JP2007170465A - Caulked retainer for thrust ball bearing, its design method, and thrust ball bearing - Google Patents

Caulked retainer for thrust ball bearing, its design method, and thrust ball bearing Download PDF

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JP2007170465A
JP2007170465A JP2005365976A JP2005365976A JP2007170465A JP 2007170465 A JP2007170465 A JP 2007170465A JP 2005365976 A JP2005365976 A JP 2005365976A JP 2005365976 A JP2005365976 A JP 2005365976A JP 2007170465 A JP2007170465 A JP 2007170465A
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Prior art keywords
ball
pocket
cage
ball bearing
bearing
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JP2005365976A
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Kazuhiro Matsuki
和宏 松木
Yoshihiro Sato
佳宏朗 佐藤
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NSK Ltd
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NSK Ltd
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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
    • F16C19/10—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for axial load mainly
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/38—Ball cages
    • F16C33/3887—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
    • F16C33/38—Ball cages
    • F16C33/42—Ball cages made from wire or sheet metal strips
    • F16C33/422—Ball cages made from wire or sheet metal strips made from sheet metal
    • F16C33/425—Ball cages made from wire or sheet metal strips made from sheet metal from a single part, e.g. ribbon cages with one corrugated annular part
    • 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
    • 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

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

Abstract

<P>PROBLEM TO BE SOLVED: To provide a caulked retainer for a thrust ball bearing which can suppress the generation of excessive stress caused by the lead and lag of balls at circumferential edges of pockets. <P>SOLUTION: The caulked retainer is manufactured by adjusting a caulking force to the diameter da of a pocket 28 or balls 25 so that the ratio of a pocket clearance δ between the pocket 28 and the ball 25 in the circumference to the diameter da of the ball 25 satisfies the following formula 0.06≤δ/da≤0.12. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

本発明は、スラスト玉軸受に用いられる加締め保持器とその設計方法に関する。また、本発明は加締め保持器を備えたスラスト玉軸受に関する。   The present invention relates to a caulking cage used for a thrust ball bearing and a design method thereof. The present invention also relates to a thrust ball bearing provided with a caulking cage.

ボールねじ軸などの回転軸の端部を支持する軸受装置として、図８に示すものが知られている（例えば特許文献１参照）。この軸受装置はモータＭにより回転駆動されるボールねじ軸ＢＳの上端部を支持する上部軸受としての一対のアンギュラ玉軸受１，１を有しており、これらアンギュラ玉軸受１，１の下方には、鉛直方向の荷重を受ける下部軸受としてスラスト玉軸受２が設けられている。   As a bearing device for supporting the end of a rotating shaft such as a ball screw shaft, one shown in FIG. 8 is known (see, for example, Patent Document 1). This bearing device has a pair of angular ball bearings 1, 1 as upper bearings that support the upper end of a ball screw shaft BS that is rotationally driven by a motor M, and below these angular ball bearings 1, 1. A thrust ball bearing 2 is provided as a lower bearing that receives a load in the vertical direction.

このような軸受装置に用いられるスラスト玉軸受の一例を図９に示す。同図に示されるスラスト玉軸受は固定側環状レース部材３および回転側環状レース部材４を備えており、固定側環状レース部材３の図中下面部には、円環状のボール軌道溝５が形成されている。このボール軌道溝５は回転側環状レース部材４の図中上面部に形成された円環状のボール軌道溝６と対向しており、ボール軌道溝５とボール軌道溝６との間に設けられた複数個の玉７は、加締め保持器８によりレース部材３，４の周方向に一定間隔で保持されている。   An example of a thrust ball bearing used in such a bearing device is shown in FIG. The thrust ball bearing shown in the figure includes a fixed-side annular race member 3 and a rotation-side annular race member 4, and an annular ball raceway groove 5 is formed on the lower surface portion of the fixed-side annular race member 3 in the figure. Has been. The ball raceway groove 5 faces an annular ball raceway groove 6 formed on the upper surface portion of the rotary annular race member 4 in the drawing, and is provided between the ball raceway groove 5 and the ball raceway groove 6. The plurality of balls 7 are held by the crimping cage 8 at regular intervals in the circumferential direction of the race members 3 and 4.

