JP4135321B2 - Rolling bearing - Google Patents

Rolling bearing Download PDF

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Publication number
JP4135321B2
JP4135321B2 JP2001025495A JP2001025495A JP4135321B2 JP 4135321 B2 JP4135321 B2 JP 4135321B2 JP 2001025495 A JP2001025495 A JP 2001025495A JP 2001025495 A JP2001025495 A JP 2001025495A JP 4135321 B2 JP4135321 B2 JP 4135321B2
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Japan
Prior art keywords
cage
diameter
clearance
subtracting
ring
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JP2002227850A (en
Inventor
清 荻野
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JTEKT Corp
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JTEKT Corp
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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
    • F16C19/52—Bearings with rolling contact, for exclusively rotary movement with devices affected by abnormal or undesired conditions
    • F16C19/527—Bearings with rolling contact, for exclusively rotary movement with devices affected by abnormal or undesired conditions related to vibration and noise
    • 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
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/44—Needle bearings
    • F16C19/46—Needle bearings with one row or needles
    • 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
    • F16C33/46—Cages for rollers or needles
    • F16C33/4617—Massive or moulded cages having cage pockets surrounding the rollers, e.g. machined window cages
    • F16C33/4623—Massive or moulded cages having cage pockets surrounding the rollers, e.g. machined window cages formed as one-piece cages, i.e. monoblock cages
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/46—Cages for rollers or needles
    • F16C33/467—Details of individual pockets, e.g. shape or roller retaining means
    • F16C33/4676—Details of individual pockets, e.g. shape or roller retaining means of the stays separating adjacent cage pockets, e.g. guide means for the bearing-surface of 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
    • 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
    • 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
    • F16C2361/00—Apparatus or articles in engineering in general
    • F16C2361/61—Toothed gear systems, e.g. support of pinion shafts

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

Abstract

PROBLEM TO BE SOLVED: To provide a bearing capable of inhibiting a noise at the time of non-load rotation. SOLUTION: In the bearing, a value (guide clearance S1) obtained by subtracting a radius R1 of a circumscribed circle of a retainer 5 from a half of an inner diameter D2 of an outer ring 2 is made to 4% or less of a value (clearance S2 between an inner ring and an outer ring) obtained by subtracting a half of an outer diameter D1 of the inner ring 1 from a half of the inner diameter D2 of the outer ring 2. Thereby, it was confirmed by an experiment that a self-excitation vibration of the retainer 5 or the retainer 5 and a rolling body 3 can be inhibited at the time of non-load rotation and a noise is not generated. Whereas, when the guide clearance S1 exceeds 4% of the clearance S2 between the inner ring and the outer ring, it was confirmed by an experiment that a noise is generated.

