WO2015129064A1 - アンギュラ玉軸受 - Google Patents

アンギュラ玉軸受 Download PDF

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Publication number
WO2015129064A1
WO2015129064A1 PCT/JP2014/069096 JP2014069096W WO2015129064A1 WO 2015129064 A1 WO2015129064 A1 WO 2015129064A1 JP 2014069096 W JP2014069096 W JP 2014069096W WO 2015129064 A1 WO2015129064 A1 WO 2015129064A1
Authority
WO
WIPO (PCT)
Prior art keywords
cage
radial
ball
outer ring
inner ring
Prior art date
Application number
PCT/JP2014/069096
Other languages
English (en)
French (fr)
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 KR1020167023382A priority Critical patent/KR101988706B1/ko
Priority to CN201480076581.5A priority patent/CN106164512B/zh
Priority to JP2016504985A priority patent/JP6376212B2/ja
Publication of WO2015129064A1 publication Critical patent/WO2015129064A1/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
    • F16C33/412—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
    • 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
    • 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
    • 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
    • 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
    • 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

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).
  • 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 outer ring having a raceway surface on the inner peripheral surface An inner ring having a raceway surface on the outer peripheral surface; A plurality of balls disposed between the raceways of the outer ring and the inner ring; Holding the ball so as to roll freely, a cage that is a ball guide system, An angular contact ball bearing comprising: On the outer peripheral surface of the inner ring, if the outer diameter of the inner ring counter bore recessed on the back side is D1, and the outer diameter of the inner ring groove shoulder projecting on the front side is D2, D1 ⁇ D2.
  • the contact angle ⁇ of the balls is 45 ° ⁇ ⁇ ⁇ 65 °
  • 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
  • Ae is obtained by dividing the radial height of the outer ring groove shoulder by the diameter of the ball, 0.35 ⁇ Ae ⁇ 0.50
  • the cage is formed between a substantially annular ring portion, a plurality of column portions protruding in the axial direction at a predetermined interval from the front side or the back side of the ring portion, and a plurality of adjacent column portions.
  • a pocket-shaped cage having A reinforcing material is added to the cage,
  • the pitch circle diameter of the balls is X
  • ⁇ Rmax X 2 ⁇ 5.0 ⁇ 10 ⁇ 6 + X ⁇ 1.8 ⁇ 10 ⁇ 3 +0.14
  • ⁇ Rmin X 2 ⁇ 5.5 ⁇ 10 ⁇ 6 + X ⁇
  • the radial movement amount ⁇ R of the cage is ⁇ Rmin ⁇ ⁇ R ⁇ ⁇ Rmax
  • An angular contact ball bearing wherein ⁇ t ⁇ Rmin, where ⁇ t is a radial relative expansion amount of the cage at 100 ° C.
  • 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 according to (1) wherein a radial cross-sectional shape of the pocket portion is a circle having an arbitrary radius.
  • the cage is made of polyamide resin,
  • the reinforcing material is glass fiber;
  • the angular contact ball bearing according to (1) or (2), wherein the proportion of the reinforcing material in the cage is 5 to 30% by weight.
  • the outer diameter D1 of the inner ring counterbore is smaller than the outer diameter D2 of the inner ring groove shoulder (D1 ⁇ D2), and the inner diameter D3 of the outer ring counterbore is equal to the inner diameter of the outer ring groove shoulder D4. (D3> D4), and the contact angle ⁇ of the ball satisfies 45 ° ⁇ ⁇ ⁇ 65 °. Therefore, by increasing the contact angle, the load capacity of the bearing in the axial direction increases, and the bearing can be used with a larger preload. As a result, the rigidity of the bearing and thus the ball screw system can be improved.
  • the pitch circle diameter of the ball be X
  • ⁇ Rmax X 2 ⁇ 5.0 ⁇ 10 ⁇ 6 + X ⁇ 1.8 ⁇ 10 ⁇ 3 +0.14
  • ⁇ Rmin X 2 ⁇ 5.5 ⁇ 10 ⁇ 6 + X
  • the radial movement amount ⁇ R of the cage is set so as to satisfy ⁇ Rmin ⁇ ⁇ R ⁇ ⁇ Rmax. Therefore, it is possible to prevent the radial movement amount of the cage from becoming larger than the radial gap between the cage and the inner ring and the outer ring, and to prevent a problem that the cage and the inner ring or the outer ring are in contact with each other.
  • the radial relative expansion amount of the cage at 100 ° C. is ⁇ t, ⁇ t ⁇ Rmin. Therefore, the cage and the ball can be used without striking even at the upper limit of the bearing operating temperature.
  • FIG. 6 is a sectional view taken along the line VI-VI in FIG. 4. It is sectional drawing of the angular ball bearing which concerns on a modification. It is the figure which looked at the holder
  • (A) is a side view of the cage, and (b) is a view taken in the direction of the arrow IX of the AA ′ cross section of (a). It is a graph which shows the relationship between the pitch circle diameter of a ball
  • 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.
  • 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 X of the ball 3, so that 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.
  • the oil 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 shifted radially inward from the radial center of the ring portion 31.
  • the radial cross-sectional shape of the pocket portion 33 is a circle having an arbitrary radius r.
