JP2006329218A - Rolling bearing cage - Google Patents

Rolling bearing cage Download PDF

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Publication number
JP2006329218A
JP2006329218A JP2005149241A JP2005149241A JP2006329218A JP 2006329218 A JP2006329218 A JP 2006329218A JP 2005149241 A JP2005149241 A JP 2005149241A JP 2005149241 A JP2005149241 A JP 2005149241A JP 2006329218 A JP2006329218 A JP 2006329218A
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Prior art keywords
inner peripheral
cage
peripheral surface
rolling bearing
grease
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Pending
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JP2005149241A
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Japanese (ja)
Inventor
Keiichi Ueda
敬一 植田
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NTN Corp
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NTN Corp
NTN Toyo Bearing Co Ltd
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Priority to JP2005149241A priority Critical patent/JP2006329218A/en
Publication of JP2006329218A publication Critical patent/JP2006329218A/en
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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
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/66—Special parts or details in view of lubrication
    • F16C33/6603—Special parts or details in view of lubrication with grease as lubricant
    • F16C33/6607—Retaining the grease in or near the bearing
    • F16C33/6614—Retaining the grease in or near the bearing in recesses or cavities provided in retainers, races or rolling elements
    • 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
    • F16C33/3837—Massive or moulded cages having cage pockets surrounding the balls, e.g. machined window cages
    • F16C33/3843—Massive or moulded cages having cage pockets surrounding the balls, 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
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/16—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls
    • F16C19/163—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls with angular contact
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2300/00—Application independent of particular apparatuses
    • F16C2300/20—Application independent of particular apparatuses related to type of movement
    • F16C2300/22—High-speed rotation

Abstract

<P>PROBLEM TO BE SOLVED: To provide a rolling bearing cage for improving the reliability of lubricating grease in a high speed application. <P>SOLUTION: The rolling bearing cage 5 comprises pockets 6 provided at a plurality of circumferential positions on the ring cage for holding rolling elements 4. An inner diameter d1 at either end in the cross direction of the cage is smaller than an inner diameter d2 at the center in the cross direction. For example, the inner peripheral face of the cage 5 consists of a center inner peripheral face portion 5a shaped into a cylindrical face and both-side end inner peripheral face portions 5b, 5b located adjacent to the center inner peripheral face portion 5a at a level difference. The inner diameter of the end inner peripheral face portion 5b is smaller than the inner diameter of the center inner peripheral face portion 5a. The center inner peripheral face portion 5a is wider than the pocket 6. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

この発明は、工作機械用主軸支持部やボールねじ支持部など、一般産業機械の支持部に用いられるグリース潤滑の転がり軸受の保持器に関する。   The present invention relates to a grease-lubricated rolling bearing retainer used for a support part of a general industrial machine such as a spindle support part for a machine tool or a ball screw support part.

軸受における潤滑の目的は、転がり面や滑り面に薄い油膜を形成して、金属と金属が直接するのを防ぐことであり、その潤滑により次に列挙するような効果が得られる。
(1) 摩擦および摩耗の低減、(2) 摩擦熱の排出、(3) 軸受寿命の延長、(4) さび止め、(5) 異物の侵入防止。
軸受の潤滑において、これらの効果を発揮させるためには、使用条件に適した潤滑方法の採用、良質な潤滑剤の選定、潤滑剤中のダスト除去、軸受外部からの異物の侵入と潤滑剤の漏れ防止のための適切な密封構造の設計が必要である。 The purpose of lubrication in the bearing is to form a thin oil film on the rolling and sliding surfaces to prevent the metal and the metal from being directly applied. The lubrication provides the following effects.
(1) Reducing friction and wear, (2) Dissipating frictional heat, (3) Extending bearing life, (4) Rust prevention, (5) Preventing entry of foreign matter.
In order to exert these effects in the lubrication of the bearing, the use of a lubrication method suitable for the conditions of use, selection of a good quality lubricant, removal of dust in the lubricant, intrusion of foreign matter from the outside of the bearing and lubricant It is necessary to design an appropriate sealing structure to prevent leakage.

