WO2015145794A1 - Roulement à billes à contact oblique - Google Patents

Roulement à billes à contact oblique Download PDF

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Publication number
WO2015145794A1
WO2015145794A1 PCT/JP2014/069087 JP2014069087W WO2015145794A1 WO 2015145794 A1 WO2015145794 A1 WO 2015145794A1 JP 2014069087 W JP2014069087 W JP 2014069087W WO 2015145794 A1 WO2015145794 A1 WO 2015145794A1
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WO
WIPO (PCT)
Prior art keywords
radial
cage
ball
ring
inner ring
Prior art date
Application number
PCT/JP2014/069087
Other languages
English (en)
Japanese (ja)
Inventor
恭平 松永
美昭 勝野
Original Assignee
日本精工株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 日本精工株式会社 filed Critical 日本精工株式会社
Priority to CN201580017138.5A priority Critical patent/CN106460929B/zh
Priority to PCT/JP2015/058384 priority patent/WO2015146811A1/fr
Priority to JP2016510290A priority patent/JP6508196B2/ja
Priority to KR1020167026686A priority patent/KR101960145B1/ko
Publication of WO2015145794A1 publication Critical patent/WO2015145794A1/fr
Priority to JP2019016171A priority patent/JP2019074214A/ja

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Classifications

    • 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
    • F16C19/14—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
    • F16C2240/70—Diameters; Radii
    • F16C2240/80—Pitch circle diameters [PCD]
    • 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
    • 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
    • F16C33/66—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 radial side with respect to the radial center of the ring portion,
  • the radial cross-sectional shape of the pocket portion is a circle with an arbitrary radius composed of an arc connecting the one radial side surface and the other 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. It is sectional drawing of a holder
  • 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. That is, the spherical center position of the pocket portion 33 is shifted from the radial center of the ring portion 31 radially inward (one radial direction side).
  • the radial cross-sectional shape of the pocket portion 33 is from an arc 33a connecting the radial inner side surface (one radial side surface) 31a and the radial outer side surface (radial other side surface) 31b of the ring portion 31.
  • a circle with an arbitrary radius r. The center of the circle is indicated by P.
  • the arc 33a is a first straight-shaped portion 33b extending in the axial direction by cutting out the radially inner portion (one radial portion).
  • the first straight shape portion 33b is disposed on the back side of the center P of the circle.
  • the arc 33a has a second straight shape in which a portion connecting the front end of the first straight shape portion 33b and the back end of the radial inner side surface 31a of the ring portion 31 is notched. Part 33c. 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). Further, the first straight shape portion 33b is formed so that the center Oi of the ball 3 (spherical center of the pocket portion 33) overlaps the first straight shape portion 33b in the axial direction.
  • both side surfaces in the circumferential direction of the column portion 32 and side surfaces on the back side (column portion 32 side) of the ring portion 31 forming the pocket portion 33 are spherical shapes similar to the balls 3.
  • 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.
  • a resin such as polyamide, polyetheretherketone, polyphenylene sulfide, or polyimide is applied, and as a reinforcing material, glass fiber, carbon fiber, aramid fiber, or the like is 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 radial cross-sectional shape of the pocket portion 33 of the cage 30 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 (see FIG. 1). ) Becomes narrow, and the possibility that the cage 30 and the inner ring 20 interfere with each other increases.
  • the axial distance ⁇ S1 between the cage 30 and the inner ring 20 can be increased by forming the second straight shape portion 33c in the pocket portion 33. It is possible to reduce the possibility that the cage 30 and the inner ring 20 interfere with each other.
  • 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.
  • FIGS. 9 and 10 an example of the shape when the radial load F is applied to the cage 30 and the cage 30 is bent in the radial direction is schematically represented by a broken line.
  • 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 radial cross-sectional shape of the pocket portion 33 of the cage 30 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 is narrowed and retained. The possibility that the container 30 and the inner ring 20 interfere with each other increases. Therefore, as in the angular ball bearing 1 of the present embodiment, the axial distance ⁇ S1 between the cage 30 and the inner ring 20 can be increased by forming the second straight shape portion 33c in the pocket portion 33. It is possible to reduce the possibility that the cage 30 and the inner ring 20 interfere with each other.
