WO2015146811A1 - アンギュラ玉軸受 - Google Patents
アンギュラ玉軸受 Download PDFInfo
- Publication number
- WO2015146811A1 WO2015146811A1 PCT/JP2015/058384 JP2015058384W WO2015146811A1 WO 2015146811 A1 WO2015146811 A1 WO 2015146811A1 JP 2015058384 W JP2015058384 W JP 2015058384W WO 2015146811 A1 WO2015146811 A1 WO 2015146811A1
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- WIPO (PCT)
- Prior art keywords
- radial
- cage
- ball
- ring
- inner ring
- Prior art date
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Classifications
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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
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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
- 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
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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
- F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
- F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
- F16C2240/70—Diameters; Radii
- F16C2240/80—Pitch circle diameters [PCD]
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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
- F16C2322/00—Apparatus used in shaping articles
- F16C2322/39—General build up of machine tools, e.g. spindles, slides, actuators
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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
- F16C33/412—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
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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
- F16C33/66—Special parts or details in view of lubrication
- F16C33/6637—Special parts or details in view of lubrication with liquid lubricant
- F16C33/6659—Details of supply of the liquid to the bearing, e.g. passages or nozzles
Definitions
- the present invention relates to an angular contact ball bearing.
- Ball screws that convert rotary motion into linear motion are used for machine tools such as NC lathes, milling machines, machining centers, multi-axis machines, and 5-axis machines, and linear feed mechanisms for beds and spindle heads.
- An angular ball bearing is employed as a bearing that rotatably supports the shaft end of the ball screw (for example, see Patent Document 1).
- These bearings have a bearing inner diameter of about 10 mm to about 100 mm depending on the size of the headstock of the machine tool used or the bed on which the workpiece is mounted.
- the bearing size can be increased or the number of combinations can be increased.
- the bearing size is increased, the space at the ball screw shaft end increases, and the number of combinations is increased. If the number is increased excessively, the ball screw unit portion becomes wide. As a result, the required floor area of the machine tool increases and the height dimension increases, so there is a limit to the increase in the size of the bearings and the number of rows.
- the present invention has been made in view of the above circumstances, and an object thereof is to provide an angular ball bearing capable of achieving both an increase in axial load capacity and high rigidity in a limited space.
- An angular contact ball bearing comprising: On the outer peripheral surface of the inner ring, an inner ring counterbore is recessed on the back side, and an inner ring groove shoulder is protruded on the front side, On the inner peripheral surface of the outer ring, an outer ring counter bore is recessed on the front side, and an outer ring groove shoulder is protruded on the back side,
- the contact angle ⁇ of the balls is 45 ° ⁇ ⁇ ⁇ 65 °, When Ai is obtained by dividing the radial height of the inner ring groove shoulder by the diameter of the ball, 0.35 ⁇ Ai ⁇ 0.50, When Ae is obtained by dividing the
- a pocket-shaped cage having The spherical center position of the pocket portion is shifted to one side in the radial direction from the radial intermediate position between the outermost diameter portion and the innermost diameter portion of the ring portion,
- the side surface viewed from the circumferential direction of the pillar portion forming the pocket portion is formed by cutting out a circular arc connecting one radial side surface and the other radial side surface of the ring portion, or a part of the circular arc.
- the side surface seen from the circumferential direction of the pillar portion forming the pocket portion is a first straight shape portion formed so as to extend in the axial direction by cutting out one end portion in the radial direction of the arc.
- the side surface seen from the circumferential direction of the pillar portion forming the pocket portion is a cutout portion of the arc connecting the first straight shape portion and the one radial side surface of the ring portion.
- 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 a larger preload. Can be used with load. As a result, the rigidity of the bearing and thus the ball screw system can be improved.
- Ai is obtained by dividing the radial height of the inner ring groove shoulder by the ball diameter, 0.35 ⁇ Ai ⁇ 0.50, and the radial height of the outer ring groove shoulder is divided by the ball diameter.
- FIG. 6 is a sectional view taken along the line VI-VI in FIG. 4.
- FIG. 5 is a cross-sectional view taken along the line VII-VII in FIG. 4.
- FIG. 23 is a sectional view taken along the line XXIII-XXIII in FIG.
- the angular ball bearing 1 of the present embodiment includes an outer ring 10 having a raceway surface 11 on an inner peripheral surface, an inner ring 20 having a raceway surface 21 on an outer peripheral surface, and raceway surfaces of the outer ring 10 and the inner ring 20. 11 and 21, a plurality of balls 3, and a retainer 30 that holds the balls 3 in a freely rolling manner and is a ball guide system.
- the outer peripheral surface of the outer ring 10 is protruded on the back side (load side; left side in FIG. 1) of the raceway surface 11 and the front side of the raceway surface 11 (on the anti-load side). 1 on the right side of the outer ring counter bore 13.
