral surface of the inner ring, an inner ring countersunk hole is recessed on the back side, and is protruded on the front side The inner ring groove shoulder portion; the outer circumferential surface of the outer ring is recessed with an outer ring countersunk hole on the front side, and the outer ring groove shoulder is protruded on the back side; and the contact angle α of the ball is 45° ≦α≦65 °; if the value obtained by dividing the height of the inner ring groove shoulder by the ball diameter is Ai, then 0.35 ≦ Ai ≦ 0.50; if the diameter of the outer ring groove shoulder is divided by the ball diameter The value is Ae, which is 0.35 ≦Ae ≦ 0.50. The retainer has a substantially annular ring portion, a plurality of column portions protruding from the front side or the back side of the ring portion at a predetermined interval in the axial direction, and a crown of a plurality of pockets formed between the adjacent column portions a retainer; the spherical center position of the recess portion is offset from the intermediate position of the outermost diameter portion and the innermost diameter portion of the ring portion to the radial direction side; and the column portion of the recess portion is formed The side surface viewed from the circumferential direction is a portion of a circular arc connecting one side surface in the radial direction of the ring portion and the other side surface in the radial direction, and includes a first linear shape portion for cutting the circle Arc trail The direction is formed at one end and extends in the axial direction. The oblique-angle ball bearing according to claim 1, wherein the side surface of the column portion forming the recess portion viewed from a circumferential direction includes a second linear shape portion that connects the arcuate portion to the first linear shape portion, It is formed by cutting off a part of the side surface of the ring portion in the radial direction. An oblique angle ball bearing, comprising: an outer ring having a raceway surface on an inner circumferential surface; an inner ring having a raceway surface on an outer circumferential surface; a plurality of balls disposed on the outer ring and the inner ring And a retainer, which is a ball guiding method, and holds the ball to roll freely; and in the outer peripheral surface of the inner ring, an inner ring countersunk hole is recessed on the back side, and is protruded on the front side The inner ring groove shoulder portion; the outer circumferential surface of the outer ring is recessed with an outer ring countersunk hole on the front side, and the outer ring groove shoulder is protruded on the back side; and the contact angle α of the ball is 45° ≦α≦65 °; if the value obtained by dividing the height of the inner ring groove shoulder by the ball diameter is Ai, then 0.35 ≦ Ai ≦ 0.50; if the diameter of the outer ring groove shoulder is divided by the ball diameter The value is Ae, which is 0.35 ≦Ae ≦ 0.50. The retainer has a substantially annular ring portion, a plurality of column portions protruding from the front side or the back side of the ring portion at a predetermined interval in the axial direction, and forming a crown of a plurality of pockets between adjacent columns Holder; spherical center of the pocket portion of said uppermost position of the line representing the outer diameter portion of the ring portion and the maximum inner diameter portion of the diameter direction of the intermediate position, offset to one side of a radial direction; The side surface of the column portion forming the recess portion viewed from the circumferential direction is a portion of a circular arc connecting one side surface of the ring portion in the radial direction and the other side surface in the radial direction, and includes a linear portion. It is formed by cutting at least a part of the end portion of the circular arc in the radial direction and at least a portion of the side surface of the ring portion in the radial direction. The oblique-angle ball bearing according to any one of claims 1 to 3, wherein a relationship between the distances L of the adjacent balls and the circumference πdm of the ball joint obtained by multiplying the circumference ratio π by the diameter of the ball pitch circle dm satisfies 2.5 × 10 ^-3 ≦L/πdm≦13×10 ^-3 .