  • 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 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 a structure shifted radially outward as shown in FIGS. 7 and 8. 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 tip of the column part 32 is provided with a notch 34 in the middle in the circumferential direction and is divided into two parts. Therefore, when the retainer 30 is manufactured by injection molding, The corner portion 35 on the pocket portion 33 side of the column portion 32 can be prevented from being damaged by forcibly removing the mold part forming the portion 33.
  • 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 X increases, the ball 3 and the pocket portion 33 of the retainer 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.
  • 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 becomes narrow, 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 value ⁇ Rmax needs to be a specific value or less.
  • the radial movement amount ⁇ R of the ball guide type retainer 30 is, as shown in FIG. 9, the radial gap ⁇ Ri between the ball 3 and the pocket portion 33 on the radially inner side of the pocket portion 33, or the radially outer side.
  • ⁇ R min ( ⁇ Re, ⁇ Ri) ⁇ is determined by the smaller radial clearance ⁇ Re between the ball 3 and the pocket portion 33 in FIG.
  • the radial movement amount ⁇ R varies within a certain range due to variations in processing accuracy of the cage 30.
  • a dimensional error at the time of molding is added and the degree of variation tends to increase.
  • the angular ball bearing 1 of the present embodiment has a narrow space between the inner ring 20 and the outer ring 10 on the front side or the back side, so that a sufficient amount of grease can be secured.
  • the shape of the cage 30 has a special structure of a one-side ring structure. Therefore, in order to ensure the strength of the ring portion 31, the radial clearance of the cage 30 is determined so that the radial thickness of the ring portion 31 is as thick as possible and does not interfere with the inner ring 20 or the outer ring 10. There is a need to.
  • the radial motion amount ⁇ R of the cage 30 can be changed to the diameter between the cage 30 and the outer ring 10 or the inner ring 20. It is possible to prevent the gap from becoming larger than the direction gap, and to prevent a problem that the retainer 30 and the outer ring 10 or the inner ring 20 are in contact with each other.
  • the cage 30 is made of polyamide resin, the reinforcing material is glass fiber, and the addition amount of the glass fiber is set in the range of 5 to 30 weight percent.
  • the radial relative expansion amount ⁇ t of the cage 30 means the radial relative expansion amount of the cage 30 with respect to the outer ring 10, the inner ring 20, and the ball 3 (relative expansion amount caused by the difference in material), and the radial gap Defined by
  • the radial relative expansion amount ⁇ t of the cage 30 decreases as the glass fiber addition amount increases. This is due to the property of the polyamide that the linear expansion coefficient becomes smaller as the proportion of glass fiber in the component increases.
  • the cage 30 is made of polyamide resin, and the amount of glass fiber added is set in the range of 5 to 30 weight percent, and “the lower limit value ⁇ Rmin of the radial motion amount ⁇ R of the cage 30> the cage
  • a resin such as polyetheretherketone, polyphenylene sulfide, or polyimide may be used instead of polyamide.
  • a synthetic resin to which an appropriate amount of carbon fiber, aramid fiber, or the like is added may be used as the reinforcing material.
  • FIG. 11 shows the relationship between the glass fiber content and the linear expansion coefficient of the polyamide 66.
  • the polyamide 66 has a property that the linear expansion coefficient becomes smaller as the glass fiber content in the component increases.
  • Example 1 In the angular contact ball bearing 1 having a bearing inner diameter (d) of ⁇ 30 mm, a bearing outer diameter (D) of ⁇ 62 mm, and a ball pitch circle diameter (W) of ⁇ 47 mm, ⁇ Rmax ⁇ 0.24 mm and ⁇ Rmin ⁇ 0.10 mm.
  • the radial motion amount ⁇ R ⁇ R min ( ⁇ Re, ⁇ Ri) ⁇ of the container 30 is set to 0.10 mm ⁇ ⁇ R ⁇ 0.24 mm.
  • the radial motion amount ⁇ R exceeds the upper limit of 0.24 mm, the radial motion amount ⁇ R of the cage 30 increases, and there is a problem that the cage 30 and the inner and outer rings come into contact. If the thickness of the ring portion 31 of the retainer 30 is reduced, it becomes difficult to make contact, but the strength of the ring portion 31 of the retainer 30 is lowered and may break during use.
  • the upper limit of the bearing temperature is 100 ° C. Therefore, if the room temperature is 20 ° C., the temperature difference ⁇ T is 80 ° C.
  • Table 1 shows the relationship between the radial relative expansion amount ⁇ t of the cage 30 and the glass fiber content at an operating temperature of 100 ° C.
  • Example 2 In the angular contact ball bearing 1 having a bearing inner diameter (d) of ⁇ 60 mm, a bearing outer diameter (D) of ⁇ 120 mm, and a ball pitch circle diameter (W) of ⁇ 93 mm, ⁇ Rmax ⁇ 0.36 mm and ⁇ Rmin ⁇ 0.21 mm.
  • the radial movement amount ⁇ R of the container 30 is set to 0.21 mm ⁇ ⁇ R ⁇ 0.36 mm.
  • Table 2 shows the relationship between the radial relative expansion amount ⁇ t of the cage 30 and the glass fiber content at a use temperature of 100 ° C.
  • the lower limit of the reinforcing fiber content in the synthetic resin of the cage 30 material is preferably 5 weight percent.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)
PCT/JP2014/069096 2014-02-27 2014-07-17 アンギュラ玉軸受 WO2015129064A1 (ja)

