JP2008224026A - Rolling bearing and its cage - Google Patents

Rolling bearing and its cage Download PDF

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Publication number
JP2008224026A
JP2008224026A JP2007205468A JP2007205468A JP2008224026A JP 2008224026 A JP2008224026 A JP 2008224026A JP 2007205468 A JP2007205468 A JP 2007205468A JP 2007205468 A JP2007205468 A JP 2007205468A JP 2008224026 A JP2008224026 A JP 2008224026A
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Prior art keywords
groove
outer ring
raceway groove
cage
ring raceway
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JP2007205468A
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Japanese (ja)
Inventor
Toshiaki Seto
敏明 瀬戸
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NSK Ltd
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NSK Ltd
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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16CSHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30Parts of ball or roller bearings
    • F16C33/38Ball cages
    • F16C33/41Ball cages comb-shaped
    • F16C33/418Details of individual pockets, e.g. shape or ball retaining means
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16CSHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14Bearings 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
    • F16C19/18Bearings 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 two or more rows of balls
    • F16C19/181Bearings 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 two or more rows of balls with angular contact
    • F16C19/183Bearings 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 two or more rows of balls with angular contact with two rows at opposite angles
    • F16C19/184Bearings 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 two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16CSHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2240/00Specified values or numerical ranges of parameters; Relations between them
    • F16C2240/40Linear dimensions, e.g. length, radius, thickness, gap
    • F16C2240/70Diameters; Radii
    • F16C2240/76Osculation, i.e. relation between radii of balls and raceway groove

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

Abstract

<P>PROBLEM TO BE SOLVED: To provide a rolling bearing cage having high axial load property and moment resistant property for preventing the noises of the cage or the deformation and breakage of the cage, and to provide a rolling bearing. <P>SOLUTION: The rolling bearing 1 comprises an annular outer ring 3 having outer ring raceway grooves 19, 21 in the inner peripheral face, an annular inner ring 5 arranged concentrically with the outer ring inward in the radial direction and having inner ring raceway grooves 23, 25 in the outer peripheral face, a plurality of rolling elements 7, 9 for rolling between the outer ring raceway groove and the inner ring raceway groove, and the cages 15, 17 each having a recessed portion for rollingly storing the plurality of rolling elements at equal spaces in the peripheral direction, and a pawl portion for holding the rolling elements in the recessed portion. Groove shoulders 31, 35, 33, 27, 41, 39 at both ends of the raceway grooves are different in height, and the pawl portion of the cage is inclined at a predetermined angle δ to the axial direction so as to tend toward the lower groove shoulder. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

本発明は、外輪軌道溝と内輪軌道溝との間で転動する複数の転動体を有する転がり軸受及び転がり軸受用保持器の改良に関する。   The present invention relates to an improvement in a rolling bearing having a plurality of rolling elements that roll between an outer ring raceway groove and an inner ring raceway groove, and a rolling bearing retainer.

従来より、アキシアル負荷能力や耐モーメント性が要求されるポンプやコンプレッサ等の転がり軸受として、複列アンギュラ玉軸受が利用されている。図3、図4を参照して、従来の複列アンギュラ玉軸受について説明する。図3は、従来の複列アンギュラ転がり軸受の一部を示す縦方向断面図である。図4は、図3に示される保持器の斜視図である。   Conventionally, double row angular contact ball bearings have been used as rolling bearings for pumps, compressors and the like that require axial load capacity and moment resistance. A conventional double-row angular contact ball bearing will be described with reference to FIGS. 3 and 4. FIG. 3 is a longitudinal sectional view showing a part of a conventional double-row angular rolling bearing. FIG. 4 is a perspective view of the cage shown in FIG.

複列アンギュラ玉軸受101は、外輪103、内輪105、2列で配列される複数の転動体107、109と、転動体107、109を保持する2つの保持器115、117と、を備える。外輪103の内周面には、2列の外輪軌道溝119、121が設けられ、内輪105の外周面には、2列の内輪軌道溝123、125が設けられている。また、転動体107、109は、それぞれ保持器115、117のポケット127内で転動可能に収容されている。   The double-row angular ball bearing 101 includes an outer ring 103, an inner ring 105, a plurality of rolling elements 107, 109 arranged in two rows, and two cages 115, 117 that hold the rolling elements 107, 109. Two rows of outer ring raceway grooves 119 and 121 are provided on the inner peripheral surface of the outer ring 103, and two rows of inner ring raceway grooves 123 and 125 are provided on the outer peripheral surface of the inner ring 105. Moreover, the rolling elements 107 and 109 are accommodated in the pockets 127 of the holders 115 and 117, respectively, so that they can roll.

図3に示されるように、複列アンギュラ玉軸受101は、径方向に関し左右対称の構造を呈しているので、図中右方に位置する構成要素について説明する。外輪103の外輪軌道溝119の軸方向で内方に配置される内方溝肩135の溝肩高さI1は軸方向で外方に配置される外方溝肩131の溝肩高さI0よりも高くなっている。また、内輪105の内輪軌道溝123の軸方向で外方に配置される外方溝肩137の溝肩高さi0は、軸方向で内方に配置される内方溝肩141の溝肩高さi1よりも高くなっている。このように、軸受の一方の作用線y1が、径方向に対して所定角度(接触角e)だけ傾斜する構成である。   As shown in FIG. 3, the double-row angular ball bearing 101 has a symmetrical structure with respect to the radial direction, so the components located on the right side in the figure will be described. The groove shoulder height I1 of the inner groove shoulder 135 disposed inward in the axial direction of the outer ring raceway groove 119 of the outer ring 103 is greater than the groove shoulder height I0 of the outer groove shoulder 131 disposed outward in the axial direction. Is also high. Also, the groove shoulder height i0 of the outer groove shoulder 137 disposed outward in the axial direction of the inner ring raceway groove 123 of the inner ring 105 is the groove shoulder height of the inner groove shoulder 141 disposed inward in the axial direction. It is higher than i1. Thus, one action line y1 of the bearing is configured to be inclined by a predetermined angle (contact angle e) with respect to the radial direction.

図4の保持器115の爪部143は、所定寸法の厚さ129を有し、複列アンギュラ玉軸受101の軸方向(図1中の水平方向)に延びる。そして、爪部143の厚さ129は、外輪103の内方溝肩135、外方溝肩131、内輪105の内方溝肩141、外方溝肩137に接触しないように寸法付けされている。   4 has a predetermined thickness 129 and extends in the axial direction of the double-row angular ball bearing 101 (horizontal direction in FIG. 1). The thickness 129 of the claw 143 is dimensioned so as not to contact the inner groove shoulder 135, the outer groove shoulder 131 of the outer ring 103, the inner groove shoulder 141 of the inner ring 105, and the outer groove shoulder 137. .