Description

【０００１】
【発明の属する技術分野】
この発明は、無負荷回転時の異音を抑制できる転がり軸受に関する。
【０００２】
【従来の技術】
自動車の変速機等に組込まれる軸受(例えば、ギヤインナ用針状ころ軸受)において、外部から荷重がかからない条件(無負荷)で使用しているときに、保持器や転動体が自励振動して、大きな振動や耳障りな異音を発することがある。
【０００３】
【発明が解決しようとする課題】
そこで、この発明の目的は、無負荷回転時の異音を抑制できる転がり軸受を提供することにある。
【０００４】
【課題を解決するための手段】
発明者らは、外輪に案内される外輪案内の保持器を備えた軸受では、外側部材の内径の２分の１と保持器の外接円の半径との差(案内すきま)が大きいほど、無負荷回転時に保持器(または保持器と転動体)の自励振動が大きくなり、異音が大きくなることを実験によって確認した。この発明は、この予期しない事実に基く。
【０００５】
すなわち、請求項１の発明の転がり軸受は、内側部材と外側部材との間に保持器が配置され、上記保持器で転動体が保持され、上記外側部材の内周面で上記保持器を案内する転がり軸受において、
上記保持器は、外形が三角形状、多角形状、楕円形状のいずれかであり、
外側部材の内径(内直径)の２分の１から保持器の外接円の半径を減算した値を、外側部材の内径の２分の１から内側部材の外径(外直径)の２分の１を減算した値の４％以内にしたことを特徴としている。
【０００６】
この請求項１の発明の転がり軸受では、外側部材の内径の２分の１から保持器の外接円の半径を減算した値(案内すきま)を、外側部材の内径の２分の１から内側部材の外径の２分の１を減算した値(内,外側部材間のすきま)の４％以内にした。これにより、無負荷回転時に保持器または保持器と転動体の自励振動を抑制でき、異音が発生しなくなることを実験で確認した。一方、上記案内すきまが、上記転動体径に相当する値の４％を越えると、異音が発生することを実験で確認した。
【０００７】
また、発明者らは、内輪に案内される内輪案内の保持器を備えた軸受では、内側部材の外径の２分の１と保持器の内接円の半径との差(案内すきま)が大きいほど、無負荷回転時に保持器または保持器と転動体の自励振動が大きくなり、異音が大きくなることを実験によって確認した。
【０００８】
したがって、一参考例の軸受は、内側部材と外側部材との間に保持器が配置され、上記内側部材の外周面で上記保持器を案内する軸受において、
保持器の内接円の半径から内側部材の外径の２分の１を減算した値を、外側部材の内径の２分の１から内側部材の外径の２分の１を減算した値の４％以内にしたことを特徴としている。
【０００９】
この一参考例の軸受では、保持器の内接円の半径から内側部材の外径の２分の１を減算した値(案内すきま)を、外側部材の内径の２分の１から内側部材の外径の２分の１を減算した値(内,外側部材間のすきま)の４％以内にした。これにより、無負荷回転時に保持器または保持器と転動体の自励振動を抑制でき、異音が発生しなくなることを実験で確認した。一方、上記案内すきまが、上記転動体径に相当する値の４％を越えると、異音が発生することを実験で確認した。
【００１０】
【発明の実施の形態】
以下、この発明を図示の実施の形態により詳細に説明する。
【００１１】
図１に、この発明の軸受の参考例の模式的な断面を示す。この軸受は、内輪１と外輪２と、この内輪１と外輪２との間に配置されたころ３と保持器５を備える。この保持器５は、周方向に所定間隔を隔てて形成された複数のポケット４を有し、このポケット４に、ころ３を保持している。
【００１２】
上記保持器５は、図３の部分断面図に示すように、外周面の軸方向の両端で径方向に突き出した鍔６,７を有し、この鍔６,７の軸方向内方に隣接して、径方向に突き出した断面台形状の突起１０,１１を有している。この突起１０,１１は、ポケット４に隣接する柱部１２に形成されている。また、図４に、保持器５を径方向内側から見た様子を部分的に示すように、ポケット４は、略細長い矩形状の開口であり、軸方向の中央部に周方向への逃げ窪み１３が両側に形成されている。この逃げ窪み１３は、保持器５ところ３との摺動抵抗を低減して、ポケット４に配置されるころ３の回転を円滑にするために形成されている。
【００１３】
この参考例では、図１に示す外輪２の内径Ｄ２の２分の１から保持器５の外接円の半径Ｒ１を減算した値(案内すきまＳ１)を、外輪２の内径Ｄ２の２分の１から内輪１の外径Ｄ１の２分の１を減算した値Ｓ２の２％にした。すなわち、
Ｓ１＝((１/２)Ｄ２−Ｒ１)＝０.０２(１/２(Ｄ２−Ｄ１))＝０.０２Ｓ２
とした。なお、図１では、案内すきまＳ１を誇張して描いている。
【００１４】
このように、この参考例では、保持器５の外接円と外輪２の内周面２Ａとの間の案内すきまＳ１を、内輪１の外周面１Ａと外輪２の内周面２Ａとの間のすきまＳ２の４％以内(Ｓ１≦０.０４Ｓ２)の２％に設定した。これにより、図２に示すような、保持器５の実線で描いた位置と、破線で描いた位置との間で起るような自励振動を抑制でき、異音が発生しなくなることを実験で確認した。一方、上記案内すきまＳ１が、内輪１と外輪２との間のすきまＳ２の４％を越えると、異音が発生することを実験で確認した。
【００１５】
なお、上記参考例では、保持器５が外輪２の内周面で案内される外輪案内の軸受について説明したが、保持器５が内輪１の外周面１Ａで案内される内輪案内の軸受の場合には、保持器５の内接円の半径から内輪１の外径Ｄ１の２分の１を減算した案内すきまを、外輪２の内径Ｄ２の２分の１から内輪１の外径Ｄ１の２分の１を減算した値の４％以内に設定すればよい。これにより、保持器あるいは保持器ところの自励振動を抑制でき、無負荷回転時の異音が発生することを防止できた。
【００１６】
また、図５に模式的に示すように、外輪案内の軸受において、保持器５１の外形が三角形状である場合には、本発明の実施形態となる。すなわち、この場合には、一点鎖線で示した保持器５１の外接円５２の半径を、破線で示す外輪５３のガイド面(内周面)５３Ａの直径の２分の１から減算した値(案内すきまＳ５０)を、外輪５３のガイド面５３Ａの直径から内輪(図示せず)の外周面の直径を減算した値の２分の１の４％以内の値に設定することによって、無負荷回転時に、保持器５１(もしくは保持器ところ(図示せず))が自励振動することを抑制して、異音の発生を防止できることを実験で確認できた。なお、上記三角形の角が湾曲した形状である場合や、保持器の外径が三角形以上の多角形状である場合、さらには、保持器が楕円形である場合にも本発明を適用できることを実験で確かめることができた。
【００１７】
【発明の効果】
以上より明らかなように、請求項１の発明の転がり軸受は、外側部材の内径の２分の１から保持器の外接円の半径を減算した値(案内すきま)を、外側部材の内径の２分の１から内側部材の外径の２分の１を減算した値(内,外輪間すきま)の４％以内にした。これにより、無負荷回転時に保持器または保持器と転動体の自励振動を抑制でき、異音が発生しなくなることを実験で確認した。一方、上記案内すきまが、上記内,外輪間すきまの４％を越えると、異音が発生することを実験で確認した。
【００１８】
また、一参考例の軸受は、保持器の内接円の半径から内側部材の外径の２分の１を減算した値(案内すきま)を、外側部材の内径の２分の１から内側部材の外径の２分の１を減算した値(内,外輪間すきま)の４％以内にした。これにより、無負荷回転時に保持器または保持器と転動体の自励振動を抑制でき、異音が発生しなくなることを実験で確認した。一方、上記案内すきまが、上記内,外輪間すきまの４％を越えると、異音が発生することを実験で確認した。
【図面の簡単な説明】
【図１】 この発明の転がり軸受の参考例の断面を示す模式図である。
【図２】 軸受の自励振動が起る様子を模式的に示した図である。
【図３】 上記参考例の保持器の部分断面図である。
【図４】 上記保持器のポケットの形状を示す図である。
【図５】 上記保持器が三角形状であるこの発明の一実施形態を模式的に示す図である。
【符号の説明】
１…内輪、２…外輪、３…ころ、４…ポケット、５…保持器、６,７…鍔、
１０,１１…突起、１２…柱部、１３…逃げ窪み、Ｄ２…外輪の内径、
Ｄ１…内輪の外径、Ｒ１…保持器の外接円の半径、Ｓ１…案内すきま。[0001]
BACKGROUND OF THE INVENTION
This invention relates to a rolling bearing can be suppressed abnormal noise during idling.
[0002]
[Prior art]
When bearings (such as needle roller bearings for gear inners) incorporated in automobile transmissions are used under conditions where no external load is applied (no load), the cage and rolling elements self-vibrate. May emit loud vibrations or annoying noises.
[0003]
[Problems to be solved by the invention]
Accordingly, an object of the present invention is to provide a rolling bearing can be suppressed abnormal noise during idling.
[0004]
[Means for Solving the Problems]
The inventors have found that in bearings having an outer ring guide cage guided by the outer ring, the larger the difference (guide clearance) between the half of the inner diameter of the outer member and the radius of the circumscribed circle of the cage, the more It was confirmed by experiments that the self-excited vibration of the cage (or the cage and rolling elements) increased during load rotation, and abnormal noise increased. The present invention is based on this unexpected fact.
[0005]
That is, the rolling bearing of the invention of claim 1 is arranged cage between the inner and outer members, the rolling elements are held in the cage, guiding the cage on the inner peripheral surface of the outer member in the rolling bearing to,
