KR101988706B1 - Angular ball bearing - Google Patents

Angular ball bearing Download PDF

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Publication number
KR101988706B1
KR101988706B1 KR1020167023382A KR20167023382A KR101988706B1 KR 101988706 B1 KR101988706 B1 KR 101988706B1 KR 1020167023382 A KR1020167023382 A KR 1020167023382A KR 20167023382 A KR20167023382 A KR 20167023382A KR 101988706 B1 KR101988706 B1 KR 101988706B1
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South Korea
Prior art keywords
retainer
ring
outer ring
ball
diameter
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KR1020167023382A
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Korean (ko)
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KR20160113258A (en
Inventor
교헤이 마츠나가
요시아키 가츠노
Original Assignee
닛본 세이고 가부시끼가이샤
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/38—Ball cages
    • F16C33/41—Ball cages comb-shaped
    • F16C33/418—Details of individual pockets, e.g. shape or ball retaining means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/10—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for axial load mainly
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/38—Ball cages
    • F16C33/41—Ball cages comb-shaped
    • F16C33/412—Massive or moulded comb cages, e.g. snap ball cages
    • F16C33/414—Massive or moulded comb cages, e.g. snap ball cages formed as one-piece cages, i.e. monoblock comb cages
    • F16C33/416—Massive or moulded comb cages, e.g. snap ball cages formed as one-piece cages, i.e. monoblock comb cages made from plastic, e.g. injection moulded comb cages
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F16C33/583—Details of specific parts of races
    • F16C33/585—Details of specific parts of races of raceways, e.g. ribs to guide the rollers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/16—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls
    • F16C19/163—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls with angular contact
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
    • F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
    • F16C2240/46—Gap sizes or clearances

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

The retainer 30 includes a ring portion 31 having a substantially annular shape and a plurality of columnar portions 32 projecting in the axial direction at predetermined intervals from the front surface side or the back surface side of the ring portion 31, And a plurality of pocket portions (33) formed between the pair of side walls (32). To the retainer 30, a reinforcement material is added. The pitch circle diameter of the balls 3 in the X, ΔRmax = X 2 × 5.0 × 10 -6 + a X × 1.8 × 10 -3 +0.14 and, ΔRmin = X 2 × 5.5 × 10 -6 + X × 1.5 × 10 -3 +0.02, the radial movement amount? R of the holder 30 is? Rmin?? R?? Rmax. DELTA t < DELTA R > where DELTA t is the relative expansion of the retainer 30 at 100 DEG C in the radial direction.

Figure 112016082829594-pct00003

Description

ANGULAR BALL BEARING

The present invention relates to an angular ball bearing.

BACKGROUND ART A ball screw is used for a machine tool such as an NC lathe, a presser half, a machining center, a complex machining tool, a 5-axis machining tool, or the like and a linearly moving mechanism of a bed for mounting a main shaft or a workpiece. An angular ball bearing is employed as a bearing for rotationally supporting the shaft end of the ball screw (for example, see Patent Document 1).

The cutting load generated during machining or the inertia load when the main shaft and the bed are moved by rapid acceleration is loaded as an axial load to the angular ball bearing through the ball screw. In recent machine tools, an inertia load due to a cutting load or a rapid feed is large for the purpose of high-efficiency machining, and a large axial load tends to be loaded on an angular ball bearing.

Therefore, in such an angular ball bearing for ball screw support, it is necessary to increase both the load capacity in the axial direction and high rigidity for maintaining machining accuracy in order to increase the rolling fatigue life.

Japanese Patent Application Laid-Open No. 2000-104742

However, if the bearing size is increased, the space is increased at the ball screw shaft end, and if the number of combinations is large, the ball screw unit The portion becomes a wide configuration. As a result, the required floor area of the machine tool is increased and the dimension in the height direction is increased. Therefore, there is a limit to the increase in the size of the bearing and the increase in the number of heat.

SUMMARY OF THE INVENTION It is an object of the present invention to provide an angular ball bearing capable of achieving both increased load capacity in the axial direction and high rigidity in a limited space.