他方、図3中において軸受101の左側の構成要素である外輪103の外輪軌道溝121、内輪105の内輪軌道溝125、外輪103の外方溝肩133及び内方溝肩135、内輪105の外方溝肩139及び内方溝肩141は、前述したように、右側の構成要素と径方向に関し左右対称の位置関係である。軸受101のもう一方の作用線y2は、径方向に対して接触角f(角度−e)を有する。従って、複列アンギュラ玉軸受101は、単列アンギュラ玉軸受を背面同士で連結した構成と同等である(例えば、特許文献1参照。)。
特開2001−59523(図1等)
On the other hand, in FIG. 3, the outer ring raceway groove 121 of the outer ring 103, the inner ring raceway groove 125 of the inner ring 105, the outer groove shoulder 133 and the inner groove shoulder 135 of the outer ring 103, which are the left side components of the bearing 101. As described above, the lateral groove shoulder 139 and the inward groove shoulder 141 have a symmetric positional relationship with the right component in the radial direction. The other action line y2 of the bearing 101 has a contact angle f (angle −e) with respect to the radial direction. Accordingly, the double-row angular contact ball bearing 101 is equivalent to a configuration in which single-row angular contact ball bearings are connected to each other on the back (see, for example, Patent Document 1).
JP 2001-59523 (FIG. 1 etc.)

特許文献1に開示されるように、従来の複列アンギュラ玉軸受において、モーメント荷重が保持器に掛かる場合、同一軌道上に複数配列される転動体それぞれに対する接触角eが異なる。結果として、複数の転動体各々に速度差が生じ、保持器に対して転動体による引っ張り応力や圧縮応力が掛かる場合がある。   As disclosed in Patent Document 1, in the conventional double-row angular contact ball bearing, when a moment load is applied to the cage, the contact angles e with respect to each of a plurality of rolling elements arranged on the same track are different. As a result, a speed difference is generated in each of the plurality of rolling elements, and tensile stress or compressive stress by the rolling elements may be applied to the cage.

従って、アキシアル負荷能力や耐モーメント性の観点からは、鉄製の保持器を使用することが考えられる。しかし、軽量化、低騒音化、焼付き寿命の観点からは、プラスチック製の保持器を使用することが望ましい。   Therefore, it is conceivable to use an iron cage from the viewpoint of axial load capacity and moment resistance. However, it is desirable to use a plastic cage from the viewpoint of weight reduction, noise reduction, and seizure life.

また、アンギュラ玉軸受を設計する際には、アンギュラ玉軸受が受けるアキシャル負荷及びモーメント荷重に応じて、外輪の内方溝肩、外方溝肩及び内輪の内方溝肩、外方溝肩の溝高さを考慮する必要がある。また、保持器についても、アキシャル負荷及びモーメント荷重に応じて設計するとともに、保持器の水平に伸びる爪部の厚さは、外輪の内方溝肩と内輪の外方溝肩に接触しないように寸法付けする必要がある。従って、保持器をプラスチック製とした場合には、保持器の厚さを十分にとれずに、必要な剛性を得られず、保持器音の発生、保持器の変形、破損の恐れがある。また、保持器の剛性を確保すべく、保持器の爪部の厚さを設計すると、複列アンギュラ玉軸受全体の寸法を大きくする必要が生じることも考えられる。   Also, when designing angular contact ball bearings, the inner ring shoulder of the outer ring, the outer groove shoulder of the outer ring, the inner groove shoulder of the inner ring, and the outer groove shoulder of the inner ring according to the axial load and moment load received by the angular ball bearing. It is necessary to consider the groove height. In addition, the cage is designed according to the axial load and moment load, and the thickness of the claw that extends horizontally in the cage should not touch the inner groove shoulder of the outer ring and the outer groove shoulder of the inner ring. Need to be dimensioned. Therefore, when the cage is made of plastic, the cage is not sufficiently thick and the required rigidity cannot be obtained, and there is a risk of cage noise generation, cage deformation, and damage. Moreover, if the thickness of the claw portion of the cage is designed to ensure the rigidity of the cage, it may be necessary to increase the overall size of the double-row angular ball bearing.

そこで、本発明は、高アキシアル負荷特性及び耐モーメント特性を確保し、保持器音の発生や保持器の変形及び破損を防止できる転がり軸受用保持器及び転がり軸受を提供することを目的とする。   SUMMARY OF THE INVENTION Accordingly, an object of the present invention is to provide a rolling bearing cage and a rolling bearing that can secure high axial load characteristics and moment resistance characteristics, and can prevent generation of cage noise and deformation and breakage of the cage.

上記課題を解決するために、本発明による転がり軸受は、内周面に外輪軌道溝を有する環状の外輪と、前記外輪の径方向内方で同心に配置され、外周面に内輪軌道溝を有する環状の内輪と、前記外輪軌道溝と前記内輪軌道溝との間で転動する複数の転動体と、前記複数の転動体を周方向に等間隔で転動可能に収容する凹部と、前記凹部内に前記転動体を保持する爪部と、を有する保持器と、を備え、前記各軌道溝の両端の溝肩は溝肩高さが異なり、前記保持器の爪部が前記溝肩高さの低い溝肩に向かうように軸方向に関し所定角度で傾斜していることを特徴とする転がり軸受。   In order to solve the above problems, a rolling bearing according to the present invention has an annular outer ring having an outer ring raceway groove on an inner peripheral surface, and is arranged concentrically radially inward of the outer ring, and has an inner ring raceway groove on an outer peripheral surface. An annular inner ring, a plurality of rolling elements that roll between the outer ring raceway groove and the inner ring raceway groove, a recess that accommodates the plurality of rolling elements in a circumferential direction so as to allow rolling, and the recess A retainer having a claw portion for holding the rolling element therein, groove shoulder heights at both ends of each raceway groove are different, and the claw portion of the retainer has a groove shoulder height. A rolling bearing characterized by being inclined at a predetermined angle with respect to the axial direction so as to be directed to a low shoulder of the groove.

上記転がり軸受は、前記外輪軌道溝及び前記内輪軌道溝が、軸方向に複列に配置され、2列の転動体を保持する2つの保持器を有する複列アンギュラ玉軸受又は前記外輪軌道溝及び前記内輪軌道溝が単列に配置される単列アンギュラ玉軸受であることが好ましい。   In the rolling bearing, the outer ring raceway groove and the inner ring raceway groove are arranged in a double row in the axial direction, and the double row angular contact ball bearing or the outer ring raceway groove having two cages for holding two rows of rolling elements, and It is preferable that the inner ring raceway groove is a single row angular contact ball bearing in which the inner ring raceway grooves are arranged in a single row.