一般に工作機械の主軸支持に用いる軸受の潤滑では、攪拌による発熱をできるだけ小さくするために、非常に少ない量の潤滑油が用いられる。図１１に、軸受の潤滑に用いられる油量と、摩擦損失および軸受温度との関係のグラフを示す。軸受の潤滑方法には、グリース潤滑、オイルミスト潤滑、エアオイル潤滑、ジェット潤滑などがあり、要求機能にあった適切な潤滑方法が選択される。   Generally, in lubricating a bearing used for supporting a spindle of a machine tool, a very small amount of lubricating oil is used in order to minimize heat generation by stirring. FIG. 11 is a graph showing the relationship between the amount of oil used for bearing lubrication, friction loss, and bearing temperature. The bearing lubrication method includes grease lubrication, oil mist lubrication, air oil lubrication, jet lubrication, and the like, and an appropriate lubrication method suitable for the required function is selected.

このうちグリース潤滑（図１１の油量領域IIとなる）は、外部潤滑装置が不要であり、主軸支持用の軸受に適用した場合、主軸回りの構造を簡素にできる。加えて、初期に封入される少量のグリースで潤滑できることから、環境汚染の原因となるオイルミストの発生も極めて少なくできる。そのため、主軸支持用軸受などの潤滑では、グリース潤滑が最も一般的に使用されている。グリース潤滑を用いた転がり軸受として、外輪の内周面にグリース溜まりを設けたものも提案されている（例えば特許文献１）。
特開２００２−１２２１４９号公報 Of these, grease lubrication (in the oil amount region II in FIG. 11) does not require an external lubrication device, and when applied to a bearing for supporting the main shaft, the structure around the main shaft can be simplified. In addition, since it can be lubricated with a small amount of grease filled in the initial stage, generation of oil mist that causes environmental pollution can be extremely reduced. Therefore, grease lubrication is most commonly used for lubrication of a spindle support bearing or the like. As a rolling bearing using grease lubrication, a bearing provided with a grease reservoir on the inner peripheral surface of the outer ring has been proposed (for example, Patent Document 1).
JP 2002-122149 A

上記したように、主軸支持用の軸受にグリース潤滑を適用した場合、主軸構造の簡素化に有利であるだけでなく、オイルミストの発生も極めて少ないことから環境負荷軽減に寄与できる。また、運転に伴い発生する音も他の潤滑方法に比べて小さいので、周辺環境へ与える影響も低い。   As described above, when grease lubrication is applied to the bearing for supporting the main shaft, it is not only advantageous for simplification of the main shaft structure, but also the generation of oil mist is extremely small, which can contribute to reducing the environmental load. In addition, since the sound generated during operation is small compared to other lubrication methods, the influence on the surrounding environment is low.

しかし、工作機械の主軸支持用軸受などの高速用途にグリース潤滑を使用する場合、発熱や摩耗によるグリースの劣化、つまり潤滑寿命が重要となる。そのため、グリース潤滑を適用できる主軸回転の速度範囲には制約がある。グリース潤滑を用いて主軸回転の高速化を図るには、グリース劣化を抑制（発熱や摩擦の低減）すると共に、より多くのグリースを軸受内部に保持することが必要となる。   However, when grease lubrication is used for high-speed applications such as spindle support bearings for machine tools, grease deterioration due to heat generation or wear, that is, lubrication life is important. Therefore, there is a limitation on the speed range of the spindle rotation to which grease lubrication can be applied. In order to increase the rotation speed of the spindle using grease lubrication, it is necessary to suppress grease deterioration (reducing heat generation and friction) and to hold more grease inside the bearing.