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

(1) an outer ring having an inner raceway surface,

An inner ring having an orbital surface on its outer circumferential surface,

A plurality of balls disposed between the raceway surfaces of the outer ring and the inner ring,

The ball is kept to be freely rotatable,

And an angular contact ball bearing

D1 > D2 where D1 is the outer diameter of the inner wheel counterbore formed in the outer peripheral surface of the inner ring on the rear side, and D2 is the outer diameter of the convexly formed inner wheel groove shoulder on the front side,

D3 > D4 where D3 is the inner diameter of the outer ring counterbore formed on the front surface side of the inner peripheral surface of the outer ring, and D4 is the inner diameter of the outer ring groove shoulder portion formed on the back surface side,

The contact angle alpha of the ball is 45 DEG ≤ 65 DEG,

Ai is defined as 0.35 < / = Ai ≤ 0.50 where Ai is the radial height of the inner ring groove shoulder portion divided by the diameter of the ball,

And Ae denotes a value obtained by dividing the radial height of the outer ring groove shoulder by the diameter of the ball, 0.35? Ae? 0.50,

The retainer includes a ring portion having a substantially annular shape and a plurality of pillars protruding in the axial direction at predetermined intervals from a front side or back side of the ring portion, A crown-type retainer having a pocket portion,

In the retainer, a reinforcement material is added,

Wherein X is a pitch circle diameter of the balls and? Rmax = X 2 x 5.0 x 10 -6 + X x 1.8 x 10 -3 +0.14, and ΔRmin = X 2 x 5.5 x 10 -6 + X x 1.5 x 10 - 3 +0.02, the radial motion amount? R of the retainer is? Rmin?? R?? Rmax,

And? T < DELTA Rmin, where DELTA t is the relative expansion of the retainer at 100 DEG C in the radial direction.

(2) The spherical center position of the pocket portion is shifted in the radial direction with respect to the radial center of the ring portion,

The angular ball bearing as set forth in (1), wherein a radial cross-sectional shape of the pocket portion is a cause of an arbitrary radius.

(3) The above-mentioned retainer is made of a polyamide resin,

The reinforcing material is glass fiber,

The angular ball bearing according to (1) or (2), wherein the ratio of the reinforcement material in the retainer is 5 to 30 wt%.

The inner diameter D3 of the outer ring counterbore is larger than the inner diameter D4 of the outer ring groove shoulder (D3 > D4), and the inner diameter of the outer ring groove bore is larger than the inner diameter D2 of the outer ring groove shoulder , And the contact angle? Of the ball satisfies 45???? 65. Therefore, by increasing the contact angle, the load capacity of the axial load of the bearing increases, and it can be used as a larger preload. As a result, it is possible to improve the rigidity of the bearing, and furthermore, the balls.

If Ai is obtained by dividing the radial height of the inner ring groove shoulder portion by the diameter of the ball, Ai is 0.35? Ai? 0.50, and Ae is the radial height of the outer ring groove shoulder portion divided by the diameter of the ball. It is possible to facilitate the grinding process of the inner and outer ring groove shoulder portions while preventing the load capacity of the axial load of the bearing from being insufficient.

Also, the pitch circle diameter of the ball to X and, ΔRmax = X 2 × 5.0 × 10 -6 to + X × 1.8 × 10 -3 +0.14 and, ΔRmin = X 2 × 5.5 × 10 -6 + X × 1.5 × 10 -3 +0.02, the radial movement amount? R of the retainer is set so as to satisfy? Rmin?? R?? Rmax. Therefore, it is possible to prevent the radial movement amount of the retainer from becoming larger than the radial clearance between the retainer and the inner and outer rings, and to prevent the contact between the retainer and the inner or outer ring.

When? T <? Rmin, the relative amount of expansion of the retainer in the radial direction at 100 占 폚 is? T. Therefore, even at the upper limit of the bearing service temperature, the retainer and the ball can be used without interfering with each other.

1 is a sectional view of an angular ball bearing according to an embodiment of the present invention.
Fig. 2 is a cross-sectional view of the angular ball bearings of Fig. 1 in combination.
3 is a side view of the retainer.
4 is a view of the retainer viewed from one side in the axial direction.
5 is a view of the retainer viewed from the other side in the axial direction.
Fig. 6 is a view as seen from a cross-sectional view taken along the line VI-VI in Fig.
7 is a cross-sectional view of an angular ball bearing according to a modification.
Fig. 8 is a view of the retainer related to the modified example viewed from one side in the axial direction. Fig.
9 (a) is a side view of the retainer, and FIG. 9 (b) is a view as seen from arrows IX in FIG.
10 is a graph showing the relationship between the pitch circle diameter of the ball, the radial motion amount of the holder and the radial direction relative expansion amount.
11 is a graph showing the relationship between the glass fiber content and the linear expansion coefficient of polyamide 66. Fig.