上記転がり軸受において前記内輪軌道溝及び前記外輪軌道溝の少なくとも一方の溝半径(r’)と前記玉部材の直径(D)との半径比(r’/D)が52%以下であることが好ましい。これにより、内輪軌道溝及び/又は外輪軌道溝において玉部材と接触する面積が大きくなり、軌道溝上の応力が小さくなるので、軸受の高負荷化を実現できる。   In the rolling bearing, a radius ratio (r ′ / D) between a groove radius (r ′) of at least one of the inner ring raceway groove and the outer ring raceway groove and a diameter (D) of the ball member may be 52% or less. preferable. As a result, the area of the inner ring raceway groove and / or outer ring raceway groove that comes into contact with the ball member is increased, and the stress on the raceway groove is reduced, so that a high load on the bearing can be realized.

また、前記潤滑剤としてグリースを充填し、前記グリースの調度(グリースの粘度を示す指標)が200乃至280の範囲内にあることが好ましい。   In addition, it is preferable that grease is filled as the lubricant, and the condition of the grease (an index indicating the viscosity of the grease) is in the range of 200 to 280.

本発明による転がり軸受用保持器は、内周面に外輪軌道溝を有する環状の外輪と、前記外輪の径方向内方で同心に配置され、外周面に内輪軌道溝を有する内輪と、前記外輪軌道溝と前記内輪軌道溝との間で転動する複数の転動体と、前記複数の転動体を周方向に等間隔で転動可能に収容する凹部と前記凹部内に前記転動体を保持する爪部とを有する保持器と、を備え、前記各軌道溝の両端の溝肩の溝肩高さが異なる転がり軸受のための前記保持器であって、前記保持器の爪部が前記溝肩高さの低い溝肩に向かうように軸方向に関し所定角度で傾斜していることを特徴とする。   A rolling bearing retainer according to the present invention includes an annular outer ring having an outer ring raceway groove on an inner peripheral surface, an inner ring having an inner ring raceway groove on an outer peripheral surface, concentrically disposed radially inward of the outer ring, and the outer ring. A plurality of rolling elements that roll between the raceway groove and the inner ring raceway groove, a recess that accommodates the plurality of rolling elements in a circumferential direction so as to be capable of rolling at equal intervals, and the rolling element is held in the recess. A cage having a claw portion, and the cage for a rolling bearing having different groove shoulder heights at both ends of each raceway groove, wherein the claw portion of the cage has the groove shoulder. It is characterized in that it is inclined at a predetermined angle with respect to the axial direction so as to be directed to the groove shoulder having a low height.

本発明によれば、保持器の爪部が溝肩高さの低い溝肩に向かい、軸方向に関し所定角度で傾斜しているので、軸方向に平行に延びる爪部と比べ、爪部と溝肩との干渉が抑えられ、爪部の厚さの設計の自由度が広がる。よって、モーメント荷重による引っ張り応力及び圧縮応力に耐えられ、保持器音の発生や、変形、破損を防止できる、高アキシアル負荷特性、及び耐モーメント特性を備える転がり軸受及び転がり軸受用保持器を提供することができる。   According to the present invention, since the claw portion of the cage faces the groove shoulder having a low groove shoulder height and is inclined at a predetermined angle with respect to the axial direction, the claw portion and the groove are compared with the claw portion extending parallel to the axial direction. Interference with the shoulder is suppressed, and the degree of freedom in designing the nail thickness is expanded. Therefore, the present invention provides a rolling bearing and a rolling bearing retainer having high axial load characteristics and moment resistance characteristics that can withstand tensile stress and compressive stress due to moment load, and can prevent generation, deformation, and breakage of cage noise. be able to.

以下、本発明の転がり軸受を複列アンギュラ玉軸受に適用した実施形態について図面を参照しつつ説明する。各図面中、同一要素は同一符号で示してある。   Hereinafter, an embodiment in which the rolling bearing of the present invention is applied to a double-row angular ball bearing will be described with reference to the drawings. In the drawings, the same elements are denoted by the same reference numerals.

〈第1の実施形態〉   <First Embodiment>

第1の実施形態である複列アンギュラ玉軸受について、図1、図2を参照しつつ説明する。図1は、第1の実施形態による複列アンギュラ玉軸受の一部を軸方向に沿った断面で示す図である。図2は、図1に示される保持器の斜視図である。   The double row angular contact ball bearing which is 1st Embodiment is demonstrated referring FIG. 1, FIG. FIG. 1 is a view showing a part of the double-row angular contact ball bearing according to the first embodiment in a cross section along the axial direction. FIG. 2 is a perspective view of the cage shown in FIG.

図1に示されるように、複列アンギュラ玉軸受1は、環状の外輪3、外輪3の径方向内方であって、外輪3と同心で相対回転可能に配置される環状の内輪5と、外輪3と内輪5との間で複列に複数配置される転動体すなわち玉部材7、9と、玉部材7、9を回転可能に保持する一対の保持器15、17と、を備える。   As shown in FIG. 1, the double-row angular contact ball bearing 1 includes an annular outer ring 3, a radially inner side of the outer ring 3, an annular inner ring 5 that is concentrically arranged with the outer ring 3 and is relatively rotatable. A plurality of rolling elements or ball members 7 and 9 arranged in a double row between the outer ring 3 and the inner ring 5 and a pair of cages 15 and 17 that hold the ball members 7 and 9 rotatably are provided.

外輪3の内周面には、周方向に延在する2つの凹部すなわち外輪軌道溝19、21が設けられている。同様に、内輪5の外周面には、周方向に延在する2つの凹部すなわち内輪軌道溝23、25が設けられている。外輪軌道溝19と内輪軌道溝23により形成される第1軌道24、そして、外輪軌道溝21と内輪軌道溝25により形成される第2軌道26にはそれぞれ複数の玉部材7、9が転動可能に配置される。また、各軌道溝19、21、23、25の曲率半径は、玉部材7、9の曲率半径より若干大きく寸法付けされている。従って、玉部材7が第1軌道24を転動し、玉部材9が第2軌道26を転動する。このように、玉部材9により外輪3と内輪5は、相対回転可能な構成となっている。   On the inner peripheral surface of the outer ring 3, two concave portions extending in the circumferential direction, that is, outer ring raceway grooves 19 and 21 are provided. Similarly, on the outer peripheral surface of the inner ring 5, two concave portions extending in the circumferential direction, that is, inner ring raceway grooves 23 and 25 are provided. A plurality of ball members 7 and 9 roll on the first track 24 formed by the outer ring raceway groove 19 and the inner ring raceway groove 23 and on the second raceway 26 formed by the outer ring raceway groove 21 and the inner ring raceway groove 25, respectively. Arranged as possible. Further, the radius of curvature of each raceway groove 19, 21, 23, 25 is slightly larger than the radius of curvature of the ball members 7, 9. Therefore, the ball member 7 rolls on the first track 24, and the ball member 9 rolls on the second track 26. Thus, the outer ring 3 and the inner ring 5 are configured to be relatively rotatable by the ball member 9.