- the outer peripheral surface of the inner ring 20 is an inner ring groove shoulder 22 projecting on the front side (load side; right side in FIG. 1) from the raceway surface 21, and the back side (anti-load side, FIG. 1). And an inner ring counter bore 23 recessed in the middle left side.).
- a taper-shaped outer ring chamfer 14 is provided at the rear side end portion of the outer ring groove shoulder portion 12 so as to go radially outward toward the rear side.
- a taper-shaped inner ring chamfer 24 that is directed radially inward toward the front side is provided.
- the radial widths of the outer ring chamfer 14 and the inner ring chamfer 24 are set to a relatively large value that is larger than half of the radial heights He and Hi of the outer ring groove shoulder 12 and the inner ring groove shoulder 22.
- Such an angular ball bearing 1 can be used in parallel as shown in FIG. Since the angular ball bearing 1 of the present embodiment is provided with the outer ring groove shoulder 12 and the inner ring groove shoulder 22 up to the vicinity of the pitch circle diameter dm of the ball 3, the outer ring chamfer 14 and the inner ring chamfer 24 are not provided. 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, causing a problem during rotation of the bearing. In addition, when used in oil lubrication, if the outer ring chamfer 14 and the inner ring chamfer 24 are not provided, the oil does not pass between the angular ball bearings 1, and the oil is poorly lubricated.
- outer ring chamfer 14 and the inner ring chamfer 24 it is possible to prevent interference between the inner ring 20 and the outer ring 10 and to improve oil repellency.
- Both the outer ring chamfer 14 and the inner ring chamfer 24 do not necessarily need to be provided, and at least one may be provided.
- the cage 30 is a ball guide type plastic cage made of synthetic resin, and the base resin constituting the cage 30 is a polyamide resin.
- the kind of polyamide resin is not restrict
- glass fiber, carbon fiber, aramid fiber, or the like is added to the base resin as a reinforcing material.
- the cage 30 is manufactured by injection molding or cutting.
- the retainer 30 includes a substantially annular ring portion 31 (see FIG. 1) disposed coaxially with the inner ring 20 and the outer ring 10, and a plurality of protrusions protruding in the axial direction at a predetermined interval from the back side of the ring portion 31. It is a crown type retainer having a column portion 32 and a plurality of pocket portions 33 formed between adjacent column portions 32.
- the radial heights He and Hi of the outer ring groove shoulder portion 12 and the inner ring groove shoulder portion 22 are increased in order to realize a high load capability of the axial load.
- the bearing internal space is reduced. Therefore, when the cage 30 arranged in such a bearing internal space is a crown type cage (one-side ring structure), the ring portion 31 is arranged between the outer ring counter bore 13 and the inner ring groove shoulder portion 22, and the outer ring 10 and the raceway surfaces 11 and 21 of the inner ring 20, the column portion 32 is arranged, and the ring portion 31 is connected to the radially outer end of the column portion 32.
- the spherical center position of the pocket portion 33 is radially inward (one radial direction side) from the radial intermediate position M between the outermost diameter portion m1 and the innermost diameter portion m2 of the ring portion 31.
- the spherical center position of the pocket portion 33 is a position that coincides with the center Oi of the ball 3.
- the outermost diameter portion m1 of the ring portion 31 is the radially outer side surface 31b
- the innermost diameter portion m2 is the radially inner side surface of the inner convex portion 38.
- the spherical center position of the pocket portion 33 is shifted radially inward from the innermost diameter portion m ⁇ b> 2 of the ring portion 31.
- the side surface seen from the circumferential direction of the column part 32 which forms the pocket part 33 is the radial inner side surface (radial one side surface) 31a and the radial outer side surface (radial other side surface) of the ring part 31. )
- a part of the arc 33a connecting to 31b is cut away.
- the center of the arc 33a is indicated by P, and the radius is indicated by r.
- the side surface viewed from the circumferential direction of the column part 32 is a first straight formed so that the radially inner end (radial one side end) of the arc 33a is notched and extends in the axial direction.
- the shape part 33b is included.
- the 1st straight shape part 33b is arrange
- the first straight shape portion 33b overlaps the center Oi of the ball 3 (the spherical center of the pocket portion 33) in the axial direction.
- the side surface viewed from the circumferential direction of the column part 32 includes an end part of the arc 33a on the front side of the first straight shape part 33b and an end part on the back side of the radial inner side face 31a of the ring part 31. It includes a second straight shape portion 33c formed by cutting a portion to be tied. Therefore, the 2nd straight shape part 33c is made into the linear shape which goes to a radial direction outer side as it goes to the front side (ring part 31 side).
- the side surface of the pillar portion 32 viewed from the circumferential direction has a third straight shape portion 33e formed so that the radially outer end portion (radial other side end portion) of the arc 33a is notched and extends in the axial direction. including.
- the third straight shape portion 33e is formed on the same plane as the radially outer surface 31b of the ring portion 31, and is connected to the radially outer surface 31b without a step.