加締め保持器８は円環状の金属板９から形成されており、この金属板９には複数のポケット１０（図１０参照）が金属板９の周方向に一定間隔で穿設されている。これらのポケット１０は玉７の直径よりも小さい直径（例えば玉直径の９９〜９５％程度）で円形に形成されており、玉７は金属板９の外側周縁部と内側周縁部を波形にプレス加工し、金属板９の外側周縁部と内側周縁部とで玉７を加締めることによって各ポケット１０内に保持されている。
特開２００３−６２６６０号公報 The caulking cage 8 is formed of an annular metal plate 9, and a plurality of pockets 10 (see FIG. 10) are formed in the metal plate 9 at regular intervals in the circumferential direction of the metal plate 9. These pockets 10 are formed in a circular shape with a diameter smaller than the diameter of the ball 7 (for example, about 99 to 95% of the ball diameter), and the ball 7 presses the outer peripheral edge and inner peripheral edge of the metal plate 9 in a corrugated shape. The ball 7 is processed and held in each pocket 10 by crimping the balls 7 at the outer peripheral edge and the inner peripheral edge of the metal plate 9.
JP 2003-62660 A

ところで、ボールねじ軸などの回転軸の端部がラジアル方向に偏芯した状態で回転すると、図１１に示すように、スラスト玉軸受の固定側環状レース部材３と回転側環状レース部材４との間にラジアル方向の相対変位が生じ、レース部材３，４に対する玉７の接触角が変化する。そして、玉７の接触角が変化すると保持器８のポケット１０内に保持された玉７がそれぞれ異なる速度で公転することになるため、玉７の進み遅れが保持器８のポケット１０内で発生し、図１２に示すように、進み遅れの発生した玉７がポケット１０の周縁部に当接する。このため、上述した加締め保持器では、スラスト玉軸受の固定側環状レース部材３と回転側環状レース部材４との間にラジアル方向の相対変位が生じると玉７がポケット１０の周縁部に当接し、保持器の破損を招くような過大な応力がポケット１０の周縁部に発生するという問題があった。なお、図１１に示す矢印は固定側環状レース部材４の回転方向を示し、図１２に示す矢印は加締め保持器８の回転方向を示している。また、玉の公転速度Ｖｃは、次式で表される。
Ｖｃ＝（π・Ｄｐｗ／６０×１０−３）×ｎｃ
ただし、Ｄｐｗ：転動体ピッチ径（ｍｍ）
ｎｃ：回転速度（ｍｉｎ−１） By the way, when the end of the rotating shaft such as the ball screw shaft is rotated in a state of being eccentric in the radial direction, as shown in FIG. 11, the fixed-side annular race member 3 and the rotating-side annular race member 4 of the thrust ball bearing A relative displacement in the radial direction occurs between them, and the contact angle of the balls 7 with respect to the race members 3 and 4 changes. When the contact angle of the ball 7 changes, the balls 7 held in the pocket 10 of the cage 8 revolve at different speeds, so that the advance and delay of the ball 7 occurs in the pocket 10 of the cage 8. Then, as shown in FIG. 12, the ball 7 with the advance / delay is brought into contact with the peripheral edge of the pocket 10. For this reason, in the caulking cage described above, when a radial displacement occurs between the stationary annular race member 3 and the rotational annular race member 4 of the thrust ball bearing, the ball 7 contacts the peripheral edge of the pocket 10. There has been a problem that excessive stress is generated at the peripheral edge of the pocket 10 in contact with the cage and causing damage to the cage. In addition, the arrow shown in FIG. 11 has shown the rotation direction of the stationary side annular race member 4, and the arrow shown in FIG. Further, the revolution speed V c of the ball is expressed by the following equation.
V c = (π · D pw / 60 × 10 −3 ) × n c
Where D pw : rolling element pitch diameter (mm)
n c : rotational speed (min −1 )

本発明は上述した問題点に着目してなされたものであり、その目的は、玉の進み遅れに起因する過大な応力がポケットの周縁部に発生することを抑制することのできるスラスト玉軸受用加締め保持器及びその設計方法を提供することにある。また、本発明の他の目的は、固定側環状レース部材と回転側環状レース部材との間に発生するラジアル方向の相対変位により加締め保持器に過大な負荷が加わることを防止することのできるスラスト玉軸受を提供することにある。   The present invention has been made paying attention to the above-mentioned problems, and its purpose is for a thrust ball bearing capable of suppressing the occurrence of excessive stress in the peripheral portion of the pocket due to the advance and delay of the balls. A caulking cage and a design method thereof are provided. Another object of the present invention is to prevent an excessive load from being applied to the crimping cage due to the relative displacement in the radial direction that occurs between the stationary annular race member and the rotating annular race member. It is to provide a thrust ball bearing.