ところが、従来、転がり軸受においては、図１２（Ａ）のように保持器１５の幅方向の両端の内径を、幅方向の中央の内径より大きな寸法としたり、図１２（Ｂ）のように保持器１５の内径を幅方向の全域にわたって同一の寸法としているので、軸受内部へグリースＧを十分保持できていない。これは、軸受の回転に伴って保持器１５に遠心力が作用するため、保持器１５の内径面に付着したグリースＧは中央部から端部に向かって移動するが、上記した保持器内径寸法のため、グリースＧが保持器１５のポケット１６に保持される転動体１４の近傍に保持され難いからである。   However, in a conventional rolling bearing, the inner diameter at both ends in the width direction of the cage 15 is made larger than the inner diameter at the center in the width direction as shown in FIG. 12 (A) or held as shown in FIG. 12 (B). Since the inner diameter of the container 15 is the same across the entire region in the width direction, the grease G cannot be sufficiently held inside the bearing. This is because the centrifugal force acts on the cage 15 as the bearing rotates, so that the grease G adhering to the inner diameter surface of the cage 15 moves from the center portion toward the end portion. Therefore, the grease G is difficult to be held in the vicinity of the rolling element 14 held in the pocket 16 of the cage 15.

この発明の目的は、高速用途におけるグリース潤滑の信頼性を高めることができる転がり軸受用保持器を提供することである。   An object of the present invention is to provide a rolling bearing cage capable of improving the reliability of grease lubrication in high-speed applications.

この発明の転がり軸受用保持器は、リング状の保持器の円周方向複数箇所における幅方向の中間に、転動体を保持するポケットを有し、グリース潤滑の転がり軸受に用いられる保持器において、保持器の幅方向の両端の内径が、幅方向の中央の内径よりも小さな寸法であることを特徴とする。この転がり軸受用保持器はアンギュラ玉軸受に用いられるものであっても良い。
この構成によると、軸受の運転に伴ってグリースに遠心力が作用して、保持器内径面に付着したグリースが中央部から端部に向かって移動しても、保持器の両端の内径が小さいため、グリースは保持器内径面の端部または中央部付近で保持される。その結果、従来の保持器の場合に比べて、転動体の近傍に多くのグリースが存在できることとなり、高速用途における潤滑の信頼性を高めることができる。 The cage for a rolling bearing according to the present invention has a pocket for holding a rolling element in the middle of the width direction at a plurality of locations in the circumferential direction of the ring-shaped cage, and is used in a grease lubricated rolling bearing. The inner diameter at both ends in the width direction of the cage is smaller than the inner diameter at the center in the width direction. This rolling bearing retainer may be used for an angular ball bearing.
According to this configuration, even if the grease acts on the grease with the operation of the bearing and the grease adhered to the inner diameter surface of the cage moves from the central portion toward the end portion, the inner diameters at both ends of the cage are small. Therefore, the grease is held near the end or the center of the inner diameter surface of the cage. As a result, more grease can be present near the rolling elements than in the case of the conventional cage, and the reliability of lubrication in high-speed applications can be improved.

この発明において、保持器の内周面が、それぞれ円筒面状とされた中央内周面部分、およびこの中央内周面部分に段差をもって隣接する両側の端部内周面部分からなり、中央内周面部分は、前記ポケットの幅よりも広いものとしても良い。
この構成の場合、保持器の端部内周面部分が段差を持って小径となっているため、運転に伴ってグリースに遠心力が作用し、保持器内径面のグリースが中央部から端部に向かって移動しても、前記端部内周面部分の付近で中央内周面部分にグリースが確実に保持される。 In this invention, the inner peripheral surface of the cage is composed of a central inner peripheral surface portion each having a cylindrical surface shape, and end inner peripheral surface portions on both sides adjacent to the central inner peripheral surface portion with a step, The surface portion may be wider than the width of the pocket.
In this configuration, since the inner peripheral surface of the cage has a small diameter with a step, centrifugal force acts on the grease during operation, and the grease on the cage inner surface moves from the center to the end. Even when moving toward the end, the grease is reliably held on the central inner peripheral surface portion in the vicinity of the end inner peripheral surface portion.