- the side surface of the pillar portion 32 viewed from the circumferential direction has a shape in which the third straight shape portion 33e, the arc 33a, the first straight shape portion 33b, and the second straight shape portion 33c are connected. It has become.
- the circumferential side surfaces of the column part 32 and the side surfaces on the back side (column part 32 side) of the ring part 31, which form the pocket part 33 are the balls 3 when viewed from the radial direction. It is formed in a similar spherical shape.
- the tip of the column part 32 is provided with a notch 34 having a substantially V-shaped cross section in the middle in the circumferential direction, and is divided into two.
- the ratio of the reinforcing material added to the synthetic resin of the cage 30 material is preferably 5 to 30 weight percent. If the proportion of the reinforcing material in the synthetic resin component exceeds 30% by weight, the flexibility of the cage 30 is reduced. Therefore, when the mold is forcibly removed from the pocket portion 33 when the cage 30 is molded, When the ball 3 is press-fitted into the pocket portion 33 during assembly, the corner portion 35 of the column portion 32 is damaged. Further, since the thermal expansion of the cage 30 depends on the linear expansion coefficient of the resin material that is the base material, if the proportion of the reinforcing material is less than 5 weight percent, the thermal expansion of the cage 30 during the rotation of the bearing causes the ball 3 to rotate.
- the pitch circle diameter dm expands, the ball 3 and the pocket portion 33 of the cage 30 stick against each other, causing problems such as seizure. Therefore, the above-mentioned problem can be prevented by setting the ratio of the reinforcing material in the synthetic resin component in the range of 5 to 30% by weight.
- resins such as polyamide, polyetheretherketone, polyphenylene sulfide, and polyimide are applied, and as the reinforcing material, glass fibers, carbon fibers, aramid fibers, and the like are applied.
- the cage 130 and the inner ring 120 or the outer ring 110 do not overlap in the radial direction. Therefore, even if the cage 130 exceeds the design value due to the inertia at the time of starting and stopping the rotation of the deep groove ball bearing 100, even if the cage 130 moves in the axial direction relative to the inner ring 120 or the outer ring 110, There is no interference with the inner ring 120 or the outer ring 110.
- the cage 30 and the inner ring 20 or the outer ring 10 overlap in the radial direction as in the angular ball bearing 1 of the present embodiment, the cage 30 exceeds the design value, and the inner ring 20 or the outer ring 10 Thus, the cage 30 and the inner ring 20 or the outer ring 10 may interfere with each other when moving relatively in the axial direction. If the side surface viewed from the circumferential direction of the pillar portion 32 has a shape that does not have the second straight shape portion 33c (see FIG. 7), the axial distance ⁇ S1 between the cage 30 and the inner ring 20 (see FIG. 1) is narrowed, and the possibility that the cage 30 and the inner ring 20 interfere with each other increases.
- the side surface viewed from the circumferential direction of the column portion 32 has the second straight shape portion 33c, so that the axial distance ⁇ S1 between the cage 30 and the inner ring 20 is increased. Therefore, the possibility that the cage 30 and the inner ring 20 interfere with each other can be reduced.
- the radial heights He and Hi of the outer ring groove shoulder 12 and the inner ring groove shoulder 22 are set to the pitch circle of the ball 3, respectively.
- the radial space between the outer ring 10 and the inner ring 20 is narrowed, and the radial thickness of the ring portion 31 of the cage 30 located in the space between the outer ring 10 and the inner ring 20 is larger than that of the standard bearing. Cannot be thick.
- the strength of the ring portion 31 may be reduced due to insufficient thickness.
- the material of the cage 30 is a synthetic resin such as polyamide resin, polyacetal resin, polyetheretherketone, polyimide, and the reinforcing fiber content in the base resin is 30 weight percent or less.
- the strength of the ring portion 31 of the cage 30 tends to be low, and when a radial impact load or vibration load is applied, the cage 30 bends in the radial direction.
- an example of the shape when the radial load F is applied to the cage 30 and is bent in the radial direction is schematically represented by a broken line in FIG. 9 and a one-dot chain line in FIG.
- the radial position of the cage 30 approaches the inner ring 20 side or the outer ring 10 side.
- the axial distance ⁇ S1 between the cage 30 and the inner ring 20 is reduced, and the possibility that the cage 30 and the inner ring 20 interfere with each other increases.
- the side surface viewed from the circumferential direction of the pillar portion 32 is a shape that does not have the second straight shape portion 33c, the axial distance ⁇ S1 between the cage 30 and the inner ring 20 becomes narrow, and the cage 30 And the inner ring 20 are likely to interfere with each other.
- the side surface viewed from the circumferential direction of the column portion 32 has the second straight shape portion 33c, so that the axial distance ⁇ S1 between the cage 30 and the inner ring 20 is increased. Therefore, the possibility that the cage 30 and the inner ring 20 interfere with each other can be reduced.
- the axial movement amount ⁇ A of the cage 30 is increased.