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

1, an angular ball bearing 1 according to the present embodiment includes an outer ring 10 having an inner raceway surface 11 on its inner circumferential surface, an inner ring 20 having a raceway surface 21 on its outer circumferential surface, A plurality of balls 3 disposed between the raceway surfaces 11 and 21 of the outer ring 10 and the inner ring 20 and a retainer 30 that keeps the ball 3 freely rotatable, Respectively.

The inner circumferential surface of the outer ring 10 has an outer ring groove shoulder portion 12 convexed on the rear side (load side, left side in FIG. 1) than the raceway surface 11 and a front side And the outer ring counterbore 13 formed on the right side in Fig. 1).

The outer circumferential surface of the inner ring 20 has a convex inner ring groove shoulder portion 22 that is convex on the front side (load side, right side in FIG. 1) than the raceway surface 21, (Left side in Fig. 1).

D1 <D2, the inner diameter of the outer ring counterbore 13 is D3, and the inner diameter of the inner ring groove shoulder portion 22 is D2. When the outer diameter of the inner ring groove bore 23 is D1 and the outer diameter of the inner ring groove shoulder portion 22 is D2, When the inner diameter of the shoulder portion 12 is D4, D3> D4. 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 in this way, it is preferable to set the contact angle [alpha] It is possible. More specifically, by setting the outer diameter D2 and the inner diameter D4 as described above, it is possible to set the contact angle alpha to about 45 DEG &amp;le; 65 DEG, and to take into account the deviation of the contact angle alpha Can be set to about 50 DEG &amp;le; alpha &amp;le; 60 DEG, and the contact angle alpha can be increased.

If Ai is the height (Hi) in the radial direction of the inner ring groove shoulder 22 divided by the diameter Dw of the ball 3, then (Ai = Hi / Dw) and 0.35? (Ae = He / Dw) and 0.35 ≤ Ae ≤ 0.50, where Ae is the height (He) in the radial direction of the outer race groove shoulder portion 12 divided by the diameter (Dw) of the ball do.

In the case of 0.35 &gt; Ai or 0.35 &gt; Ae, the radial height (Hi, He) of the inner ring groove shoulder portion 22 or outer ring groove shoulder portion 12 is excessively small with respect to the diameter Dw of the ball 3 The contact angle alpha becomes less than 45 DEG and the load capacity of the bearing in the axial direction becomes insufficient. When 0.50 &lt; Ai or 0.50 &lt; Ae, the raceway surfaces 11 and 21 of the outer ring 10 and the inner ring 20 are formed with the pitch circle diameter X of the ball 3 being emptied , The outer ring groove shoulder portion 12 and the inner ring groove shoulder portion 22 are difficult to grind.

A tapered outer ring bevel 14 is formed at the rear end side of the outer ring groove shoulder portion 12 toward the radially outward side toward the rear side. At the front side end portion, a tapered inner ring chamfer 24 is formed facing the radially inward side toward the front side. The radial widths of the outer ring bevel 14 and the inner ring chamfer 24 are larger than half of the radial height He and Hi of the outer ring groove shoulder portion 12 and the inner wheel groove shoulder portion 22, .

Such an angular ball bearing 1 can be used in parallel combination as shown in Fig. Since the outer ring groove shoulder portion 12 and the inner ring groove shoulder portion 22 are formed in the vicinity of the pitch circle diameter X of the ball 3 in the angular ball bearing 1 of the present embodiment, The inner ring 20 of one angular ball bearing 1 and the outer ring 10 of the other angular ball bearing 1 interfere with each other and a problem occurs during the rotation of the bearing unless the inner ring 14 and the inner ring chamfer 24 are formed. . When oil lubrication is used, oil does not pass between the respective angular ball bearings 1 unless the outer ring bevel 14 and the inner ring chamfer 24 are formed. As a result, oil dropping becomes worse, This leads to a temperature rise due to a large amount of oil remaining in the bearing. By forming the outer ring bevel 14 and the inner ring bevel 24 in this way, it is possible to prevent interference between the inner ring 20 and the outer ring 10 and to improve the oil dropping performance. The outer ring bevel 14 and the inner ring bevel 24 are not necessarily formed in both directions, and at least one of them may be formed.