上記課題を解決するため、本発明のうち請求項１の発明に係るスラスト玉軸受用加締め保持器の設計方法は、回転軸の端部を支持する軸受装置の上部軸受として用いられるラジアル転がり軸受の下部に配置されるスラスト玉軸受の玉を保持するためのポケットを周方向に複数有する加締め保持器の設計方法であって、前記ポケットと前記玉との間の保持器周方向のポケット隙間が所定の値より大きくなるように、前記ポケット隙間を前記回転軸の偏心量の関数として設定して前記加締め保持器を設計することを特徴とする。   In order to solve the above-described problems, a thrust ball bearing caulking cage design method according to claim 1 of the present invention is a radial rolling bearing used as an upper bearing of a bearing device that supports an end of a rotating shaft. A method for designing a caulking cage having a plurality of pockets in the circumferential direction for holding balls of thrust ball bearings arranged in the lower part of the cage, wherein the pocket clearance in the circumferential direction of the cage between the pockets and the balls The caulking cage is designed by setting the pocket gap as a function of the amount of eccentricity of the rotating shaft so that the value becomes larger than a predetermined value.

本発明のうち請求項２の発明に係るスラスト玉軸受用加締め保持器は、回転軸の端部を支持する軸受装置の上部軸受として用いられるラジアル転がり軸受の下部に配置されるスラスト玉軸受の玉を保持する複数のポケットを有する加締め保持器であって、前記ポケットと前記玉との間の保持器周方向のポケット隙間をδ、前記玉の直径をｄａとしたとき、前記ポケット隙間と前記玉の直径との比が０．０６≦δ／ｄａ≦０．１２であることを特徴とする。   A thrust ball bearing caulking cage according to the invention of claim 2 of the present invention is a thrust ball bearing disposed at the lower part of a radial rolling bearing used as an upper bearing of a bearing device for supporting an end of a rotating shaft. A caulking cage having a plurality of pockets for holding balls, wherein the pocket gap in the circumferential direction of the cage between the pocket and the ball is δ, and the diameter of the ball is da, A ratio with the diameter of the ball is 0.06 ≦ δ / da ≦ 0.12.

本発明のうち請求項３の発明に係るスラスト玉軸受用加締め保持器は、請求項２記載のスラスト玉軸受用加締め保持器において、前記ポケット隙間と前記玉の直径との比が０．０６≦δ／ｄａ≦０．１２となるように、前記ポケットの直径または前記玉への加締め力を調整してなることを特徴とする。
本発明のうち請求項４の発明に係るスラスト玉軸受は、請求項３または請求項４記載の加締め保持器を備えたことを特徴とする。 A thrust ball bearing caulking cage according to a third aspect of the present invention is the thrust ball bearing caulking cage according to the second aspect, wherein the ratio of the pocket clearance to the ball diameter is 0. The diameter of the pocket or the caulking force on the ball is adjusted so that 06 ≦ δ / da ≦ 0.12.
A thrust ball bearing according to a fourth aspect of the present invention includes the caulking cage according to the third or fourth aspect.

本発明によれば、玉の進み遅れがポケット内で発生しても玉がポケットの周縁部に当接することがないので、玉の進み遅れに起因する過大な応力がポケットの周縁部に発生することを抑制することができる。したがって、固定側環状レース部材と回転側環状レース部材との間に発生するラジアル方向の相対変位により加締め保持器に過大な負荷が加わることを防止でき、保持器の破損を抑制することができる。   According to the present invention, even if a ball advance delay occurs in the pocket, the ball does not come into contact with the peripheral edge portion of the pocket, so that excessive stress due to the ball advance delay occurs in the peripheral edge portion of the pocket. This can be suppressed. Therefore, it is possible to prevent an excessive load from being applied to the crimping cage due to the relative displacement in the radial direction generated between the fixed-side annular race member and the rotary-side annular race member, and it is possible to suppress breakage of the cage. .