The cage has a triangular outer shape, a polygonal shape, or an elliptical shape,
The value obtained by subtracting the radius of the circumscribed circle of the cage from the half of the inner diameter (inner diameter) of the outer member is half the outer diameter (outer diameter) of the inner member from one half of the inner diameter of the outer member. It is characterized by being within 4% of the value obtained by subtracting 1.
[0006]
In the rolling bearing of the invention as claimed in claim 1, 2 minute radius subtracted value of the circumscribed circle of the retainer from the first inner diameter of the outer member (guide clearance), the inner member from one half of the inner diameter of the outer member It was made within 4% of the value (clearance between the inner and outer members) subtracting one half of the outer diameter. As a result, it was confirmed by experiments that the self-excited vibration of the cage or the cage and the rolling element can be suppressed during no-load rotation, and no abnormal noise is generated. On the other hand, when the guide clearance exceeded 4% of the value corresponding to the rolling element diameter, it was confirmed by experiments that abnormal noise was generated.
[0007]
Further, the inventors have found that in a bearing provided with an inner ring guide cage guided by the inner ring, there is a difference (guide clearance) between a half of the outer diameter of the inner member and the radius of the inscribed circle of the cage. It was confirmed by experiments that the larger the value, the greater the self-excited vibration of the cage or the cage and the rolling element during no-load rotation and the greater the noise.
[0008]
Therefore, in the bearing of one reference example, the cage is disposed between the inner member and the outer member, and the cage is guided on the outer peripheral surface of the inner member.
The value obtained by subtracting one half of the outer diameter of the inner member from the radius of the inscribed circle of the cage, and the value obtained by subtracting one half of the outer diameter of the inner member from one half of the inner diameter of the outer member. It is characterized by being within 4%.
[0009]
In the bearing of this reference example, a value (guide clearance) obtained by subtracting one half of the outer diameter of the inner member from the radius of the inscribed circle of the cage is calculated from one half of the inner diameter of the outer member. It was within 4% of the value obtained by subtracting one half of the outer diameter (clearance between the inner and outer members). As a result, it was confirmed by experiments that the self-excited vibration of the cage or the cage and the rolling element can be suppressed during no-load rotation, and no abnormal noise is generated. On the other hand, when the guide clearance exceeded 4% of the value corresponding to the rolling element diameter, it was confirmed by experiments that abnormal noise was generated.
[0010]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, the present invention will be described in detail with reference to the illustrated embodiments.
[0011]
In FIG. 1, the typical cross section of the reference example of the bearing of this invention is shown. The bearing includes an inner ring 1 and an outer ring 2, and rollers 3 and a cage 5 disposed between the inner ring 1 and the outer ring 2. The cage 5 has a plurality of pockets 4 formed at predetermined intervals in the circumferential direction, and the rollers 3 are held in the pockets 4.
[0012]
As shown in the partial cross-sectional view of FIG. 3, the cage 5 has flanges 6 and 7 protruding radially at both ends of the outer peripheral surface in the axial direction, and adjacent to the axially inner sides of the flanges 6 and 7. And it has the projections 10 and 11 of the cross-sectional trapezoid shape projected in the radial direction. The protrusions 10 and 11 are formed on the column portion 12 adjacent to the pocket 4. 4 partially shows a state in which the cage 5 is viewed from the inside in the radial direction, the pocket 4 is a substantially elongated rectangular opening, and a recess in the circumferential direction at the central portion in the axial direction. 13 is formed on both sides. The escape recess 13 is formed in order to reduce the sliding resistance with the cage 5 and 3 and to smoothly rotate the roller 3 disposed in the pocket 4.
[0013]
In this reference example, a value (guide clearance S1) obtained by subtracting the radius R1 of the circumscribed circle of the cage 5 from one half of the inner diameter D2 of the outer ring 2 shown in FIG. From this, 2% of the value S2 is obtained by subtracting one half of the outer diameter D1 of the inner ring 1. That is,
S1 = ((1/2) D2-R1) = 0.02 (1/2 (D2-D1)) = 0.02S2
It was. In FIG. 1, the guide clearance S1 is exaggerated.
[0014]