Next, with reference to Figs. 3 to 6, the structure of the retainer 30 will be described in detail. The retainer 30 is a ball guide type plastic retainer made of a synthetic resin, and the base resin constituting the retainer 30 is a polyamide resin. The type of the polyamide resin is not limited, and other synthetic resins such as polyacetal resin, polyether ether ketone, and polyimide may be used in addition to polyamide. In the base resin, glass fibers, carbon fibers, aramid fibers and the like are added as reinforcing materials. The retainer 30 is manufactured by injection molding or cutting.

The retainer 30 has a substantially annular ring portion 31 (see Fig. 1) arranged coaxially with the inner ring 20 and the outer ring 10 and a ring portion 31 And a plurality of pocket portions 33 formed between the adjacent column portions 32. The columnar portion 32 has a plurality of columnar portions 32 protruding in the direction of the columnar portion 32,

Here, in the angular ball bearing 1 of the present embodiment, the radial height (He, Hi) of the outer ring groove shoulder portion 12 and the inner ring groove shoulder portion 22 is set to be large Therefore, the space inside the bearing is reduced. Therefore, when the retainer 30 disposed in the bearing inner space is a tubular retainer (one-side ring structure), the ring portion 31 is disposed between the outer ring counterbore 13 and the inner ring groove shoulder portion 22 And the structure in which the column portion 32 is disposed between the raceway surfaces 11 and 21 of the outer ring 10 and the inner ring 20 and the ring portion 31 is connected to the radially outer end portion of the column portion 32 do. That is, the spherical center position of the pocket portion 33 is shifted radially inward with respect to the radial center of the ring portion 31. In addition, the cross-sectional shape in the radial direction of the pocket portion 33 is a circle having an arbitrary radius r.

6, both side surfaces in the circumferential direction of the column portion 32 forming the pocket portion 33 and the side surface of the ring portion 31 on the back surface side (on the column portion 32 side) 3 and a similar spherical surface. Here, the tip end of the column portion 32 is formed with a cutout portion 34 having a substantially V-shape in cross section in the middle in the circumferential direction, and is divided into bifurcations. As a result, when the retainer 30 is manufactured by injection molding, the edge portion 35 of the column portion 32 on the side of the pocket portion 33, due to unreasonable removal of the mold component forming the pocket portion 33, It is possible to prevent breakage of the battery.

The spherical center position of the pocket portion 33 is not limited to the configuration shifted radially inward with respect to the radial center of the ring portion 31. As shown in Figs. 7 and 8, the radially outwardly displaced structure Lt; / RTI &gt; That is, the ring portion 31 is disposed between the outer ring groove shoulder portion 12 and the inner wheel counterbore 23, and the column portion 32 (32) is provided between the raceway surfaces 11, 21 of the outer ring 10 and the inner ring 20 And the ring portion 31 is connected to the radially inner end portion of the column portion 32. In this case, Even in this case, the distal end of the columnar section 32 is formed with the notch 34 in the middle in the circumferential direction and is divided into two branches. Therefore, 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 unreasonable removal of the mold component forming the column portion 33. [

The ratio of the reinforcement material added to the synthetic resin of the material for the retainer 30 is preferably 5 to 30 weight percent. If the ratio of the reinforcement material in the synthetic resin component exceeds 30 weight percent, the flexibility of the retainer 30 deteriorates, and therefore, the excessive release of the mold from the pocket portion 33 at the time of molding the retainer 30 The corner portion 35 of the column portion 32 is broken when the ball 3 is press-fitted into the pocket portion 33 when assembling the bearing. Since the thermal expansion of the retainer 30 depends on the linear expansion coefficient of the resin material as the base material, if the ratio of the reinforcement material is less than 5 weight percent, the thermal expansion of the retainer 30 during rotation And the pocket 3 of the ball 3 and the pocket portion 33 of the retainer 30 are in contact with each other to cause a problem such as seizure. 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 problem can be prevented.