さらに第1軌道24を構成する部材及びその周辺要素について説明する。外輪軌道溝19の軸方向両端には、外方溝肩31と内方溝肩35が形成されている。外方溝肩31の溝肩高さH0は、内方溝肩35の溝肩高さH1より低く寸法付けされている。他方、内輪軌道溝23の軸方向両端には、外方溝肩27と内方溝肩41が形成されている。外方溝肩27の溝肩高さh0は、内方溝肩41の溝肩高さh1より高く寸法付けされている。ここで、溝肩高さとは、軌道溝の最底部から溝肩の最上面までの軸受の径方向距離である。   Further, members constituting the first track 24 and peripheral elements thereof will be described. An outer groove shoulder 31 and an inner groove shoulder 35 are formed at both axial ends of the outer ring raceway groove 19. The groove shoulder height H 0 of the outer groove shoulder 31 is dimensioned lower than the groove shoulder height H 1 of the inner groove shoulder 35. On the other hand, an outer groove shoulder 27 and an inner groove shoulder 41 are formed at both axial ends of the inner ring raceway groove 23. The groove shoulder height h 0 of the outer groove shoulder 27 is dimensioned higher than the groove shoulder height h 1 of the inner groove shoulder 41. Here, the groove shoulder height is the radial distance of the bearing from the bottom of the raceway groove to the top surface of the groove shoulder.

また、作用線Y1は、図中の径方向線X1に対して接触角aで交差し、径方向内方に向かうに従い転がり軸受1から離れるように延びている。したがって、内方溝肩35、外方溝肩27は負荷を受ける側である。   In addition, the action line Y1 intersects the radial line X1 in the figure at a contact angle a and extends away from the rolling bearing 1 as it goes radially inward. Therefore, the inner groove shoulder 35 and the outer groove shoulder 27 are on the side receiving the load.

また、第2の軌道26を構成する外輪軌道溝21、内輪軌道溝25、及び保持器17は、上記した外輪軌道溝19、内輪軌道溝23及び保持器15と、図1の径方向中心線x’に関して左右対称の位置関係となっている。したがって、作用線Y2は、径方向線X2に対して接触角bで交差し、径方向内方に向かうに従い転がり軸受1から離れるように延びている。したがって、内方溝肩35、外方溝肩39は負荷を受ける側である。また、接触角bとaの傾きは互いに逆向きであるが、角度の大きさは互いに等しい。   Further, the outer ring raceway groove 21, the inner ring raceway groove 25, and the cage 17 constituting the second raceway 26 are the same as the outer ring raceway groove 19, the inner ring raceway groove 23, the cage 15 and the radial center line of FIG. The positional relationship is symmetrical with respect to x ′. Accordingly, the action line Y2 intersects the radial line X2 at the contact angle b, and extends away from the rolling bearing 1 as it goes inward in the radial direction. Therefore, the inner groove shoulder 35 and the outer groove shoulder 39 are on the side receiving the load. The inclinations of the contact angles b and a are opposite to each other, but the magnitudes of the angles are equal to each other.

次に、保持器について詳述する。樹脂製の保持器15、17は、同一形状で同一寸法であり、異なるのは配置される向きである。よって、保持器15についてのみ図2を参照して説明する。保持器15は、環状の主部15aと、主部15aから軸方向に対して所定角度δで上方に突出し、周方向に等間隔に凹部であるポケット18が形成された柱部15bと、柱部15bに連続しポケット18の両端から突出し玉部材7をポケット18内に保持するための爪部15cと、を備える。爪部15cの玉部材7に当接する湾曲面は、ポケット18を構成する湾曲面とほぼ同じ曲率半径を有しおり、互いに滑らかに連続している。上記構成において、ポケット18を介して対向配置される一対の爪部15cを互いに離れる方向に撓ませることで、玉部材7はポケット18内に装着される。   Next, the cage will be described in detail. The resin cages 15 and 17 have the same shape and the same dimensions, and the difference is the direction in which they are arranged. Therefore, only the cage 15 will be described with reference to FIG. The retainer 15 includes an annular main portion 15a, a column portion 15b that protrudes upward from the main portion 15a at a predetermined angle δ with respect to the axial direction, and pockets 18 that are recessed portions at equal intervals in the circumferential direction. A claw portion 15c that is continuous with the portion 15b and protrudes from both ends of the pocket 18 to hold the ball member 7 in the pocket 18. The curved surfaces in contact with the ball member 7 of the claw portion 15c have substantially the same radius of curvature as the curved surfaces constituting the pocket 18, and are smoothly continuous with each other. In the above-described configuration, the ball member 7 is mounted in the pocket 18 by bending the pair of claw portions 15c arranged to face each other via the pocket 18 in a direction away from each other.

また、保持器15の主部15a、柱部15b、爪部15cの外周面は、回転軸線に平行な線Lに対して角度δを有し傾斜している。すなわち、保持器15は、爪部15cの先端に向かい縮径する構成である。   Further, the outer peripheral surfaces of the main portion 15a, the column portion 15b, and the claw portion 15c of the cage 15 are inclined with an angle δ with respect to the line L parallel to the rotation axis. That is, the cage 15 is configured to reduce in diameter toward the tip of the claw portion 15c.

図1、図2の複列アンギュラ玉軸受1によれば、上記のように保持器15の外周面を傾斜させることにより、外輪3の内周面と内輪5の外周面とにより形成され環状空間内に凹凸が存在しても、保持器15の主部15a、柱部15b、爪部15cの厚さ29を最大の寸法とすることができる。   According to the double-row angular ball bearing 1 of FIGS. 1 and 2, an annular space is formed by the inner peripheral surface of the outer ring 3 and the outer peripheral surface of the inner ring 5 by inclining the outer peripheral surface of the cage 15 as described above. Even if there are irregularities inside, the thickness 29 of the main portion 15a, the column portion 15b, and the claw portion 15c of the cage 15 can be set to the maximum dimension.