Thus, in this reference example, the guide clearance S1 between the circumscribed circle of the cage 5 and the inner peripheral surface 2A of the outer ring 2 is set between the outer peripheral surface 1A of the inner ring 1 and the inner peripheral surface 2A of the outer ring 2. It was set to 2% within 4% of the clearance S2 (S1 ≦ 0.04S2). As a result, it is possible to suppress self-excited vibration that occurs between the position drawn by the solid line of the cage 5 and the position drawn by the broken line, as shown in FIG. Confirmed with. On the other hand, when the guide clearance S1 exceeds 4% of the clearance S2 between the inner ring 1 and the outer ring 2, it was confirmed through experiments that abnormal noise is generated.
[0015]
In the above-described reference example, the outer ring guide bearing in which the cage 5 is guided by the inner peripheral surface of the outer ring 2 has been described. However, the cage 5 is an inner ring guide bearing that is guided by the outer peripheral surface 1A of the inner ring 1. The guide clearance obtained by subtracting one half of the outer diameter D1 of the inner ring 1 from the radius of the inscribed circle of the cage 5 is 2 times the outer diameter D1 of the inner ring 1 from one half of the inner diameter D2 of the outer ring 2. What is necessary is just to set within 4% of the value which subtracted 1 /. Thereby, the self-excited vibration of the cage or the cage can be suppressed, and abnormal noise during no-load rotation can be prevented.
[0016]
Further, as schematically shown in FIG. 5, in the outer ring guide bearing, when the outer shape of the cage 51 is a triangular shape, it is an embodiment of the present invention. In other words, in this case, a value obtained by subtracting the radius of the circumscribed circle 52 of the cage 51 indicated by the one-dot chain line from one half of the diameter of the guide surface (inner peripheral surface) 53A of the outer ring 53 indicated by the broken line (guide). By setting the clearance S50) to a value within 4% of half the value obtained by subtracting the diameter of the outer peripheral surface of the inner ring (not shown) from the diameter of the guide surface 53A of the outer ring 53, at the time of no-load rotation It has been confirmed through experiments that the cage 51 (or cage (not shown)) can be prevented from self-excited vibration and the occurrence of abnormal noise can be prevented. It should be noted that the present invention can be applied to the case where the triangle has a curved corner, the outer diameter of the cage is a polygonal shape greater than or equal to the triangle, and the cage is elliptical. I was able to confirm.
[0017]
【The invention's effect】
As apparent from the above, the rolling bearing of the invention of claim 1, 2 minute radius subtracted value of the circumscribed circle of the retainer from the first inner diameter of the outer member (guide clearance), the inner diameter of the outer member 2 The value obtained by subtracting one half of the outer diameter of the inner member from one half (the clearance between the inner and outer rings) was within 4%. As a result, it was confirmed by experiments that the self-excited vibration of the cage or the cage and the rolling element can be suppressed during no-load rotation, and no abnormal noise is generated. On the other hand, when the guide clearance exceeded 4% of the clearance between the inner and outer rings, it was confirmed by experiment that abnormal noise was generated.
[0018]
Also, in the bearing of one reference example, a value obtained by subtracting one half of the outer diameter of the inner member from the radius of the inscribed circle of the cage (guide clearance) is obtained from one half of the inner diameter of the outer member. It was within 4% of the value obtained by subtracting one half of the outer diameter (clearance between the inner and outer rings). As a result, it was confirmed by experiments that the self-excited vibration of the cage or the cage and the rolling element can be suppressed during no-load rotation, and no abnormal noise is generated. On the other hand, when the guide clearance exceeded 4% of the clearance between the inner and outer rings, it was confirmed by experiment that abnormal noise was generated.
[Brief description of the drawings]
1 is a schematic view showing a cross section of a reference example of the rolling bearing of the present invention.
FIG. 2 is a diagram schematically showing how self-excited vibration of a bearing occurs.
FIG. 3 is a partial cross-sectional view of the cage of the reference example.
FIG. 4 is a view showing a shape of a pocket of the cage.
FIG. 5 is a diagram schematically showing an embodiment of the present invention in which the cage is triangular.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 ... Inner ring, 2 ... Outer ring, 3 ... Roller, 4 ... Pocket, 5 ... Cage, 6, 7 ... Spear,
10, 11 ... projection, 12 ... column part, 13 ... escape recess, D2 ... inner diameter of outer ring,
D1 ... outer diameter of inner ring, R1 ... radius of circumscribed circle of cage, S1 ... guide clearance.