この発明において、保持器の内周面が、幅方向の中央が最も大径となる断面山形の傾斜面からなるものとしても良い。
この構成の場合、運転に伴ってグリースに遠心力が作用しても、内径面に付着したグリースは中央部近傍で保持される。その結果、転動体近傍にはより多くのグリースが存在することができるため、高速用途における潤滑の信頼性をより高めることができる。 In the present invention, the inner peripheral surface of the cage may be formed of an inclined surface having a mountain-shaped cross section having the largest diameter in the center in the width direction.
In the case of this configuration, even if a centrifugal force acts on the grease during operation, the grease attached to the inner diameter surface is held near the center. As a result, more grease can be present in the vicinity of the rolling elements, so that the reliability of lubrication in high-speed applications can be further increased.

この発明において、前記のように段差を持つ中央内周面部分および端部内周面部分を設けた場合に、これら中央内周面部分と端部内周面部分の間に円周溝を設けても良い。
上記のように円周溝が設けられていると、この円周溝によってグリースの保持空間が拡張されることになる。そのため、保持器内周面に付着したグリースがより多く中央部付近で保持され、高速用途における潤滑の信頼性がより高まる。 In the present invention, when the central inner peripheral surface portion having the step and the end inner peripheral surface portion are provided as described above, a circumferential groove may be provided between the central inner peripheral surface portion and the end inner peripheral surface portion. good.
When the circumferential groove is provided as described above, the grease holding space is expanded by the circumferential groove. Therefore, more grease adhered to the inner peripheral surface of the cage is retained near the center, and the reliability of lubrication in high-speed applications is further increased.

この発明において、前記転がり軸受用保持器が密封形の軸受で使用されるものであっても良い。
密封形の軸受では、運転によって攪拌されたグリースを、シールが軸受内部に保持する働きを持つので、保持器の構造と相まって、転動体の近傍におけるグリースの保持性をより高めることができる。 In the present invention, the rolling bearing cage may be used in a sealed bearing.
In the sealed bearing, the grease that has been agitated by the operation has a function of holding the seal inside the bearing, so that the retention of the grease in the vicinity of the rolling elements can be further improved in combination with the structure of the cage.

この発明の転がり軸受用保持器は、リング状の保持器の円周方向複数箇所における幅方向の中間に、転動体を保持するポケットを有し、グリース潤滑の転がり軸受に用いられる保持器において、保持器の幅方向の両端の内径を、幅方向の中央の内径よりも小さな寸法としたため、高速用途におけるグリース潤滑の信頼性を高めることができる。   The cage for a rolling bearing according to the present invention has a pocket for holding a rolling element in the middle of the width direction at a plurality of locations in the circumferential direction of the ring-shaped cage, and is used in a grease lubricated rolling bearing. Since the inner diameter at both ends in the width direction of the cage is smaller than the inner diameter at the center in the width direction, the reliability of grease lubrication in high-speed applications can be improved.

この発明の第１の実施形態を図１ないし図３と共に説明する。図１は、この実施形態の保持器を用いた転がり軸受の断面図を示す。この転がり軸受１は、内輪２および外輪３と、これら内外輪２，３の軌道面２ａ，３ａ間に介在させた複数の転動体４と、これら複数の転動体４を保持するリング状の保持器５とでなる。この転がり軸受１は、グリース潤滑のアンギュラ玉軸受であり、転動体４がボールからなる。   A first embodiment of the present invention will be described with reference to FIGS. FIG. 1 shows a cross-sectional view of a rolling bearing using the cage of this embodiment. The rolling bearing 1 includes an inner ring 2 and an outer ring 3, a plurality of rolling elements 4 interposed between the raceway surfaces 2a and 3a of the inner and outer rings 2 and 3, and a ring-shaped holding for holding the plurality of rolling elements 4. It becomes with vessel 5. The rolling bearing 1 is a grease-lubricated angular ball bearing, and the rolling elements 4 are balls.