すなわち、従来の保持器(図3参照)では、保持器の柱部、爪部が回転軸に対して平行に延在していたので、外輪の内方溝肩135と内輪の外方溝肩137が、保持器と接触しない程度の寸法にする必要があり、設計の自由度が狭かった。しかし、本実施形態の保持器15のように、保持器15の主部15a、柱部15b、爪部15cを傾斜させることにより、保持器15の厚さ29(図1)を従来の保持器(図3参照)より大きくしても、保持器15が外輪3の内方溝肩35と内輪5の外方溝肩27とに対し接触し干渉しないので、保持器15,17についての寸法設計の自由度を格段に広げることができる。   That is, in the conventional cage (see FIG. 3), since the pillar portion and the claw portion of the cage extend in parallel to the rotation axis, the inner groove shoulder 135 of the outer ring and the outer groove shoulder of the inner ring 137 had to be dimensioned so as not to contact the cage, and the degree of freedom in design was narrow. However, as in the cage 15 of the present embodiment, the main portion 15a, the column portion 15b, and the claw portion 15c of the cage 15 are inclined so that the thickness 29 (FIG. 1) of the cage 15 is reduced. Even if it is larger (see FIG. 3), the cage 15 does not contact and interfere with the inner groove shoulder 35 of the outer ring 3 and the outer groove shoulder 27 of the inner ring 5, so that the dimensions of the cages 15 and 17 are designed. Can be greatly expanded.

したがって、保持器15,17をプラスチック製とした場合でも、保持器の厚さ29を十分に確保でき、必要な剛性を得ることができるので、保持器音の発生、保持器の変形、破損の恐れを防止することができる。また、複列アンギュラ玉軸受全体の寸法を大きくする必要も生じない。   Therefore, even when the cages 15 and 17 are made of plastic, the cage thickness 29 can be sufficiently secured and necessary rigidity can be obtained. Fear can be prevented. Moreover, it is not necessary to increase the overall dimensions of the double-row angular contact ball bearing.

また、アンギュラ玉軸受及び保持器についてアキシャル負荷及びモーメント荷重に応じて設計する際に、外輪3の内方溝肩35、外方溝肩31,33の各溝高さ及び内輪5の内方溝肩41、外方溝肩27,39の各溝高さの寸法設計自由度が広がるとともに、保持器の厚さ等の寸法設計自由度が広がるので、アンギュラ玉軸受における高アキシアル負荷特性及び耐モーメント特性を確保することができる。   Further, when designing the angular ball bearing and the cage according to the axial load and the moment load, the inner groove shoulder 35 of the outer ring 3, the groove heights of the outer groove shoulders 31 and 33, and the inner groove of the inner ring 5. The degree of freedom in dimensional design for each groove height of the shoulder 41 and the outer groove shoulders 27 and 39 is widened, and the degree of freedom in dimensional design such as the thickness of the cage is widened. Therefore, high axial load characteristics and moment resistance in angular ball bearings Characteristics can be secured.

上記実施形態では、外輪の外方溝肩の高さを外輪の内方溝肩の高さより低くし、内輪の外方溝肩の高さを内輪の内方溝肩の高さより高くする構成としたが、本発明はこの構成に限定されるものではない。例えば、外輪の外方溝肩の高さを外輪の内方溝肩の高さより高くし、内輪の外方溝肩の高さを内輪の内方溝肩の高さより低くする構成でもよい。このような転がり軸受の場合には、保持器の外周面、すなわち主部、柱部、爪部の外周面を線Lに対して角度−δだけ傾けたような形状となる。すなわち、保持器は、爪部の先端に向かうに従い拡開する構成である。   In the above embodiment, the height of the outer groove shoulder of the outer ring is lower than the height of the inner groove shoulder of the outer ring, and the height of the outer groove shoulder of the inner ring is higher than the height of the inner groove shoulder of the inner ring; However, the present invention is not limited to this configuration. For example, the height of the outer groove shoulder of the outer ring may be higher than the height of the inner groove shoulder of the outer ring, and the height of the outer groove shoulder of the inner ring may be lower than the height of the inner groove shoulder of the inner ring. In the case of such a rolling bearing, the outer peripheral surface of the cage, that is, the outer peripheral surfaces of the main portion, the column portion, and the claw portion is inclined with respect to the line L by an angle −δ. In other words, the cage is configured to expand toward the tip of the claw portion.

本実施形態では、主部、柱部、爪部の全てを所定角度δだけ傾ける構成としたが、この角度は、外輪及び内輪の外方溝肩、内方溝肩との寸法、形状とにより適宜変更できることは言うまでもない。また、主部、柱部、爪部の何れか1つ若しくは2つのみを傾斜させる構成としてもよい。   In the present embodiment, all of the main part, the column part, and the claw part are inclined by a predetermined angle δ, but this angle depends on the outer groove shoulder of the outer ring and the inner ring, and the dimensions and shape of the inner groove shoulder. Needless to say, it can be changed as appropriate. Moreover, it is good also as a structure which inclines only any one or two of a main part, a pillar part, and a nail | claw part.

〈第2の実施形態〉   <Second Embodiment>

図5は、第2の実施形態による単列アンギュラ玉軸受(半径比が52%以下の場合の各軌道輪と玉部材を示す)の断面図(a)及び従来のラジアル玉軸受(半径比が52%を超えた場合の各軌道輪と玉部材を示す)の断面図(b)である。なお、図5では説明の便宜上、保持器の図示を省略している。   FIG. 5 is a cross-sectional view (a) of a single row angular contact ball bearing (showing each ring and ball member when the radius ratio is 52% or less) according to the second embodiment and a conventional radial ball bearing (radius ratio is It is sectional drawing (b) of each track ring and ball member when it exceeds 52%. In FIG. 5, for convenience of explanation, the cage is not shown.

図5(a)に示すように、本実施の形態による単列アンギュラ玉軸受50は、外輪軌道溝51を有する外輪52と、内輪軌道溝53を有する内輪54と、複数個の玉部材55と、各玉部材55を各ポケット18内に転動自在に均等位置に保持する保持器15(図2)と、を備え、内輪軌道溝53と外輪軌道溝51との間に複数個の玉部材55を転動自在に配置したものである。   As shown in FIG. 5A, a single row angular contact ball bearing 50 according to the present embodiment includes an outer ring 52 having an outer ring raceway groove 51, an inner ring 54 having an inner ring raceway groove 53, and a plurality of ball members 55. And a cage 15 (FIG. 2) for holding each ball member 55 in each pocket 18 at a uniform position so as to roll freely, and a plurality of ball members between the inner ring raceway groove 53 and the outer ring raceway groove 51. 55 is arranged to roll freely.

外輪軌道溝51の軸方向両端には溝肩52aと溝肩52bが形成され、溝肩52bが溝肩52aよりも高くなっている。内輪軌道溝53の軸方向両端には、溝肩54aと溝肩54bが形成され、溝肩54aが溝肩54bよりも高くなっている。なお、作用線Yは、径方向線Xに対して接触角mで交差し、溝肩52b及び溝肩54aが負荷を受ける側である。   Groove shoulders 52a and 52b are formed at both axial ends of the outer ring raceway groove 51, and the groove shoulder 52b is higher than the groove shoulder 52a. A groove shoulder 54a and a groove shoulder 54b are formed at both axial ends of the inner ring raceway groove 53, and the groove shoulder 54a is higher than the groove shoulder 54b. The action line Y intersects the radial line X at the contact angle m, and the groove shoulder 52b and the groove shoulder 54a are on the side receiving the load.