- the axial distance ⁇ S1 between the cage 30 and the inner ring 20 becomes narrow, and there is a high possibility that the cage 30 and the inner ring 20 interfere with each other.
- the side surface viewed from the circumferential direction of the pillar portion 32 is a shape that does not have the second straight shape portion 33c, the axial distance ⁇ S1 between the cage 30 and the inner ring 20 becomes narrow, and the cage 30 And the inner ring 20 are likely to interfere with each other.
- the axial distance between the cage 30 and the inner ring 20 is formed by forming the second straight shape portion 33c on the side surface viewed from the circumferential direction of the column portion 32.
- ⁇ S1 can be made wider, and the possibility that the cage 30 and the inner ring 20 interfere with each other can be reduced.
- the angular ball bearing 1 of the present embodiment is set so that the number of balls 3 (the number of balls Z) is increased in order to increase the axial load capacity.
- FIG. 11 shows two balls 3 arranged on a pitch circle having a diameter dm, the diameter of these balls 3 is Dw, the centers of these balls 3 are A and B, and a line segment AB.
- the intersection of the ball 3 and the surface of the ball 3 is C, D, the midpoint of the line segment AB is E, and the center of the pitch circle is O.
- the distance between the centers of the balls 3 that is the distance between the centers A and B of the adjacent balls 3 is T
- the distance between the balls that is the distance of the adjacent balls 3 is the distance of the line segment CD.
- Is L and the angle between line segment EO and line segment BO (angle between line segment EO and line segment AO) is ⁇ .
- the distance between the line segment AO and the line segment BO is (dm / 2)
- the ball center distance T is (dm ⁇ sin ⁇ )
- the ball distance L is (T ⁇ Dw)
- the angle ⁇ is (180 ° / Z).
- the angular ball bearing 1 is designed so as to satisfy 2.5 ⁇ 10 ⁇ 3 ⁇ L / ⁇ dm ⁇ 13 ⁇ 10 ⁇ 3 , that is, the number of balls Z is relatively large.
- the thickness in the circumferential direction of the column part 32 cannot be increased with respect to the standard bearing. Therefore, as the circumferential thickness of the pillar portion 32 becomes thinner, the thickness of the corner portion 35 becomes thinner. Therefore, as shown by an arrow A in FIG. 6, when the ball 3 and the corner portion 35 of the cage 30 hit each other, the corner portion 35 is likely to spread in the circumferential direction, and as a result, the axial movement amount ⁇ A of the cage. Becomes larger.
- the axial distance ⁇ S1 between the cage 30 and the inner ring 20 is reduced, and the possibility that the cage 30 and the inner ring 20 interfere with each other increases.
- the side surface viewed from the circumferential direction of the pillar portion 32 is a shape that does not have the second straight shape portion 33c, the axial distance ⁇ S1 between the cage 30 and the inner ring 20 becomes narrow, and the cage 30 And the inner ring 20 are likely to interfere with each other. Therefore, as in the angular ball bearing 1 of the present embodiment, the side surface viewed from the circumferential direction of the column portion 32 has the second straight shape portion 33c, so that the axial distance ⁇ S1 between the cage 30 and the inner ring 20 is increased. Therefore, the possibility that the cage 30 and the inner ring 20 interfere with each other can be reduced.
- the bearing is similar to the cage 30 of the present embodiment described above.
- the axial relative movement amount ⁇ A of the cage 30 increases.
- 33 d of radial direction inner edges which are the parts which guide the ball
- the radial distance between the radially inner edge 33 d of the pocket 33 and the ball 3 is the radial movement amount ⁇ R of the cage 30.
- the cage 30 and the ball 3 are in point contact, the cage 30 easily moves in the axial direction relative to the inner ring 20 or the outer ring 10 during the bearing rotation.
- the radial direction of the pocket portion 33 The location where the inner edge 33d is in point contact with the ball 3 also moves in the axial direction.
- the pocket portion 33 (column portion 32) moved in the axial direction is indicated by a one-dot chain line. Then, since the radial distance between the radially inner edge 33d of the pocket portion 33 and the ball 3 is smaller after the movement than before the movement in the axial direction, the radial movement amount ⁇ R of the cage 30 is reduced. Also, after movement (see the broken line in FIG.
- This phenomenon occurs every time the cage 30 moves relative to the inner ring 20 or the outer ring 10 in the axial direction (that is, from the neutral state where the ball center Oi and the spherical center position of the pocket portion 33 coincide during rotation).
- the cage 30 is relatively displaced to the left or right in the axial direction, the radial movement amount ⁇ R of the cage 30 is frequently changed in a direction in which the cage 30 becomes smaller.
- the ball is circular, the ball 3 cannot be stably guided, and the vibration of the cage 30 increases or the cage 30 and the ball 3 are stuck against each other. Problems such as early breakage of the vessel 30 occur.
- the first straight-shaped portion 33 b is provided on the side surface viewed from the circumferential direction of the column portion 32, as shown in FIG. 15, thereby guiding the ball 3 of the pocket portion 33.