保持器５は、図２に示すように、円周方向の複数箇所に転動体４を保持するポケット６を有する。ポケット６は、保持器５の幅方向の中間の位置に設けられている。保持器５の幅方向の両端の内径ｄ１は、幅方向の中央の内径ｄ２よりも小さい寸法（ｄ１＜ｄ２）とされている。すなわち、保持器５の内周面は、それぞれ円筒面状とされた中央内周面部分５ａと、この中央内周面部分５ａに段差をもって隣接する両側の端部内周面部分５ｂ，５ｂとからなり、端部内周面部分５ｂの内径寸法がｄ１、中央内周面分５ａの内径寸法がｄ２とされている。中央内周面部分５ａは、ポケット６の幅よりも広い幅とされている。なお、保持器５の材質や案内形式は限定されない。   As shown in FIG. 2, the cage 5 has pockets 6 that hold the rolling elements 4 at a plurality of locations in the circumferential direction. The pocket 6 is provided at an intermediate position in the width direction of the cage 5. The inner diameter d1 at both ends in the width direction of the cage 5 is smaller than the inner diameter d2 at the center in the width direction (d1 <d2). That is, the inner peripheral surface of the cage 5 includes a central inner peripheral surface portion 5a having a cylindrical surface shape, and end inner peripheral surface portions 5b and 5b on both sides adjacent to the central inner peripheral surface portion 5a with a step. Thus, the inner diameter dimension of the end inner peripheral surface portion 5b is d1, and the inner diameter dimension of the central inner peripheral surface portion 5a is d2. The center inner peripheral surface portion 5 a is wider than the width of the pocket 6. In addition, the material and guidance form of the holder | retainer 5 are not limited.

この構成の保持器５を備えた転がり軸受１によると、グリース潤滑で使用した場合、運転に伴って保持器５に遠心力が作用して、図３のように保持器内径面に付着したグリースＧが中央部から端部に向かって移動しても、中央内周面部分５ａに対して両側の端部内周面部分５ｂは段差をなすように内径ｄ１が小さくされているので、グリースＧは保持器内径面の端部もしくは中央部付近で保持される。また、中央内周面部分５ａは、ポケット６の幅よりも広いものとされているので、従来の保持器１５（図１２）の場合に比べて、転動体４の近傍に多くのグリースＧが存在できることとなり、高速用途における潤滑の信頼性が高まる。   According to the rolling bearing 1 having the cage 5 of this configuration, when used in grease lubrication, a centrifugal force acts on the cage 5 during operation, and the grease adhered to the inner surface of the cage as shown in FIG. Even if G moves from the central portion toward the end portion, the inner diameter d1 is made small so that the end inner peripheral surface portions 5b on both sides form a step with respect to the central inner peripheral surface portion 5a. It is held near the end or center of the inner diameter surface of the cage. Further, since the central inner peripheral surface portion 5a is wider than the width of the pocket 6, more grease G is present in the vicinity of the rolling element 4 than in the case of the conventional cage 15 (FIG. 12). This increases the reliability of lubrication in high speed applications.

この発明の他の実施形態を図４および図５に示す。図４は転がり軸受の断面図を示す。この転がり軸受１Ａは、図１の転がり軸受１と同様のアンギュラ玉軸受であるが、図５のように、保持器５の内周面は、幅方向の中央が最も大径となる断面山形の傾斜面５ｃとされている。その他の構成は図１〜図３の実施形態の場合と同様である。   Another embodiment of the present invention is shown in FIGS. FIG. 4 shows a sectional view of the rolling bearing. This rolling bearing 1A is an angular ball bearing similar to the rolling bearing 1 of FIG. 1, but as shown in FIG. 5, the inner peripheral surface of the cage 5 has a mountain-shaped cross section where the center in the width direction has the largest diameter. The inclined surface 5c is used. Other configurations are the same as those in the embodiment of FIGS.