また、図5(a)の単列アンギュラ玉軸受50において、内輪54の内輪軌道溝53は、溝半径r53を有する溝状となっており、溝半径r53と玉部材55の直径Dとの半径比 (r53/D)が52%以下である。同様に、外輪52の外輪軌道溝51は、溝半径r51を有する溝状となっており、溝半径r51と玉部材55の直径Dとの半径比 (r51/D)が52%以下である。   5A, the inner ring raceway groove 53 of the inner ring 54 has a groove shape having a groove radius r53, and the radius between the groove radius r53 and the diameter D of the ball member 55. In the single-row angular contact ball bearing 50 of FIG. The ratio (r53 / D) is 52% or less. Similarly, the outer ring raceway groove 51 of the outer ring 52 has a groove shape having a groove radius r51, and the radius ratio (r51 / D) between the groove radius r51 and the diameter D of the ball member 55 is 52% or less.

上述のように、本実施の形態による単列アンギュラ玉軸受50では、内輪54の内輪軌道溝53の溝半径r53及び外輪52の外輪軌道溝51の溝半径r51と玉部材55の直径との各半径比(r53/D,r51/D)を、図5(b)のような従来の場合に適用される52%よりも小さくすることで、玉部材55が接触する軌道溝51,53の溝上の応力を小さくしている。   As described above, in the single row angular contact ball bearing 50 according to the present embodiment, the groove radius r53 of the inner ring raceway groove 53 of the inner ring 54, the groove radius r51 of the outer ring raceway groove 51 of the outer ring 52, and the diameter of the ball member 55 are set. By making the radius ratio (r53 / D, r51 / D) smaller than 52% applied in the conventional case as shown in FIG. 5 (b), on the grooves of the raceway grooves 51, 53 with which the ball member 55 contacts. The stress is reduced.

すなわち、図5(b)の従来の場合は内輪軌道溝63の溝半径r63と玉部材55の直径Dとの半径比 (r63/D)が52%を超え、同様に外輪軌道溝61の溝半径r61と玉部材55の直径Dとの半径比 (r61/D)が52%を超える。このため、各軌道溝61,63において玉部材55と接触する面積が小さくなることから、各軌道溝61,63の溝上の応力が大きくなってしまうのに対し、本実施の形態の図5(a)によれば、各半径比(r53/D,r51/D)が52%以下であり、内輪軌道溝53及び外輪軌道溝51において玉部材55と接触する面積が大きくなることから、軌道溝51,53の溝上の応力が小さくなる。このため、本実施の形態の単列アンギュラ玉軸受50は、適用される軸受装置において高い負荷が可能となって高負荷化を達成できる。   5B, the radius ratio (r63 / D) between the groove radius r63 of the inner ring raceway groove 63 and the diameter D of the ball member 55 exceeds 52%. Similarly, the groove of the outer ring raceway groove 61 The radius ratio (r61 / D) between the radius r61 and the diameter D of the ball member 55 exceeds 52%. For this reason, since the area which contacts the ball member 55 in each track groove 61 and 63 becomes small, the stress on the groove of each track groove 61 and 63 will become large, whereas FIG. According to a), each radius ratio (r53 / D, r51 / D) is 52% or less, and the area in contact with the ball member 55 in the inner ring raceway groove 53 and the outer ring raceway groove 51 is increased. The stress on the grooves 51 and 53 is reduced. For this reason, the single-row angular contact ball bearing 50 of the present embodiment enables a high load in the applied bearing device and can achieve a high load.

また、図1と同様に、単列アンギュラ玉軸受において高アキシアル負荷特性及び耐モーメント特性を確保するとともに、保持器の厚さ等の寸法設計自由度が広がり、保持器の厚さ29を十分に確保でき、必要な剛性を得ることができるので、保持器音の発生、保持器の変形、破損の恐れを防止することができ、また、単列アンギュラ玉軸受全体の寸法を大きくする必要も生じない。   In addition, as in FIG. 1, high axial load characteristics and moment resistance characteristics are secured in the single-row angular contact ball bearings, and the degree of freedom in dimensional design such as the thickness of the cage is widened. Since it can be secured and the required rigidity can be obtained, it is possible to prevent the occurrence of cage noise, the deformation and breakage of the cage, and it is also necessary to increase the overall size of the single-row angular contact ball bearing. Absent.

なお、上述の各半径比(r53/D,r51/D)は、50%以上であることが好ましい。また、図5(a)の構成は、図1の複列アンギュラ玉軸受1に適用して好ましいことはもちろんである。   The radius ratios (r53 / D, r51 / D) described above are preferably 50% or more. Moreover, it is needless to say that the configuration of FIG. 5A is preferably applied to the double-row angular ball bearing 1 of FIG.

図6は図2の保持器15のポケット18の形状例を示す図であり、傾斜したポケット18を図2の傾斜方向nから正面にみた図である。図6のように、凹部であるポケット18は、下方部分が玉部材55の中心Oを中心とした半径r1(r1>r(r:玉部材55の半径))の球状凹面部20aであり、開口した上方部分が玉部材55の中心Oを中心とした半径r2(r2>r)の球状凹面部20cであり、中間部分が玉部材55の転動中心軸vを中心とした円筒状のアキシャル円筒状凹面部20bであるような形状に構成されている。また、図6の破線のように球状凹面部20aは転動中心軸v上の中心Oからずれた点O1を中心とする半径を有するとともに、球状凹面部20cは転動中心軸v上の中心Oからずれた点O2を中心とする半径を有する構成としてもよい。図6において、保持器15のポケット18と玉部材55との間において、球状凹面部20aと円筒状凹面部20b,20bとの境界近傍及び球状凹面部20c,20cと円筒状凹面部20b,20bとの境界近傍には比較的スペースの大きい潤滑剤溜まり部A,Bがそれぞれ形成されている。   6 is a view showing an example of the shape of the pocket 18 of the cage 15 of FIG. 2, and is a view of the inclined pocket 18 as seen from the front in the inclined direction n of FIG. As shown in FIG. 6, the pocket 18 that is a concave portion is a spherical concave surface portion 20 a having a radius r1 (r1> r (r: radius of the ball member 55)) whose lower portion is centered on the center O of the ball member 55. The opened upper portion is a spherical concave surface portion 20c having a radius r2 (r2> r) centered on the center O of the ball member 55, and the middle portion is a cylindrical axial centered on the rolling center axis v of the ball member 55. It is comprised in the shape which is the cylindrical concave-surface part 20b. Further, as indicated by the broken line in FIG. 6, the spherical concave surface portion 20a has a radius centered on the point O1 shifted from the center O on the rolling center axis v, and the spherical concave surface portion 20c has a center on the rolling center axis v. It is good also as a structure which has the radius centering on the point O2 shifted | deviated from O. In FIG. 6, between the pocket 18 of the cage 15 and the ball member 55, the vicinity of the boundary between the spherical concave surface portion 20a and the cylindrical concave surface portions 20b, 20b, and the spherical concave surface portions 20c, 20c and the cylindrical concave surface portions 20b, 20b. In the vicinity of the boundary, lubricant reservoir portions A and B having relatively large spaces are formed.