- the first straight shape portion 33b and the ball 3 are configured to make line contact in an arc shape.
- Axial relative movement can be suppressed. Therefore, a change in the radial movement amount ⁇ R of the cage 30 can be prevented, and an increase in vibration during rotation of the bearing can be suppressed.
- problems such as cage noise and early breakage of the cage 30 can be suppressed.
- the radial movement amount ⁇ R of the cage 30 is designed by the relative shift of the position of the pitch circle of the pocket portion 33 of the cage 30 and the position of the pitch circle of the ball 3 in the axial direction. It varies from the above range, and it is difficult to accurately measure the ball circumscribed circle diameter and the ball inscribed circle diameter at the time of manufacturing the cage.
- the ball 3 is lightly applied with a measurement load and fixed with the ring portion 31 of the cage 30 down.
- the measurement load is given toward the inner side in the radial direction with respect to the ball 3
- the measured load is It is given toward the outer side of the ball 3 in the radial direction.
- the ball 3 in the pocket portion 33 approaches the ring portion 31 in the pocket portion 33 by gravity.
- the position of the pitch circle of the pocket portion 33 and the position of the pitch circle of the ball 3 are relatively shifted in the axial direction.
- the radial movement amount ⁇ R of the cage 30 becomes smaller after movement (see the broken line in FIG. 13) than before movement in the axial direction (see the solid line in FIG. 13). ⁇ R becomes smaller than the design range. In this case, it becomes difficult to accurately measure the ball circumscribed circle diameter and the ball inscribed circle diameter of the cage 30.
- the ball 3 is a portion of the first straight shape portion 33b by the measurement load as shown in FIG. It becomes easy to accurately measure the ball circumscribed circle diameter and the ball inscribed circle diameter without being caught and the ball 3 being displaced in the axial direction.
- the mold has an axial draw type structure, but when the mold forming the pocket portion 33 is released, the corner portion 35 of the column portion 32 (see FIG. 6). .) The vicinity is forcibly removed, and when removing the mold from the pocket portion 33, the cage cannot be released unless it is positioned and removed in the axial direction.
- the cage 130 has a substantially annular ring portion 131 and a shaft spaced from the ring portion 131 at a predetermined interval.
- the crown-shaped cage has a plurality of column portions 132 protruding in the direction and a plurality of pocket portions 133 formed between adjacent column portions 132.
- the pitch in the circumferential direction of the pocket portion 133 of the cage 130 is wide, and the gap between the pair of corner portions 135 of the column portion 132 is the same as that of this embodiment.
- the column portions 32 are spaced apart from each other between the pair of corner portions 35. Therefore, the concave portion 136 can be provided between the pair of corner portions 135 for the purpose of easily deforming the tip portion of the column portion 132 when the mold is not removed.
- the bottom surface 137 of the recess 136 can be a plane extending in the circumferential direction. Then, a pin for punching is provided on the bottom surface 137 of the recess 136, and the pin is pushed out in the axial direction with respect to the die of the pocket portion 133, so that it is possible to release the die without forcing.
- the circumferential width of the bottom plane of the notch 34 is desirably 0.2 mm or more in consideration of the processing limit of the V-shaped sharp portion at the tip of the die where the notch 34 is injection-molded.
- the mold parts that form the pocket portion 33 are forcibly removed.
- the pocket The mold parts forming the part cannot be forcibly removed.
- an inner convex portion 38 that protrudes radially inward is formed on the radially inner side surface 31 a (one radial side surface) of the ring portion 31.
- the inner convex portion 38 is formed as a catch between the cage 30 and the mold that forms the cage main body, so that the mold parts that form the pocket portion 33 can be forcibly removed. can do.
- the shape and position of the inner convex portion 38 are not particularly limited, and may be formed so as to protrude radially inward from the front side end portion of the radial inner side surface 31a of the ring portion 31 as shown in FIG. Absent.
- the inner convex portion 38 is provided in the vicinity of the center of the ring portion 31 except for the axial end portion. desirable. That is, from the viewpoint of avoiding contact between the inner ring 20 and the inner convex portion 38, the position of the inner convex portion 38 shown in FIG. 7 is more desirable than the position of the inner convex portion 38 shown in FIG.
- the holding force at the time of releasing can be increased, but contact between the inner ring 20 and the inner convex portion 38 occurs.
- the radial dimension of the inner convex portion 38 has a limit. Therefore, in such a case, as shown in FIG. 19, it is desirable to increase the holding force at the time of mold release by setting the number of the inner convex portions 38 to a plurality (two in FIG. 19).
- the inner convex portion 38 is not provided, and the outer convex portion 39 that protrudes radially outward may be formed on the radially outer side surface 31 b (the other radial side surface) of the ring portion 31. . Also in this case, the shape, position, number, and the like of the outer convex portions 39 are appropriately set.
- both the inner convex portion 38 and the outer convex portion 39 may be formed on the ring portion 31.