Priority Applications (3)

Application Number Priority Date Filing Date Title
KR1020167023382A KR101988706B1 (ko) 2014-02-27 2014-07-17 앵귤러 볼 베어링
CN201480076581.5A CN106164512B (zh) 2014-02-27 2014-07-17 角接触滚珠轴承
JP2016504985A JP6376212B2 (ja) 2014-02-27 2014-07-17 アンギュラ玉軸受

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2014037087 2014-02-27
JP2014-037087 2014-02-27

Publications (1)

Publication Number Publication Date
WO2015129064A1 true WO2015129064A1 (ja) 2015-09-03

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2014/069096 WO2015129064A1 (ja) 2014-02-27 2014-07-17 アンギュラ玉軸受

Country Status (5)

Country Link
JP (1) JP6376212B2 (ko)
KR (1) KR101988706B1 (ko)
CN (1) CN106164512B (ko)
TW (1) TWI567306B (ko)
WO (1) WO2015129064A1 (ko)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2017072249A (ja) * 2015-10-05 2017-04-13 Ntn株式会社 アンギュラ玉軸受およびこれを用いたボールねじ装置
WO2017061417A1 (ja) * 2015-10-05 2017-04-13 Ntn株式会社 アンギュラ玉軸受およびこれを用いたボールねじ装置
WO2022024978A1 (ja) * 2020-07-28 2022-02-03 Ntn株式会社 アンギュラ玉軸受

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10618370B2 (en) 2016-09-02 2020-04-14 Mando Corporation Active roll stabilizer

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2003130060A (ja) * 2001-10-25 2003-05-08 Nsk Ltd ラジアル玉軸受
JP2004052785A (ja) * 2002-07-16 2004-02-19 Koyo Seiko Co Ltd アンギュラ玉軸受用の樹脂保持器
JP2006153094A (ja) * 2004-11-26 2006-06-15 Nsk Ltd 玉軸受及び該玉軸受を用いた工作機械の回転テーブル装置
JP2007298184A (ja) * 2006-08-25 2007-11-15 Nsk Ltd アンギュラ玉軸受
JP5375969B2 (ja) * 2009-11-19 2013-12-25 日本精工株式会社 ピニオン軸用回転支持装置

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS596262Y2 (ja) * 1978-10-16 1984-02-27 株式会社不二越 樹脂製冠形保持器
JP2000104742A (ja) 1998-09-29 2000-04-11 Ntn Corp ボールねじ支持用転がり軸受
JP4055938B2 (ja) * 2002-04-18 2008-03-05 ミネベア株式会社 ラジアルボールベアリングのリテーナ
EP1367277B1 (en) * 2002-05-30 2008-06-25 Minebea Co., Ltd. Retainer with rotationally symmetric pockets
JP2005061509A (ja) * 2003-08-11 2005-03-10 Nsk Ltd 転がり軸受
JP2008185107A (ja) * 2007-01-29 2008-08-14 Nsk Ltd 玉軸受
JP5348590B2 (ja) * 2009-06-26 2013-11-20 Ｎｔｎ株式会社 深みぞ玉軸受およびギヤ支持装置
JP2013087865A (ja) * 2011-10-18 2013-05-13 Nsk Ltd 多列組合せ玉軸受

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2003130060A (ja) * 2001-10-25 2003-05-08 Nsk Ltd ラジアル玉軸受
JP2004052785A (ja) * 2002-07-16 2004-02-19 Koyo Seiko Co Ltd アンギュラ玉軸受用の樹脂保持器
JP2006153094A (ja) * 2004-11-26 2006-06-15 Nsk Ltd 玉軸受及び該玉軸受を用いた工作機械の回転テーブル装置
JP2007298184A (ja) * 2006-08-25 2007-11-15 Nsk Ltd アンギュラ玉軸受
JP5375969B2 (ja) * 2009-11-19 2013-12-25 日本精工株式会社 ピニオン軸用回転支持装置

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2017072249A (ja) * 2015-10-05 2017-04-13 Ntn株式会社 アンギュラ玉軸受およびこれを用いたボールねじ装置
WO2017061417A1 (ja) * 2015-10-05 2017-04-13 Ntn株式会社 アンギュラ玉軸受およびこれを用いたボールねじ装置
CN108138839A (zh) * 2015-10-05 2018-06-08 Ntn株式会社 角接触滚珠轴承和采用它的滚珠丝杠装置
WO2022024978A1 (ja) * 2020-07-28 2022-02-03 Ntn株式会社 アンギュラ玉軸受

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CN106164512A (zh) 2016-11-23
CN106164512B (zh) 2019-03-29
JP6376212B2 (ja) 2018-08-22

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