図1の複列アンギュラ玉軸受1及び図5(a)の単列アンギュラ玉軸受50は、その軸受内部に潤滑剤が充填されて使用されるが、潤滑剤としてグリースを用いることが好ましく、この場合、グリースの調度(グリースの粘度を示す指標)が200乃至280の範囲内にあることが好ましい。このように比較的硬いグリースを潤滑剤として使用する場合、保持器のポケット形状が単一の球面状である場合、軸受使用中にグリースがポケットから一度外に押し出されると、なかなかポケット内に戻り難く、保持器において潤滑不良が発生し易くなってしまうが、本実施の形態では、図6のような保持器15を用いることで、ポケット18と玉部材55との間においてグリースが潤滑剤溜まり部A,Bに保持され、ポケット18から外に押し出され難くなり、また、外に押し出されてもポケット18内に戻り易くなるから、グリースによる潤滑性能を発揮し維持することができる。   The double-row angular contact ball bearing 1 of FIG. 1 and the single-row angular contact ball bearing 50 of FIG. 5A are used with a lubricant filled therein, but it is preferable to use grease as the lubricant. In this case, the grease preparation (an index indicating the viscosity of the grease) is preferably in the range of 200 to 280. When using relatively hard grease as a lubricant in this way, if the cage pocket shape is a single spherical shape, it will easily return to the pocket once the grease is pushed out of the pocket while the bearing is in use. Although it is difficult and lubrication failure is likely to occur in the cage, in this embodiment, grease is collected between the pocket 18 and the ball member 55 by using the cage 15 as shown in FIG. Since it is held by the portions A and B and is difficult to be pushed out of the pocket 18 and is easily returned to the pocket 18 even if pushed out, the lubricating performance by the grease can be exhibited and maintained.

なお、上述の保持器に使用されるプラスチック材料としては、ポリアミド樹脂等が好ましい。さらに、本発明の転がり軸受及びその保持器は、第1の実施形態の複列アンギュラ玉軸受、第2の実施形態の単列アンギュラ玉軸受及びそれらの保持器に限定されるものではなく、2つの単列アンギュラ組合せて使用する組合せアンギュラ玉軸受けや、それらの保持器等に適用することができることは言うまでもない。   In addition, as a plastic material used for the above-mentioned cage, polyamide resin or the like is preferable. Furthermore, the rolling bearing and its cage of the present invention are not limited to the double-row angular ball bearing of the first embodiment, the single-row angular ball bearing of the second embodiment, and their cages. Needless to say, the present invention can be applied to combination angular contact ball bearings used in combination with two single-row angular combinations, cages thereof, and the like.

上記実施形態では、転動体として玉部材を利用した玉軸受の構成について説明したが、本発明はこれに限定されることはない。例えば、円筒ころ軸受や針状ころ軸受といった、外輪と、外輪に対して相対回転可能な内輪とを備える転がり軸受であれば、本発明の玉軸受用保持器を適用できる。   In the said embodiment, although the structure of the ball bearing using a ball member as a rolling element was demonstrated, this invention is not limited to this. For example, the ball bearing cage of the present invention can be applied to any rolling bearing having an outer ring and an inner ring that can rotate relative to the outer ring, such as a cylindrical roller bearing or a needle roller bearing.

この発明は、その本質的特性から逸脱することなく数多くの形式のものとして具体化することができる。よって、上述した実施形態は専ら説明上のものであり、本発明を制限するものではないことは言うまでもない。   The present invention can be embodied in many forms without departing from its essential characteristics. Therefore, it is needless to say that the above-described embodiment is exclusively for description and does not limit the present invention.

第1の実施形態による実施形態の複列アンギュラ玉軸受の縦方向断面図である。It is a longitudinal section of a double row angular contact ball bearing of an embodiment by a 1st embodiment. 図1に示す保持器の斜視図である。It is a perspective view of the holder | retainer shown in FIG. 従来の複列アンギュラ玉軸受の縦方向断面図である。It is longitudinal direction sectional drawing of the conventional double row angular contact ball bearing. 図3に示す保持器の斜視図である。It is a perspective view of the holder | retainer shown in FIG. 第2の実施形態による単列アンギュラ玉軸受(半径比が52%以下の場合の各軌道輪と玉部材を示す)の断面図(a)及び従来のラジアル玉軸受(半径比が52%を超えた場合の各軌道輪と玉部材を示す)の断面図(b)である。Sectional view (a) of a single-row angular contact ball bearing according to the second embodiment (showing each bearing ring and ball member when the radius ratio is 52% or less) and a conventional radial ball bearing (radius ratio exceeding 52%) It is sectional drawing (b) of each track ring and a ball member in the case of a case. 図2の保持器15のポケット18の形状例を示す図であり、傾斜したポケット18を図2の傾斜方向nから正面にみた図である。It is a figure which shows the example of a shape of the pocket 18 of the holder | retainer 15 of FIG. 2, and is the figure which looked at the inclined pocket 18 to the front from the inclination direction n of FIG.