  • 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 radial cross-sectional shape of the pocket portion 33 of the cage 30 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 is narrowed and retained. The possibility that the container 30 and the inner ring 20 interfere with each other increases.
  • the axial distance ⁇ S1 between the cage 30 and the inner ring 20 can be increased by forming the second straight shape portion 33c in the pocket portion 33. It is possible to reduce the possibility that the cage 30 and the inner ring 20 interfere with each other.
  • 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 pitch 3 pitch circumference length ⁇ dm is 2.5 ⁇ 10 ⁇ 3 ⁇ L / ⁇ dm ⁇ 13 ⁇ 10
  • the design is such that the relationship of ⁇ 3 is established. If L / ⁇ dm is smaller than 2.5 ⁇ 10 ⁇ 3 , the circumferential thickness of the pillar portion 32 of the cage 30 becomes too thin, and a hole is opened during molding or cutting. In particular, when a large amount of reinforcing material is contained, the fluidity of the synthetic resin, which is the material of the cage 30, is deteriorated at the time of molding, and holes are easily opened. On the other hand, if L / ⁇ dm is larger than 13 ⁇ 10 ⁇ 3 , the number of balls Z is reduced, and the axial load carrying capacity and rigidity of the bearing are lowered.
  • 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 radial cross-sectional shape of the pocket portion 33 of the cage 30 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 is narrowed and retained. The possibility that the container 30 and the inner ring 20 interfere with each other increases. Therefore, as in the angular ball bearing 1 of the present embodiment, the axial distance ⁇ S1 between the cage 30 and the inner ring 20 can be increased by forming the second straight shape portion 33c in the pocket portion 33. It is possible to reduce the possibility that the cage 30 and the inner ring 20 interfere with each other.
  • the radial cross-sectional shape of the pocket portion 33 of the cage 30 is a conventional circular shape having an arbitrary radius r1, the same as the cage 30 of the present embodiment described above.
  • the axial relative movement amount ⁇ A of the cage 30 increases during the rotation of the bearing.
  • retainer 30 is circular, as shown in FIG. 14, the radial direction inner edge part 33d which is a part which guides the ball
  • bowl 3 is a point contact.
  • 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.
  • 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 portion 33 b is provided in the radial cross-sectional shape of the pocket portion 33, as shown in FIG.
  • the straight shape portion 33b and the ball 3 are configured to be in line contact with each other 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 fixed by applying a light measurement load radially inward with the ring portion 31 of the cage 30 down. There is a method to measure. At this time, the ball 3 in the pocket portion 33 approaches the ring portion 31 in the pocket portion 33 by gravity. As a result, 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. As a result, 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 fits into the straight shape portion 33b due to the measurement load, It is easy to accurately measure the ball circumscribed circle diameter and the ball inscribed circle diameter without 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 convex portion 38 is desirably provided in the vicinity of the center of the ring portion 31 excluding the axial end portion. . That is, from the viewpoint of avoiding the contact of the inner ring 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.
  • 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, and may be configured so as to be shifted radially outward as shown in FIGS. I do not care. 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 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 radial cross-sectional shape of the pocket portion 33 is an arbitrary radius r composed of an arc connecting the radial outer side surface (radial one side surface) 31b of the ring portion 31 and the radial inner side surface (radial other side surface) 31a. It is assumed to be a circle.
  • the arc 33a is a first straight-shaped portion 33b extending in the axial direction by cutting out a radially outer portion (one radial portion).
  • the first straight shape portion 33b is disposed on the front side of the center P of the circle.
  • the arc 33a has a second straight shape in which a portion connecting the end portion on the back surface side of the first straight shape portion 33b and the end portion on the front surface side of the radially outer side surface 31b of the ring portion 31 is notched. Part 33c. 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). Further, the first straight shape portion 33b is formed so that the center Oi of the ball 3 (spherical center of the pocket portion 33) overlaps the first straight shape portion 33b in the axial direction.
  • 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.