この実施形態の場合、運転に伴ってグリースに遠心力が作用しても、内径面に付着したグリースは中央部近傍で保持される。その結果、転動体近傍にはより多くのグリースが存在することができるため、高速用途における潤滑の信頼性を高めることができる。   In the case of this embodiment, even if a centrifugal force acts on the grease during operation, the grease adhering to the inner surface is held near the center. As a result, more grease can be present in the vicinity of the rolling elements, thereby improving the reliability of lubrication in high-speed applications.

この発明のさらに他の実施形態を図６および図７に示す。図６は転がり軸受の断面図を示す。この転がり軸受１Ｂは図４の転がり軸受１Ａと同様のアンギュラ玉軸受であるが、保持器５の内周面は、図７のように幅方向の中央が最も大径となる断面が円弧状の山形となった傾斜面５ｄとされている。その他の構成は図１〜図３の実施形態の場合と同様である。   Yet another embodiment of the present invention is shown in FIGS. FIG. 6 shows a sectional view of the rolling bearing. This rolling bearing 1B is an angular ball bearing similar to the rolling bearing 1A of FIG. 4, but the inner peripheral surface of the cage 5 has an arc-shaped cross section where the center in the width direction is the largest as shown in FIG. The inclined surface 5d has a mountain shape. Other configurations are the same as those in the embodiment of FIGS.

この実施形態の場合も、保持器５に遠心力が作用すると、保持器内周面が断面山形の傾斜面５ｄとされているので、保持器内周面に付着したグリースＧは中央部付近で保持されることになり、高速用途における潤滑の信頼性が高まる。   Also in this embodiment, when a centrifugal force acts on the cage 5, the cage inner peripheral surface is an inclined surface 5d having a mountain-shaped cross section, so that the grease G adhering to the cage inner peripheral surface is near the center. This increases the reliability of lubrication in high-speed applications.

この発明のさらに他の実施形態を図８および図９に示す。図８は転がり軸受の断面図を示す。この転がり軸受１Ｃは、図１の転がり軸受１と同様のアンギュラ玉軸受であるが、図９のように保持器５の内周面が形成されている。この保持器内径面は、それぞれ円筒面状とされた中央内周面部分５ａと、この中央内周面部分５ａに段差をもって隣接する両側の端部内周面部分５ｂ，５ｂと、中央内周面部分５ａと端部内周面部分５ｂの間に設けた円周溝５ｅとからなる。端部内周面部分５ｂの内径寸法ｄ１が、中央内周面分５ａの内径寸法ｄ２より小さくされていることは、図１〜図３の実施形態の場合と同様である。   Still another embodiment of the present invention is shown in FIGS. FIG. 8 shows a sectional view of the rolling bearing. This rolling bearing 1C is an angular ball bearing similar to the rolling bearing 1 of FIG. 1, but the inner peripheral surface of the cage 5 is formed as shown in FIG. The inner diameter surface of the cage includes a central inner peripheral surface portion 5a having a cylindrical surface shape, end inner peripheral surface portions 5b and 5b on both sides adjacent to the central inner peripheral surface portion 5a with a step, and a central inner peripheral surface. It consists of a circumferential groove 5e provided between the portion 5a and the end inner peripheral surface portion 5b. The inner diameter dimension d1 of the end inner peripheral surface portion 5b is smaller than the inner diameter dimension d2 of the central inner peripheral surface portion 5a, as in the embodiment of FIGS.