以下、図１〜図７を参照して本発明の実施の形態について説明する。
図１において符号２０は本発明の一実施形態であるスラスト玉軸受であって、このスラスト玉軸受２０は、固定側環状レース部材２１および回転側環状レース部材２２を備えている。上記固定側環状レース部材２１の図中下面部には、円環状のボール軌道溝２３が形成されている。このボール軌道溝２３は回転側環状レース部材２２の図中上面部に形成された円環状のボール軌道溝２４と対向しており、ボール軌道溝２３とボール軌道溝２４との間に設けられた複数個の玉２５は、加締め保持器２６によりレース部材２１，２２の周方向に一定間隔で保持されている。 Hereinafter, embodiments of the present invention will be described with reference to FIGS.
In FIG. 1, reference numeral 20 denotes a thrust ball bearing according to an embodiment of the present invention, and this thrust ball bearing 20 includes a fixed-side annular race member 21 and a rotation-side annular race member 22. An annular ball raceway groove 23 is formed on the lower surface portion of the fixed-side annular race member 21 in the figure. The ball raceway groove 23 is opposed to an annular ball raceway groove 24 formed on the upper surface portion of the rotation side annular race member 22 in the drawing, and is provided between the ball raceway groove 23 and the ball raceway groove 24. The plurality of balls 25 are held by the crimping cage 26 at regular intervals in the circumferential direction of the race members 21 and 22.

加締め保持器２６は円環状の金属板２７から形成されており、この金属板２７には複数のポケット２８（図２及び図３参照）が金属板２７の周方向に一定間隔で穿設されている。これらのポケット２８は玉２５の直径よりも小さい直径（例えば玉直径の９９〜９５％程度）で円形に形成されており、玉２５は、図４に示すように、金属板２７の外側周縁部２７ａと内側周縁部２７ｂを波形にプレス加工し、金属板２７の外側周縁部２７ａと内側周縁部２７ｂとで玉２５を加締めることによって各ポケット２８内に保持されている。   The caulking cage 26 is formed of an annular metal plate 27, and a plurality of pockets 28 (see FIGS. 2 and 3) are formed in the metal plate 27 at regular intervals in the circumferential direction of the metal plate 27. ing. These pockets 28 are formed in a circular shape with a diameter smaller than the diameter of the balls 25 (for example, about 99 to 95% of the diameter of the balls), and the balls 25 are formed on the outer peripheral edge of the metal plate 27 as shown in FIG. 27a and the inner peripheral edge portion 27b are pressed into a corrugated shape, and the ball 25 is crimped by the outer peripheral edge portion 27a and the inner peripheral edge portion 27b of the metal plate 27, thereby being held in each pocket 28.

このような構成において、ポケット２８と玉２５との間の保持器周方向のポケット隙間をδ（図２及び図１２参照）、玉２５の直径をｄａとすると、本発明の一実施形態では、ポケット隙間δと玉２５の直径ｄａとの比が０．０６≦δ／ｄａ≦０．１２となるように、ポケット２８の直径または玉２５への加締め力を調整して加締め保持器が製造されている。   In such a configuration, if the pocket clearance in the cage circumferential direction between the pocket 28 and the ball 25 is δ (see FIGS. 2 and 12) and the diameter of the ball 25 is da, in one embodiment of the present invention, The caulking cage is adjusted by adjusting the diameter of the pocket 28 or the caulking force on the ball 25 so that the ratio of the pocket gap δ to the diameter da of the ball 25 is 0.06 ≦ δ / da ≦ 0.12. It is manufactured.

ここで、ポケット隙間δと玉の直径ｄａとの比を０．０６≦δ／ｄａ≦０．１２に設定する理由は、以下の理由からである。すなわち、本発明者は保持器破損の原因となる保持器ポケット内における玉の進み遅れを調べるため、コンピュータによるシミュレーション計算を行った。その結果、図５〜図７に示すような計算結果が得られた。
なお、図５〜図７に示す計算結果は軸受内径１７ｍｍ、軸受外径３５ｍｍ、玉数１１個のスラスト玉軸受を対象とし、アキシアル荷重を１．７３ｋＮとして計算を行った結果である。 Here, the reason why the ratio between the pocket gap δ and the ball diameter da is set to 0.06 ≦ δ / da ≦ 0.12 is as follows. That is, the present inventor performed a simulation calculation by a computer in order to investigate the advance and delay of the ball in the cage pocket which causes the cage to be broken. As a result, calculation results as shown in FIGS. 5 to 7 were obtained.
The calculation results shown in FIG. 5 to FIG. 7 are the results of calculation with an axial load of 1.73 kN for a thrust ball bearing having a bearing inner diameter of 17 mm, a bearing outer diameter of 35 mm, and 11 balls.