- the spherical center position of the pocket portion 33 is not limited to the configuration shifted radially inward from the radial intermediate position M between the outermost diameter portion m1 and the innermost diameter portion m2 of the ring portion 31, and FIG.
- a configuration shifted outward in the radial direction may be used. That is, the ring portion 31 is disposed between the outer ring groove shoulder 12 and the inner ring counter bore 23, 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 inner side in the radial direction of the column portion 32. It is good also as a structure where the ring part 31 connects to an edge part.
- the spherical center position of the pocket portion 33 is shifted radially outward from the outermost diameter portion m ⁇ b> 1 of the ring portion 31.
- the notch 34 is provided in the middle in the circumferential direction at the tip of the column 32 and is divided into two parts, the pocket 33 is formed when the retainer 30 is manufactured by injection molding. It is possible to prevent the corner portion 35 on the pocket portion 33 side of the column portion 32 from being damaged by forcibly removing the mold parts forming the.
- the side surface seen from the circumferential direction of the column part 32 which forms the pocket part 33 includes a radial outer side surface (radial one side surface) 31b and a radial inner side surface (radial other side surface) 31a of the ring part 31.
- a part of the connecting arc 33a is cut out.
- the center of the arc 33a is indicated by P, and the radius is indicated by r.
- the side surface viewed from the circumferential direction of the column portion 32 is a first straight formed so that the radially outer end portion (radial one side end portion) of the arc 33a is notched and extends in the axial direction.
- the shape part 33b is included.
- the first straight shape portion 33b is disposed on the front side (the anti-load side, left side in FIG. 23) from the center P of the arc 33a.
- the first straight shape portion 33b overlaps the center Oi of the ball 3 (the spherical center of the pocket portion 33) in the axial direction.
- the side surface seen from the circumferential direction of the column part 32 is the end of the arc 33a on the back side (load side; right side in FIG. 23) of the first straight shape part 33b and the radially outer side surface of the ring part 31. It includes a second straight shape portion 33c formed by cutting out a portion connecting the front end portion of 31b. Therefore, the 2nd straight shape part 33c is made into the linear shape which goes to a radial inside as it goes to the back side (ring part 31 side).
- the side surface of the pillar portion 32 viewed from the circumferential direction has a third straight shape portion 33e formed such that the radially inner end portion (radial other side end portion) of the arc 33a is cut out and extends in the axial direction. including.
- the third straight shape portion 33e is formed on the same plane as the radial inner side surface 31a of the ring portion 31, and is connected to the radial inner side surface 31a without a step.
- the side surface of the pillar portion 32 viewed from the circumferential direction has a shape in which the third straight shape portion 33e, the arc 33a, the first straight shape portion 33b, and the second straight shape portion 33c are connected. It has become.
- An inner convex portion 38 that protrudes radially inward is formed on the radially inner side surface 31 a (the other radial side surface) of the ring portion 31.
- the inner convex portion 38 is formed as a catch between the cage 30 and the mold that forms the cage main body, so that the mold parts that form the pocket portion 33 can be forcibly removed. can do.
- an outer convex portion 39 protruding radially outward may be formed on the radially outer surface 31b (one radial side surface) of the ring portion 31.
- Example 1 In the angular ball bearing 1 of this example, the inner diameter is ⁇ 15 mm, the contact angle ⁇ is 50 °, and the value of Ai (the radial height Hi of the inner ring groove shoulder 22 is divided by the diameter Dw of the ball 3) is 0. .38, Ae (the radial height He of the outer ring groove shoulder 12 divided by the diameter Dw of the ball 3) was set to 0.38.
- the cage 30 has the shape shown in FIG. 18, and the material thereof is a polyamide resin.
- the inner diameter is ⁇ 60 mm
- the contact angle ⁇ is 60 °
- Ai the radial height Hi of the inner ring groove shoulder 22 is divided by the diameter Dw of the ball 3
- Ae the radial height He of the outer ring groove shoulder 12 divided by the diameter Dw of the ball 3 was set to 0.47.
- the cage 30 has the shape shown in FIG. 1, and the material thereof is a material in which the base resin is polyacetal resin and carbon fiber is added as a reinforcing material by 10 weight percent.
- Example 3 In the angular ball bearing 1 of the present embodiment, the inner diameter is ⁇ 40 mm, the contact angle ⁇ is 55 °, and the value of Ai (the radial height Hi of the inner ring groove shoulder 22 is divided by the diameter Dw of the ball 3) is 0. .43, Ae (the radial height He of the outer ring groove shoulder 12 divided by the diameter Dw of the ball 3) was set to 0.43.
- the cage 30 has the shape shown in FIG. 20, and the material thereof is a base resin made of polyamide resin, and 20 weight percent of glass fiber is added as a reinforcing material.