この実施形態の場合には、中央内周面部分５ａと端部内周面部分５ｂの間に設けた円周溝５ｅによってグリースＧの保持空間が拡張されることになる。そのため、保持器５の内周面に付着したグリースＧが、より多く中央部付近で保持され、高速用途における潤滑の信頼性がより高まる。   In the case of this embodiment, the holding space for the grease G is expanded by the circumferential groove 5e provided between the central inner peripheral surface portion 5a and the end inner peripheral surface portion 5b. Therefore, more grease G adhering to the inner peripheral surface of the cage 5 is held in the vicinity of the central portion, and the reliability of lubrication in high-speed applications is further increased.

なお、以上の各実施形態では、保持器５の断面形状を幅方向に左右対称なものとしているが、これに限らず、例えば左半部の断面形状を図２のようにし、右半部の断面形状を図５のようにした左右非対称なものであっても、上記各実施形態と同様の効果を得ることができる。   In each of the above embodiments, the cross-sectional shape of the cage 5 is symmetrical in the width direction. However, the present invention is not limited to this. For example, the cross-sectional shape of the left half is as shown in FIG. Even if the cross-sectional shape is asymmetrical as shown in FIG. 5, the same effects as those of the above embodiments can be obtained.

この発明のさらに他の実施形態を図１０に示す。この実施形態の保持器を用いた転がり軸受１Ｄは、図１の転がり軸受１と同様のアンギュラ玉軸受であるが、この場合はシール付きとされている。すなわち、この転がり軸受１Ｄは、内外輪２，３間の空間の両端をシール７で密封した密封形とされている。保持器５の内周面が、それぞれ円筒面状とされた中央内周面部分５ａと、この中央内周面部分５ａに段差をもって隣接する両側の端部内周面部分５ｂ，５ｂとからなり、端部内周面部分５ｂの内径寸法がｄ１、中央内周面分５ａの内径寸法がｄ２とされていること、および中央内周面部分５ａがポケット６の幅よりも広いものとされていることは図１〜図３の実施形態の場合と同様である。   Yet another embodiment of the present invention is shown in FIG. The rolling bearing 1D using the cage of this embodiment is an angular ball bearing similar to the rolling bearing 1 of FIG. 1, but in this case, it is sealed. That is, the rolling bearing 1D is a sealed type in which both ends of the space between the inner and outer rings 2 and 3 are sealed with the seals 7. The inner peripheral surface of the cage 5 is composed of a central inner peripheral surface portion 5a having a cylindrical surface shape, and end inner peripheral surface portions 5b and 5b on both sides adjacent to the central inner peripheral surface portion 5a with a step, The inner diameter of the end inner peripheral surface portion 5b is d1, the inner diameter of the central inner peripheral surface portion 5a is d2, and the central inner peripheral surface portion 5a is wider than the width of the pocket 6. Is the same as that of the embodiment of FIGS.

この実施形態の場合、運転によって攪拌されたグリースを、シール７が軸受内部に保持する働きを持つので、保持器５の構造と相まって、転動体４の近傍におけるグリースの保持性をより高めることができる。   In the case of this embodiment, since the seal 7 has the function of holding the grease agitated by the operation inside the bearing, it is possible to improve the retention of the grease in the vicinity of the rolling element 4 in combination with the structure of the cage 5. it can.

なお、上記各実施形態では、この発明の保持器をアンギュラ玉軸受に適用した場合を示したが、これに限らず深溝玉軸受やころ軸受に適用した場合でも、上記と同様にグリースの保持性を向上させることができる。   In each of the above embodiments, the cage of the present invention is applied to an angular ball bearing. However, the present invention is not limited to this, and even when applied to a deep groove ball bearing or a roller bearing, the grease retainability is the same as described above. Can be improved.