図５はスラスト玉軸受の固定側環状レース部材と回転側環状レース部材との間に発生したラジアル方向の相対変位量ｅが０．０１ｍｍ、０．０２ｍｍ、０．０３ｍｍ、０．０４ｍｍ、０．０５ｍｍ、０．０６ｍｍ、０．０７ｍｍ、０．０８ｍｍ、０．０９ｍｍ、０．１０ｍｍ、０．１１ｍｍの場合における玉の方位角と接触角との関係をコンピュータにより計算した結果を示しており、図５から明らかなように、ラジアル方向の相対変位量ｅが大きくなると、玉の接触角が大きくなることがわかる。   FIG. 5 shows that the radial relative displacement e generated between the fixed-side annular race member and the rotary-side annular race member of the thrust ball bearing is 0.01 mm, 0.02 mm, 0.03 mm, 0.04 mm,. The figure shows the result of calculating the relationship between the ball azimuth and contact angle in the case of 05 mm, 0.06 mm, 0.07 mm, 0.08 mm, 0.09 mm, 0.10 mm, and 0.11 mm by a computer. As can be seen from FIG. 5, the ball contact angle increases as the radial relative displacement amount e increases.

図６はスラスト玉軸受の固定側環状レース部材と回転側環状レース部材との間に発生したラジアル方向の相対変位量ｅが０．０１ｍｍ、０．０２ｍｍ、０．０３ｍｍ、０．０４ｍｍ、０．０５ｍｍ、０．０６ｍｍ、０．０７ｍｍ、０．０８ｍｍ、０．０９ｍｍ、０．１０ｍｍ、０．１１ｍｍの場合における玉の方位角と進み遅れ量との関係をコンピュータにより計算した結果を示しており、図６から明らかなように、ラジアル方向の相対変位量ｅが大きくなると、保持器ポケット内における玉の進み遅れが大きくなることがわかる。   FIG. 6 shows that the radial displacement e between the fixed annular race member and the rotary annular race member of the thrust ball bearing is 0.01 mm, 0.02 mm, 0.03 mm, 0.04 mm,. In the case of 05 mm, 0.06 mm, 0.07 mm, 0.08 mm, 0.09 mm, 0.10 mm, 0.11 mm, the result of calculating the relationship between the azimuth angle of the ball and the amount of advance delay is shown. As is apparent from FIG. 6, it can be seen that as the relative displacement amount e in the radial direction increases, the advance and delay of the ball in the cage pocket increases.

図７はスラスト玉軸受の固定側環状レース部材と回転側環状レース部材との間に発生したラジアル方向の相対変位量ｅが０．０１ｍｍ、０．０２ｍｍ、０．０３ｍｍ、０．０４ｍｍ、０．０５ｍｍ、０．０６ｍｍ、０．０７ｍｍ、０．０８ｍｍ、０．０９ｍｍ、０．１０ｍｍ、０．１１ｍｍの場合におけるポケット隙間δと玉直径ｄａとの比をコンピュータにより計算した結果を示しており、図７から明らかなように、ラジアル方向の相対変位量ｅが大きくなると、ポケット隙間δが玉の進み遅れによって大きくなることがわかる。   FIG. 7 shows that the radial relative displacement e generated between the fixed-side annular race member and the rotary-side annular race member of the thrust ball bearing is 0.01 mm, 0.02 mm, 0.03 mm, 0.04 mm,. The results of calculating the ratio between the pocket gap δ and the ball diameter da in the case of 05 mm, 0.06 mm, 0.07 mm, 0.08 mm, 0.09 mm, 0.10 mm, and 0.11 mm by a computer are shown. As can be seen from FIG. 7, as the radial relative displacement amount e increases, the pocket gap δ increases due to the advance and delay of the ball.