In order to maintain a large contact angle? As in the angular ball bearing 1 of the present embodiment, the radial height He and Hi of the outer ring groove shoulder portion 12 and the inner ring groove shoulder portion 22, respectively, The radial direction space between the outer ring 10 and the inner ring 20 is narrowed and the position between the outer ring 10 and the inner ring 20 is located in the space between the outer ring 10 and the inner ring 20 The thickness of the ring portion 31 of the retainer 30 in the radial direction can not be made thick with respect to the standard bearing. Particularly, in the case of the tubular holder, since the ring portion 31 does not exist only on one side in the axial direction of the retainer 30, the strength of the ring portion 31 may be lowered due to the insufficient thickness.

When the radial thickness of the ring portion 31 is increased to the vicinity of the outer ring 10 and the inner ring 20 in order to compensate for the decrease in the strength of the ring portion 31, 30, and the inner ring 20 and the outer ring 10 ", so that the ring portion 31 and the outer ring 10 or the inner ring 20 are in contact with each other, irrespective of the ball guide system. Particularly, in the case of the ball guide system, it is not assumed that the retainer 30 comes in contact with the outer ring 10 and the inner ring 20, and the surface roughness and the shape of the inner peripheral surface of the outer ring 10 and the outer peripheral surface of the inner ring 20 There is a fear that the retainer 30 may be worn or damaged by contact with the part because the accuracy is not so good.

The radial movement of the retainer 30 defined by the radial clearance in accordance with the radial clearance between the retainer 30 and the outer ring 10 and the inner ring 20 while properly maintaining the thickness of the ring portion 31 It is necessary to set the upper limit value DELTA Rmax of the amount DELTA R to a specific value or less.

9, the radial movement amount? R of the ball guide type retainer 30 is set such that the ball 3 and the pocket portion 33 in the radial direction inside of the pocket portion 33, Of the ball 3 and the radial clearance? Re of the pocket portion 33 at the radially outer side of the ball 3 and the radial clearance? Ri of the pocket portion 33 (? R = min (? Re,? Ri)}. However, from the deviation of the machining accuracy of the retainer 30, the radial motion amount? R is scattered in a certain range. Particularly, in the case of an injection-molded resin holder, the dimensional error at the time of molding is added in addition to the dimensional accuracy of the molding die, and the degree of deviation tends to increase.

As described above, in the angular ball bearing 1 of the present embodiment, unlike a general bearing, since the space between the inner ring 20 and the outer ring 10 on the front surface side or the back surface side is narrow, The shape of the retainer 30 has a special structure of a one-side ring structure. Therefore, in order to secure the strength of the ring portion 31, the thickness of the ring portion 31 in the radial direction is made as large as possible, and the diameter of the ring portion 31 in the radial direction of the retainer 30 is set so as not to interfere with the inner ring 20 or the outer ring 10 It is necessary to determine the gap. It is also possible to prevent the deterioration of the retainer 30 caused by the excessive movement of the retainer 30 in the radial direction of the retainer 30 The radial clearance is determined. Therefore, when the upper limit value? Rmax, which is the maximum value of the radial motion amount? R that can prevent interference between the retainer 30 and the outer ring 10 or the inner ring 20, is set, by, ΔRmax = X 2 × 5.0 × 10 -6 + X × 1.8 × 10 -3 +0.14 ( stage, X is a pitch circle diameter of the ball (3)) is a. As described above, by setting the radial direction motion amount DELTA R of the retainer 30 to satisfy DELTA R &amp;le; DELTA Rmax, the radial direction motion amount DELTA R of the retainer 30 is reduced 10 or the inner ring 20 and prevents the contact between the retainer 30 and the outer ring 10 or the inner ring 20. [

In addition, by a number of analysis and experimental verification, the diameter the lower limit value (ΔRmin) of forward motion amount (ΔR) is, ΔRmin = X 2 × 5.5 × 10 -6 + X × 1.5 × 10 -3 is set to be +0.02. If DELTA Rmin = 0, the retainer 30 and the ball 3 hang each other. Therefore, without causing the retainer 30 and the ball 3 to interlock with each other, the ball 3 can be prevented from being deformed without causing any abnormal heat generation, uneven torque, or excessive torque during the rotation of the bearing, DELTA Rmin is set as the minimum radial clearance required to exhibit performance capable of maintaining and guiding to freely rotate.