Abstract

L'invention concerne une cage (30) qui est une cage de type couronne ayant une bague approximativement annulaire (31), une pluralité de colonnes (32) qui font saillie dans la direction axiale à partir d'un côté avant ou d'un côté arrière de la bague (31) à intervalles prescrits, et une pluralité de cavités (33) qui sont formées entre des colonnes adjacentes (32). La position des centres des surfaces sphériques des cavités (33) est décalée dans la direction radiale vers l'intérieur par rapport au centre de la bague (31) dans la direction radiale. La forme en coupe transversale des cavités (33) dans la direction radiale est un cercle ayant un rayon arbitraire (r) et qui comprend un arc circulaire (33a) qui relie une surface intérieure dans la direction radiale (31a) de la bague (31) et une surface extérieure dans la direction radiale (31b) de la bague (31). Au moins une partie (38) faisant saillie vers l'intérieur, qui fait saillie dans la direction radiale, ou une partie (39) faisant saillie vers l'extérieur, qui fait saillie dans la direction radiale, est formée dans au moins l'une de la surface intérieure dans la direction radiale (31a) de la bague (31) et de la surface extérieure dans la direction radiale (31b) de la bague (31).
PCT/JP2014/069087 2014-03-28 2014-07-17 Roulement à billes à contact oblique WO2015145794A1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
CN201580017138.5A CN106460929B (zh) 2014-03-28 2015-03-19 角接触球轴承
PCT/JP2015/058384 WO2015146811A1 (fr) 2014-03-28 2015-03-19 Roulement à billes angulaire
JP2016510290A JP6508196B2 (ja) 2014-03-28 2015-03-19 アンギュラ玉軸受
KR1020167026686A KR101960145B1 (ko) 2014-03-28 2015-03-19 앵귤러 볼 베어링
JP2019016171A JP2019074214A (ja) 2014-03-28 2019-01-31 アンギュラ玉軸受及びその製造方法

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JP2014-068945 2014-03-28
JP2014068945 2014-03-28

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PCT/JP2015/058384 WO2015146811A1 (fr) 2014-03-28 2015-03-19 Roulement à billes angulaire

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DE102017119251A1 (de) * 2017-08-23 2019-02-28 Schaeffler Technologies AG & Co. KG Kammkäfig für ein Kugellager

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JP6950430B2 (ja) * 2017-10-04 2021-10-13 株式会社ジェイテクト 玉軸受
WO2020080061A1 (fr) * 2018-10-15 2020-04-23 日本精工株式会社 Roulement à billes angulaire
TWI708021B (zh) * 2018-10-31 2020-10-21 日商日本精工股份有限公司 圓筒滾子軸承

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JP2000104742A (ja) 1998-09-29 2000-04-11 Ntn Corp ボールねじ支持用転がり軸受
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JPH10103359A (ja) * 1996-09-30 1998-04-21 Ntn Corp アンギュラ玉軸受用樹脂保持器
JP2003329044A (ja) * 2002-05-15 2003-11-19 Nsk Ltd 転がり軸受
JP2011112195A (ja) * 2009-11-30 2011-06-09 Nsk Ltd 玉軸受
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KR101960145B1 (ko) 2019-03-19
TW201600747A (zh) 2016-01-01
JPWO2015146811A1 (ja) 2017-04-13
JP2019074214A (ja) 2019-05-16
CN106460929B (zh) 2019-12-10
CN106460929A (zh) 2017-02-22
KR20160128359A (ko) 2016-11-07
JP6508196B2 (ja) 2019-05-08
TW201713866A (zh) 2017-04-16
TWI666390B (zh) 2019-07-21
WO2015146811A1 (fr) 2015-10-01
TWI576521B (zh) 2017-04-01

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