ところで、スラスト玉軸受の固定側環状レース部材と回転側環状レース部材との間に発生するラジアル方向の相対変位量ｅがＪＩＳ Ｂ１５１４で規定する寸法許容差（０．０ｍｍ≦ｅ≦０．０１６ｍｍ）内にある場合、玉の進み遅れによって保持器ポケットの周縁部に玉が当接しないようにするためには、ポケット隙間δと玉直径ｄａとの比（δ／ｄａ）を０．０３１以上にしなければならないことが図７に示す計算結果からわかる。また、スラスト玉軸受に作用するラジアル荷重が増大し、相対変位量ｅが０．０１６ｍｍを超える場合も考慮に入れると、δ／ｄａは通常必要とされる０．０３１の２倍から４倍に相当する値に設定することが望ましく、従って、本発明では、ポケット隙間δと玉直径ｄａとの比を０．０６≦δ／ｄａ≦０．１２に設定している。   By the way, the radial relative displacement e generated between the fixed-side annular race member and the rotary-side annular race member of the thrust ball bearing is a dimensional tolerance defined by JIS B1514 (0.0 mm ≦ e ≦ 0.016 mm). In order to prevent the balls from coming into contact with the peripheral edge of the cage pocket due to the advance of the balls, the ratio (δ / da) of the pocket gap δ to the ball diameter da is set to 0.031 or more. It can be seen from the calculation results shown in FIG. In addition, if the radial load acting on the thrust ball bearing is increased and the relative displacement e exceeds 0.016 mm, δ / da is increased from 2 times to 4 times of 0.031 which is usually required. It is desirable to set the corresponding value. Therefore, in the present invention, the ratio between the pocket gap δ and the ball diameter da is set to 0.06 ≦ δ / da ≦ 0.12.

上述のように、ポケット隙間δと玉２５の直径ｄａとの比が０．０６≦δ／ｄａ≦０．１２となるように、ポケット２８の直径ｄａまたは玉２５への加締め力を調整して加締め保持器を設計すれば、玉の進み遅れがポケット２８内で発生しても玉２５がポケット２８の周縁部に当接することがないので、玉の進み遅れに起因する過大な応力がポケット２８の周縁部に発生することを抑制することができる。   As described above, the diameter da of the pocket 28 or the caulking force on the ball 25 is adjusted so that the ratio of the pocket gap δ to the diameter da of the ball 25 is 0.06 ≦ δ / da ≦ 0.12. If the caulking cage is designed, the ball 25 does not come into contact with the peripheral edge portion of the pocket 28 even if the ball advance / delay occurs in the pocket 28, so that excessive stress due to the ball advance / delay is generated. It can suppress generating in the peripheral part of the pocket 28. FIG.

本発明の一実施形態であるスラスト玉軸受の一部を示す断面図である。It is sectional drawing which shows a part of thrust ball bearing which is one Embodiment of this invention. スラスト玉軸受の玉を保持する加締め保持器の一部を示す平面図である。It is a top view which shows a part of crimping holder | retainer holding the ball | bowl of a thrust ball bearing. 図２のIII−III線に沿う断面図である。It is sectional drawing which follows the III-III line of FIG. 加締め保持器の裏面側を示す図であるIt is a figure which shows the back surface side of a caulking cage. スラスト玉軸受にラジアル方向の相対変位が発生したときの玉の方位角と接触角との関係を計算した結果を示す図である。It is a figure which shows the result of having calculated the relationship between the azimuth angle of a ball | bowl when a radial direction relative displacement generate | occur | produced in the thrust ball bearing, and a contact angle. スラスト玉軸受にラジアル方向の相対変位が発生したときの玉の方位角と進み遅れ量との関係を計算した結果を示す図である。It is a figure which shows the result of having calculated the relationship between the azimuth angle of a ball | bowl when the radial direction relative displacement generate | occur | produced in the thrust ball bearing, and the amount of advance delays. スラスト玉軸受にラジアル方向の相対変位が発生したときのラジアル変位量とポケット隙間との関係を計算した結果を示す図である。It is a figure which shows the result of having calculated the relationship between the amount of radial displacement and pocket clearance when the radial direction relative displacement generate | occur | produced in the thrust ball bearing. ボールねじ軸の端部を支持する軸受装置の概略構成を示す図である。It is a figure which shows schematic structure of the bearing apparatus which supports the edge part of a ball screw shaft. 図８の軸受装置に下部軸受として用いられるスラスト玉軸受の一部を示す断面図である。It is sectional drawing which shows a part of thrust ball bearing used as a lower bearing in the bearing apparatus of FIG. スラスト玉軸受の玉を保持する加締め保持器の一部を示す平面図である。It is a top view which shows a part of crimping holder | retainer holding the ball | bowl of a thrust ball bearing. スラスト玉軸受の固定側環状レース部材と回転側環状レース部材との間にラジアル方向の相対変位が発生したときの状態を示す図である。It is a figure which shows a state when the relative displacement of a radial direction generate | occur | produced between the stationary-side annular race member and rotation side annular race member of a thrust ball bearing. 保持器ポケット内で発生する玉の進み遅れを説明するための図である。It is a figure for demonstrating the advance delay of the ball | bowl which generate | occur | produces in a holder | retainer pocket.