It is also preferable that the retainer 30 is made of a polyamide resin, the reinforcing material is made of glass fiber, and the added amount of the glass fiber is set in the range of 5 to 30 weight percent. 10, even at 100 占 폚 at which the bearing temperature becomes the maximum temperature to be used within the range of the ball pitch circle diameter? 34 mm to? 93 mm, "the radial motion amount of the retainer 30 Of the retainer 30 becomes equal to the lower limit value DELTA Rmin of the retainer 30 in the radial direction relative expansion amount DELTA t of the retainer 30 and the problem caused by the support of the ball 3 and the pocket portion 33 of the retainer 30 Wear on the pocket, breakage of the retainer, seizure, etc.) can be prevented. The relative expansion amount? T in the radial direction of the retainer 30 is defined as the relative expansion amount? Of the retainer 30 with respect to the outer ring 10, the inner ring 20 and the ball 3 , And is defined as a radius gap.

In Fig. 10, as the amount of the glass fiber added increases, the relative expansion amount? T in the radial direction of the holder 30 decreases. This is due to the property of the polyamide that the coefficient of linear expansion becomes smaller as the proportion of the glass fiber in the component increases.

In the present embodiment, the amount of the glass fiber to be added is set to be in the range of 5 to 30 weight percent with the holder 30 made of polyamide resin, and the amount of the radial movement amount? R of the retainer 30 The relative lower limit value DELTA Rmin &gt; the radial direction relative expansion amount DELTA t of the retainer 30 is satisfied. However, in the case where the material satisfying the relationship is satisfied, polyether ether ketone, polyphenylene sulfide , Polyimide, or the like may be used. As the reinforcing material, a synthetic resin to which an appropriate amount of carbon fiber or aramid fiber is added may be used.

Next, the lower limit of the glass fiber content in the polyamide 66 when the polyamide 66 is used as the material of the holder 30 and the glass fiber is added as the reinforcing material is shown using the examples. Fig. 11 shows the relationship between the glass fiber content and the coefficient of linear expansion of polyamide 66. Fig. As described above, the polyamide 66 has such a property that the coefficient of linear expansion becomes small as the content of the glass fibers in the component increases.

(Example 1)

In the case of the angular ball bearing 1 having the bearing inner diameter d of 30 mm, the bearing outer diameter D 62 mm and the ball pitch circle diameter W 47 mm,? Rmax? 0.24 mm and? Rmin? 0.10 mm, The radial motion amount? R (? R = min (? Re,? Ri)} of the retainer 30 is set to 0.10 mm?? R? 0.24 mm.

If the radial direction motion amount DELTA R exceeds the upper limit value of 0.24 mm, there is a problem that the radial direction motion amount DELTA R of the retainer 30 becomes large and the retainer 30 and the inner and outer rings come into contact with each other. If the thickness of the ring portion 31 of the retainer 30 is made thinner, it is difficult to contact, but the strength of the ring portion 31 of the retainer 30 is lowered, and there is a risk of breakage during use.

In the application where the angular ball bearing 1 of the present invention is used, such as a machine tool or a motor-driven injection molding machine, the upper limit of the bearing temperature is set at 100 占 폚. When the room temperature is 20 占 폚, . Table 1 shows the relationship between the relative expansion amount? T in the radial direction of the retainer 30 and the glass fiber content at a use temperature of 100 占 폚.

Figure 112016082829594-pct00001

From Table 1 it can be seen that the glass fiber content is 5 weight percent or more and the lower limit value? Rmin of the radial direction movement amount? R of the retainer 30> the radial direction relative expansion amount? And that the holder 30 and the ball 3 can be used without interfering with each other even at 100 占 폚 which is the upper limit of the bearing use temperature. Therefore, in order to increase the contact angle? As in the case of the angular ball bearing 1, the outer ring groove shoulder portion 12 and the inner ring groove shoulder portion 22 are increased to the vicinity of the pitch circle diameter X of the ball 3 In consideration of the strength of the retainer 30, the addition amount ratio of the reinforcement material can be an indispensable constitution.