符号の説明Explanation of symbols

1 複列アンギュラ玉軸受
3 外輪
5 内輪
7、9 玉部材(転動体)
15、17 保持器
19、21 外輪軌道溝
23、25 内輪軌道溝
50 単列アンギュラ玉軸受
51 外輪軌道溝
52 外輪
53 内輪軌道溝
54 内輪
55 玉部材
1 Double-row angular contact ball bearing 3 Outer ring 5 Inner ring 7, 9 Ball member (rolling element)
15, 17 Cage 19, 21 Outer ring raceway groove 23, 25 Inner ring raceway groove 50 Single row angular contact ball bearing 51 Outer ring raceway groove 52 Outer ring 53 Inner ring raceway groove 54 Inner ring 55 Ball member

Claims (5)

転がり軸受であって、
内周面に外輪軌道溝を有する環状の外輪と、
前記外輪の径方向内方で同心に配置され、外周面に内輪軌道溝を有する環状の内輪と、
前記外輪軌道溝と前記内輪軌道溝との間で転動する複数の転動体と、
前記複数の転動体を周方向に等間隔で転動可能に収容する凹部と、前記凹部内に前記転動体を保持する爪部と、を有する保持器と、を備え、
前記各軌道溝の両端の溝肩は溝肩高さが異なり、前記保持器の爪部が前記溝肩高さの低い溝肩に向かうように軸方向に関し所定角度で傾斜していることを特徴とする転がり軸受。
A rolling bearing,
An annular outer ring having an outer ring raceway groove on the inner peripheral surface;
An annular inner ring that is concentrically disposed radially inward of the outer ring and has an inner ring raceway groove on the outer peripheral surface;
A plurality of rolling elements rolling between the outer ring raceway groove and the inner ring raceway groove;
A retainer having a recess that accommodates the plurality of rolling elements so as to be capable of rolling at equal intervals in the circumferential direction, and a claw that holds the rolling element in the recess.
The groove shoulders at both ends of each raceway groove have different groove shoulder heights, and the claw portions of the cage are inclined at a predetermined angle with respect to the axial direction so as to face the groove shoulders with a low groove shoulder height. Rolling bearing.
前記外輪軌道溝及び前記内輪軌道溝が、軸方向に複列に配置され、2列の転動体を保持する2つの保持器を有する複列アンギュラ玉軸受又は前記外輪軌道溝及び前記内輪軌道溝が単列に配置される単列アンギュラ玉軸受である請求項1に記載の転がり軸受。   The outer ring raceway groove and the inner ring raceway groove are arranged in a double row in the axial direction, and a double row angular contact ball bearing having two cages for holding two rows of rolling elements or the outer ring raceway groove and the inner ring raceway groove are provided. The rolling bearing according to claim 1, which is a single-row angular contact ball bearing arranged in a single row. 前記内輪軌道溝及び前記外輪軌道溝の少なくとも一方の溝半径(r’)と前記転動体の直径(D)との半径比(r’/D)が52%以下である請求項1または2に記載の転がり軸受。   The radius ratio (r '/ D) between the groove radius (r') of at least one of the inner ring raceway groove and the outer ring raceway groove and the diameter (D) of the rolling element is 52% or less. The rolling bearing described. 軸受内部に潤滑剤としてグリースを充填し、
前記グリースの調度が200乃至280の範囲内にある請求項1,2または3に記載の転がり軸受。
Fill the bearing with grease as a lubricant,
The rolling bearing according to claim 1, 2 or 3, wherein the grease has an adjustment in a range of 200 to 280.
内周面に外輪軌道溝を有する環状の外輪と、前記外輪の径方向内方で同心に配置され、外周面に内輪軌道溝を有する内輪と、前記外輪軌道溝と前記内輪軌道溝との間で転動する複数の転動体と、前記複数の転動体を周方向に等間隔で転動可能に収容する凹部と前記凹部内に前記転動体を保持する爪部とを有する保持器と、を備え、前記各軌道溝の両端の溝肩の溝肩高さが異なる転がり軸受のための前記保持器であって、
前記保持器の爪部が前記溝肩高さの低い溝肩に向かうように軸方向に関し所定角度で傾斜していることを特徴とする転がり軸受用保持器。
An annular outer ring having an outer ring raceway groove on an inner peripheral surface, an inner ring having an inner ring raceway groove concentrically disposed radially inward of the outer ring, and between the outer ring raceway groove and the inner ring raceway groove A plurality of rolling elements that roll, a retainer that accommodates the plurality of rolling elements in a circumferential direction so as to be capable of rolling at equal intervals, and a cage having a claw portion that holds the rolling elements in the recess. The cage for a rolling bearing having different groove shoulder heights at both ends of each raceway groove,
The cage for a rolling bearing, wherein the claw portion of the cage is inclined at a predetermined angle with respect to the axial direction so as to face the groove shoulder having a low groove shoulder height.
JP2007205468A 2007-02-15 2007-08-07 Rolling bearing and its cage Pending JP2008224026A (en)

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Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2011241979A (en) * 2010-04-19 2011-12-01 Nsk Ltd Tandem angular type ball bearing
JP2013076468A (en) * 2011-02-24 2013-04-25 Nsk Ltd Double-row angular ball bearing
US9151324B2 (en) 2011-02-24 2015-10-06 Nsk Ltd. Double-row angular ball bearing
CN105378311A (en) * 2013-07-08 2016-03-02 舍弗勒技术股份两合公司 Support bearing, in particular guide roller
JP2018066385A (en) * 2016-10-17 2018-04-26 日本精工株式会社 Cage for angular ball bearing, angular ball bearing and bearing device
CN110439926A (en) * 2019-08-02 2019-11-12 杰尚(无锡)精密机械制造有限公司 A kind of automobile middle control knob bearing
CN111089118A (en) * 2018-10-24 2020-05-01 斯凯孚公司 Bearing unit with cage
WO2023095639A1 (en) * 2021-11-29 2023-06-01 Ntn株式会社 Rolling bearing

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2011241979A (en) * 2010-04-19 2011-12-01 Nsk Ltd Tandem angular type ball bearing
JP2013076468A (en) * 2011-02-24 2013-04-25 Nsk Ltd Double-row angular ball bearing
US9151324B2 (en) 2011-02-24 2015-10-06 Nsk Ltd. Double-row angular ball bearing
CN105378311A (en) * 2013-07-08 2016-03-02 舍弗勒技术股份两合公司 Support bearing, in particular guide roller
US9759260B2 (en) 2013-07-08 2017-09-12 Schaeffler Technologies AG & Co. KG Support bearing, in particular running roller
CN105378311B (en) * 2013-07-08 2018-01-26 舍弗勒技术股份两合公司 Support bearing, in particular guide roller
JP2018066385A (en) * 2016-10-17 2018-04-26 日本精工株式会社 Cage for angular ball bearing, angular ball bearing and bearing device
WO2018074199A1 (en) * 2016-10-17 2018-04-26 日本精工株式会社 Retainer for angular ball bearings
CN109844336A (en) * 2016-10-17 2019-06-04 日本精工株式会社 Angular contact ball bearing retainer, angular contact ball bearing and bearing arrangement
CN111089118A (en) * 2018-10-24 2020-05-01 斯凯孚公司 Bearing unit with cage
CN110439926A (en) * 2019-08-02 2019-11-12 杰尚(无锡)精密机械制造有限公司 A kind of automobile middle control knob bearing
WO2023095639A1 (en) * 2021-11-29 2023-06-01 Ntn株式会社 Rolling bearing

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