符号の説明Explanation of symbols

１ アンギュラ玉軸受
２，２０ スラスト玉軸受
３，２１ 固定側環状レース部材
４，２２ 回転側環状レース部材
５，６，２３，２４ ボール軌道溝
７，２５ 玉
８，２６ 加締め保持器
９，２７ 金属板
１０，２８ ポケット DESCRIPTION OF SYMBOLS 1 Angular contact ball bearing 2,20 Thrust ball bearing 3,21 Fixed side annular race member 4,22 Rotation side annular race member 5,6,23,24 Ball raceway groove 7,25 Ball 8,26 Crimp cage 9,27 Metal plate 10,28 pockets

Claims (4)

回転軸の端部を支持する軸受装置の上部軸受として用いられるラジアル転がり軸受の下部に配置されるスラスト玉軸受の玉を保持するためのポケットを周方向に複数有する加締め保持器の設計方法であって、前記ポケットと前記玉との間の保持器周方向のポケット隙間が所定の値より大きくなるように、前記ポケット隙間を前記回転軸の偏心量の関数として設定して前記加締め保持器を設計することを特徴とするスラスト玉軸受用加締め保持器の設計方法。   A design method of a caulking cage having a plurality of pockets in the circumferential direction for holding balls of a thrust ball bearing arranged at the lower part of a radial rolling bearing used as an upper bearing of a bearing device for supporting an end of a rotating shaft. The cage gap is set as a function of the amount of eccentricity of the rotary shaft so that the pocket gap in the circumferential direction of the cage between the pocket and the ball is larger than a predetermined value. A design method for a caulking cage for a thrust ball bearing, characterized in that: 回転軸の端部を支持する軸受装置の上部軸受として用いられるラジアル転がり軸受の下部に配置されるスラスト玉軸受の玉を保持する複数のポケットを有する加締め保持器であって、前記ポケットと前記玉との間の保持器周方向のポケット隙間をδ、前記玉の直径をｄａとしたとき、前記ポケット隙間と前記玉の直径との比が０．０６≦δ／ｄａ≦０．１２であることを特徴とするスラスト玉軸受用加締め保持器。   A caulking cage having a plurality of pockets for holding balls of a thrust ball bearing disposed as a lower part of a radial rolling bearing used as an upper bearing of a bearing device that supports an end of a rotating shaft, the pocket and the pocket When the pocket clearance in the cage circumferential direction between the balls is δ and the diameter of the balls is da, the ratio of the pocket clearance to the diameter of the balls is 0.06 ≦ δ / da ≦ 0.12. A caulking cage for a thrust ball bearing characterized by that. 前記ポケット隙間と前記玉の直径との比が０．０６≦δ／ｄａ≦０．１２となるように、前記ポケットの直径または前記玉への加締め力を調整してなることを特徴とする請求項２記載のスラスト玉軸受用加締め保持器。   The pocket diameter or the caulking force on the ball is adjusted so that the ratio of the pocket gap to the ball diameter is 0.06 ≦ δ / da ≦ 0.12. A thrust cage for a ball bearing according to claim 2. 請求項２または請求項３記載の加締め保持器を備えたことを特徴とするスラスト玉軸受。   A thrust ball bearing comprising the caulking cage according to claim 2.
JP2005365976A 2005-12-20 2005-12-20 Caulked retainer for thrust ball bearing, its design method, and thrust ball bearing Pending JP2007170465A (en)

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2009185983A (en) * 2008-02-08 2009-08-20 Ntn Corp Metal holder
WO2013031249A1 (en) * 2011-08-29 2013-03-07 日本精工株式会社 Thrust bearing

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2009185983A (en) * 2008-02-08 2009-08-20 Ntn Corp Metal holder
WO2013031249A1 (en) * 2011-08-29 2013-03-07 日本精工株式会社 Thrust bearing
US8870465B2 (en) 2011-08-29 2014-10-28 Nsk Ltd. Thrust bearing

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