Claims (1)

内側部材と外側部材との間に保持器が配置され、上記保持器で転動体が保持され、上記外側部材の内周面で上記保持器を案内する転がり軸受において、
上記保持器は、外形が三角形状、多角形状、楕円形状のいずれかであり、
上記外側部材の内径の２分の１から上記保持器の外接円の半径を減算した値を、上記外側部材の内径の２分の１から上記内側部材の外径の２分の１を減算した値の４％以内にしたことを特徴とする転がり軸受。Cage is disposed between the inner member and the outer member, rolling elements are held in the cage, in the rolling bearing for guiding the retainer in the inner peripheral surface of the outer member,
The cage has a triangular outer shape, a polygonal shape, or an elliptical shape,
A value obtained by subtracting the radius of the circumscribed circle of the cage from one half of the inner diameter of the outer member, and a half of the outer diameter of the inner member from one half of the inner diameter of the outer member. rolling bearing characterized by being within 4% of the value.
JP2001025495A 2001-02-01 2001-02-01 Rolling bearing Expired - Fee Related JP4135321B2 (en)

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Application Number Priority Date Filing Date Title
JP2001025495A JP4135321B2 (en) 2001-02-01 2001-02-01 Rolling bearing

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Application Number Priority Date Filing Date Title
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Publication Number Publication Date
JP2002227850A JP2002227850A (en) 2002-08-14
JP4135321B2 true JP4135321B2 (en) 2008-08-20

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DE102009024681B4 (en) * 2009-06-12 2011-04-28 Aktiebolaget Skf roller bearing

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