- Example 4 In the angular ball bearing 1 of the present embodiment, the inner diameter is ⁇ 40 mm, the contact angle ⁇ is 55 °, and the value of Ai (the radial height Hi of the inner ring groove shoulder 22 is divided by the diameter Dw of the ball 3) is 0. .43, Ae (the radial height He of the outer ring groove shoulder 12 divided by the diameter Dw of the ball 3) was set to 0.43.
- the cage 30 has the shape shown in FIG. 19, and the material thereof is a base resin made of polyamide resin and glass fiber added as a reinforcing material by 20 weight percent.
- the outer shape of the side surface viewed from the circumferential direction of the column portion 32 is not limited to a shape in which a part of the arc 33a connecting the one radial side surface and the other radial side surface of the ring portion 31 is cut away. That is, the side surface viewed from the circumferential direction of the column portion 32 does not necessarily have the first to third straight shape portions 33a, 33b, and 33d, and may be an arc 33a having a radius r.
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Abstract
Description
(1) 内周面に軌道面を有する外輪と、
外周面に軌道面を有する内輪と、
前記外輪及び前記内輪の軌道面間に配置された複数の玉と、
前記玉を転動自在に保持し、玉案内方式である保持器と、
を備えるアンギュラ玉軸受であって、
前記内輪の外周面には、背面側に内輪カウンターボアが凹設され、正面側に内輪溝肩部が凸設され、
前記外輪の内周面には、正面側に外輪カウンターボアが凹設され、背面側に外輪溝肩部が凸設され、
前記玉の接触角αは、45°≦α≦65°であり、
前記内輪溝肩部の径方向高さを前記玉の直径で除したものをAiとすると、0.35≦Ai≦0.50であり、
前記外輪溝肩部の径方向高さを前記玉の直径で除したものをAeとすると、0.35≦Ae≦0.50であり、
前記保持器は、略円環状のリング部と、前記リング部の正面側又は背面側から、所定間隔で軸方向に突出した複数の柱部と、隣り合う前記柱部の間に形成された複数のポケット部と、を有する冠型保持器であり、
前記ポケット部の球面中心位置は、前記リング部の最外径部と最内径部との径方向中間位置よりも、径方向一方側にずれており、
前記ポケット部を形成する前記柱部の周方向から見た側面は、前記リング部の径方向一方側面と径方向他方側面を結ぶ円弧、又は前記円弧の一部が切り欠かれてなるものであり、
前記リング部の径方向一方側面及び径方向他方側面のうち、少なくとも一方には、径方向に突出する凸部が少なくとも一つ形成される
ことを特徴とするアンギュラ玉軸受。
(2) 前記ポケット部を形成する前記柱部の周方向から見た側面は、前記円弧の径方向一方側端部が切り欠かれて軸方向に延びるように形成された第1ストレート形状部を含む
ことを特徴とする(1)に記載のアンギュラ玉軸受。
(3) 前記ポケット部を形成する前記柱部の周方向から見た側面は、前記円弧の、前記第1ストレート形状部と、前記リング部の前記径方向一方側面と、を結ぶ部分が切り欠かれて形成された第2ストレート形状部を含む
ことを特徴とする(2)に記載のアンギュラ玉軸受。
(4) 隣り合う前記玉同士の距離Lと、玉ピッチ円直径dmに円周率πを乗じた玉ピッチ円周長さπdmと、の関係は、2.5×10-3≦L/πdm≦13×10-3を満たす
ことを特徴とする(1)~(3)の何れか1つに記載のアンギュラ玉軸受。
また、内輪溝肩部の径方向高さを玉の直径で除したものをAiとすると0.35≦Ai≦0.50であり、外輪溝肩部の径方向高さを玉の直径で除したものをAeとすると0.35≦Ae≦0.50であるので、軸受の軸方向荷重の負荷能力が不足することを防止しつつ、内外輪溝肩部の研削加工を容易とすることが可能である。
また、リング部の径方向一方側及び径方向他方側面のうち、少なくとも一方には、径方向に突出する凸部が少なくとも一つ形成されるので、保持器を射出成形で製造する場合、ポケット部を形成する金型部品の無理抜きを可能とすることができる。