(Example 2)

? Rmax? 0.36 mm and? Rmin? 0.21 mm in the bearing inner diameter (d)? 60 mm, the bearing outer diameter (D)? 120 mm and the ball pitch circle diameter (W)? 93 mm, The radial movement amount? R of the holder 30 is set to 0.21 mm?? R? 0.36 mm. Table 2 shows the relationship between the relative expansion amount? T in the radial direction of the holder 30 at a service temperature of 100 占 폚 and the glass fiber content ratio in the same manner as in Example 1. Fig.

Figure 112016082829594-pct00002

Table 2 shows that the glass fiber content is 5 weight percent or more and the lower limit value DELTA Rmin of the radial direction movement amount DELTA R of the retainer 30 is smaller than the lower limit value DELTA Rmin in the radial direction relative expansion amount DELTA t of the retainer 30 Thus, it can be seen that the retainer 30 and the ball 3 can be used without being stuck to each other even at 100 캜 which is the upper limit of the bearing use temperature.

As described above, it has become clear that the lower limit of the content of reinforcing fibers in the synthetic resin of the material of the retainer 30 is preferably 5 weight percent.

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

The present application is based on Japanese Patent Application No. 2014-037087 filed on February 27, 2014, the content of which is incorporated herein by reference.

1: Angular contact ball bearing
3: Ball
10: Outer ring
11: raceway surface
12: outer shoulder groove shoulder portion
13: Paddle counterbore
14: Chamfer of the paddle
20: Inner ring
21: Orbital plane
22: inner ring groove shoulder portion
23: inner ring counter bore
24: Chamfer of inner ring
30: retainer
31: Rings
32:
33: pocket portion
34:
35:

Claims (3)

An outer ring having an inner raceway surface,
An inner ring having an orbital surface on its outer circumferential surface,
A plurality of balls disposed between the raceway surfaces of the outer ring and the inner ring,
The balls are held in a freely rotatable manner, and a ball guide system,
And an angular contact ball bearing
D1 &gt; D2 where D1 is the outer diameter of the inner wheel counterbore formed in the outer peripheral surface of the inner ring on the rear side, and D2 is the outer diameter of the convexly formed inner wheel groove shoulder on the front side,
D3 &gt; D4 where D3 is the inner diameter of the outer ring counterbore formed on the front surface side of the inner peripheral surface of the outer ring, and D4 is the inner diameter of the outer ring groove shoulder portion formed on the back surface side,
The contact angle alpha of the ball is 45 DEG &amp;le; 65 DEG,
Ai is defined as 0.35 &lt; / = Ai &amp;le; 0.50 where Ai is the radial height of the inner ring groove shoulder portion divided by the diameter of the ball,
And Ae denotes a value obtained by dividing the radial height of the outer ring groove shoulder by the diameter of the ball, 0.35? Ae? 0.50,
The retainer includes an annular ring portion and a plurality of pillar portions protruding in the axial direction at predetermined intervals from a front side or a rear side of the ring portion and a plurality of pockets formed between the adjacent pillar portions, A crown-type retainer having a portion,
In the retainer, a reinforcement material is added,
Wherein X is a pitch circle diameter of the balls and? Rmax = X 2 x 5.0 x 10 -6 + X x 1.8 x 10 -3 +0.14, and ΔRmin = X 2 x 5.5 x 10 -6 + X x 1.5 x 10 - 3 +0.02, the radial motion amount? R of the retainer is? Rmin?? R?? Rmax,
DELTA t &lt; DELTA Rmin, where DELTA t is the relative expansion of the retainer at 100 DEG C in the radial direction,
A notch portion having a V-shaped cross section is formed at the tip of the column portion,
The pitch circle diameter X of the balls is 34 mm or more and 93 mm or less,
Wherein the retainer is made of a polyamide resin,
The reinforcing material is glass fiber,
Wherein the ratio of the reinforcement material in the retainer is 5 to 30 wt%. The method according to claim 1,
The spherical center position of the pocket portion is shifted in the radial direction with respect to the radial center of the ring portion,
Wherein the radial cross-sectional shape of the pocket portion is a cause of an arbitrary radius. delete
KR1020167023382A 2014-02-27 2014-07-17 Angular ball bearing KR101988706B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JPJP-P-2014-037087 2014-02-27
JP2014037087 2014-02-27
PCT/JP2014/069096 WO2015129064A1 (en) 2014-02-27 2014-07-17 Angular ball bearing

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