本実施例のアンギュラ玉軸受1においては、内径をΦ15mm、接触角αを50°、Ai(内輪溝肩部22の径方向高さHiを玉3の直径Dwで除したもの)の値を0.38、Ae(外輪溝肩部12の径方向高さHeを玉3の直径Dwで除したもの)の値を0.38に設定した。保持器30は図18に示した形状を有しており、その材質はポリアミド樹脂である。玉間距離Lと、玉ピッチ円直径dmに円周率πを乗じた玉3ピッチ円周長さπdmと、の関係は、L/πdm=12×10-3を満たす。
本実施例のアンギュラ玉軸受1においては、内径をΦ60mm、接触角αを60°、Ai(内輪溝肩部22の径方向高さHiを玉3の直径Dwで除したもの)の値を0.47、Ae(外輪溝肩部12の径方向高さHeを玉3の直径Dwで除したもの)の値を0.47に設定した。保持器30は図1に示した形状を有しており、その材質は、ベース樹脂がポリアセタール樹脂であり、強化材としてカーボン繊維を10重量パーセント添加したものである。玉間距離Lと、玉ピッチ円直径dmに円周率πを乗じた玉3ピッチ円周長さπdmと、の関係は、L/πdm=2.3×10-3を満たす。
本実施例のアンギュラ玉軸受1においては、内径をΦ40mm、接触角αを55°、Ai(内輪溝肩部22の径方向高さHiを玉3の直径Dwで除したもの)の値を0.43、Ae(外輪溝肩部12の径方向高さHeを玉3の直径Dwで除したもの)の値を0.43に設定した。保持器30は図20に示した形状を有しており、その材質は、ベース樹脂がポリアミド樹脂であり、強化材としてガラス繊維を20重量パーセント添加したものである。玉間距離Lと、玉ピッチ円直径dmに円周率πを乗じた玉3ピッチ円周長さπdmと、の関係は、L/πdm=7.0×10-3を満たす。
本実施例のアンギュラ玉軸受1においては、内径をΦ40mm、接触角αを55°、Ai(内輪溝肩部22の径方向高さHiを玉3の直径Dwで除したもの)の値を0.43、Ae(外輪溝肩部12の径方向高さHeを玉3の直径Dwで除したもの)の値を0.43に設定した。保持器30は図19に示した形状を有しており、その材質は、ベース樹脂がポリアミド樹脂であり、強化材としてガラス繊維を20重量パーセント添加したものである。玉間距離Lと、玉ピッチ円直径dmに円周率πを乗じた玉3ピッチ円周長さπdmと、の関係は、L/πdm=7.0×10-3を満たす。
3 玉
10 外輪
11 軌道面
12 外輪溝肩部
13 外輪カウンターボア
14 外輪面取り
20 内輪
21 軌道面
22 内輪溝肩部
23 内輪カウンターボア
24 内輪面取り
30 保持器
31 リング部
31a 径方向内側面(径方向一方側面、径方向他方側面)
31b 径方向外側面(径方向他方側面、径方向一方側面)
32 柱部
33 ポケット部
33a 円弧
33b 第1ストレート形状部
33c 第2ストレート形状部
33d 径方向内側縁部
33e 第3ストレート形状部
34 切欠部
35 角部
38 内側凸部(凸部)
39 外側凸部(凸部)
Oi 玉中心(ポケット部球面中心)
Claims (4)
- 内周面に軌道面を有する外輪と、
外周面に軌道面を有する内輪と、
前記外輪及び前記内輪の軌道面間に配置された複数の玉と、
前記玉を転動自在に保持し、玉案内方式である保持器と、
を備えるアンギュラ玉軸受であって、
前記内輪の外周面には、背面側に内輪カウンターボアが凹設され、正面側に内輪溝肩部が凸設され、
前記外輪の内周面には、正面側に外輪カウンターボアが凹設され、背面側に外輪溝肩部が凸設され、
前記玉の接触角αは、45°≦α≦65°であり、
前記内輪溝肩部の径方向高さを前記玉の直径で除したものをAiとすると、0.35≦Ai≦0.50であり、
前記外輪溝肩部の径方向高さを前記玉の直径で除したものをAeとすると、0.35≦Ae≦0.50であり、
前記保持器は、略円環状のリング部と、前記リング部の正面側又は背面側から、所定間隔で軸方向に突出した複数の柱部と、隣り合う前記柱部の間に形成された複数のポケット部と、を有する冠型保持器であり、
前記ポケット部の球面中心位置は、前記リング部の最外径部と最内径部との径方向中間位置よりも、径方向一方側にずれており、
前記ポケット部を形成する前記柱部の周方向から見た側面は、前記リング部の径方向一方側面と径方向他方側面を結ぶ円弧、又は前記円弧の一部が切り欠かれてなるものであり、
前記リング部の径方向一方側面及び径方向他方側面のうち、少なくとも一方には、径方向に突出する凸部が少なくとも一つ形成される
ことを特徴とするアンギュラ玉軸受。 - 前記ポケット部を形成する前記柱部の周方向から見た側面は、前記円弧の径方向一方側端部が切り欠かれて軸方向に延びるように形成された第1ストレート形状部を含む
ことを特徴とする請求項1に記載のアンギュラ玉軸受。 - 前記ポケット部を形成する前記柱部の周方向から見た側面は、前記円弧の、前記第1ストレート形状部と、前記リング部の前記径方向一方側面と、を結ぶ部分が切り欠かれて形成された第2ストレート形状部を含む
ことを特徴とする請求項2に記載のアンギュラ玉軸受。 - 隣り合う前記玉同士の距離Lと、玉ピッチ円直径dmに円周率πを乗じた玉ピッチ円周長さπdmと、の関係は、2.5×10-3≦L/πdm≦13×10-3を満たす
ことを特徴とする請求項1~3の何れか1項に記載のアンギュラ玉軸受。
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