この発明の第１の実施形態にかかる保持器を用いた転がり軸受の断面図である。It is sectional drawing of the rolling bearing using the holder | retainer concerning 1st Embodiment of this invention. 同保持器の断面図である。It is sectional drawing of the holder | retainer. 同保持器によるグリースの保持性を示す説明図である。It is explanatory drawing which shows the retainability of the grease by the retainer. この発明の他の実施形態にかかる保持器を用いた転がり軸受の断面図である。It is sectional drawing of the rolling bearing using the holder | requirement concerning other embodiment of this invention. 同保持器の断面図である。It is sectional drawing of the holder | retainer. この発明のさらに他の実施形態にかかる保持器を用いた転がり軸受の断面図である。It is sectional drawing of the rolling bearing using the holder | requirement concerning further another embodiment of this invention. 同保持器の断面図である。It is sectional drawing of the holder | retainer. この発明のさらに他の実施形態にかかる保持器を用いた転がり軸受の断面図である。It is sectional drawing of the rolling bearing using the holder | requirement concerning further another embodiment of this invention. 同保持器の断面図である。It is sectional drawing of the holder | retainer. この発明のさらに他の実施形態にかかる保持器を用いた転がり軸受の断面図である。It is sectional drawing of the rolling bearing using the holder | requirement concerning further another embodiment of this invention. 軸受の潤滑に用いられる油量と、摩擦損失および軸受温度との関係を示すグラフである。It is a graph which shows the relationship between the oil quantity used for lubrication of a bearing, friction loss, and bearing temperature. 転がり軸受用保持器の各従来例を示す断面図である。It is sectional drawing which shows each conventional example of the cage for rolling bearings.

符号の説明Explanation of symbols

１，１Ａ〜１Ｄ…転がり軸受
４…転動体
５…保持器
５ａ…中央内周面部分
５ｂ…端部内周面部分
５ｃ，５ｄ…傾斜面
５ｅ…円周溝
６…ポケット
７…シール DESCRIPTION OF SYMBOLS 1,1A-1D ... Rolling bearing 4 ... Rolling body 5 ... Cage 5a ... Center inner peripheral surface part 5b ... End inner peripheral surface part 5c, 5d ... Inclined surface 5e ... Circumferential groove 6 ... Pocket 7 ... Seal

Claims (6)

リング状の保持器の円周方向複数箇所における幅方向の中間に、転動体を保持するポケットを有し、グリース潤滑の転がり軸受に用いられる保持器において、保持器の幅方向の両端の内径が、幅方向の中央の内径よりも小さな寸法であることを特徴とする転がり軸受用保持器。   In a cage used for a grease-lubricated rolling bearing having pockets for holding rolling elements in the middle in the width direction at a plurality of circumferential locations of a ring-shaped cage, the inner diameters at both ends in the width direction of the cage are A cage for a rolling bearing having a size smaller than the inner diameter at the center in the width direction. 請求項１において、保持器の内周面が、それぞれ円筒面状とされた中央内周面部分、およびこの中央内周面部分に段差をもって隣接する両側の端部内周面部分からなり、中央内周面部分は、前記ポケットの幅よりも広いものとした転がり軸受用保持器。   2. The inner peripheral surface of the cage according to claim 1, comprising a central inner peripheral surface portion having a cylindrical surface shape and end inner peripheral surface portions on both sides adjacent to the central inner peripheral surface portion with a step. A rolling bearing retainer having a peripheral surface portion wider than the width of the pocket. 請求項１において、保持器の内周面が、幅方向の中央が最も大径となる断面山形の傾斜面からなる転がり軸受用保持器。   The rolling bearing retainer according to claim 1, wherein the inner peripheral surface of the retainer is an inclined surface having a mountain-shaped cross section having a largest diameter in the center in the width direction. 請求項２において、中央内周面部分と端部内周面部分の間に円周溝を設けた転がり軸受用保持器。   The rolling bearing retainer according to claim 2, wherein a circumferential groove is provided between the central inner peripheral surface portion and the end inner peripheral surface portion. 請求項１ないし請求項４のいずれか１項において、アンギュラ玉軸受に用いられるものである転がり軸受用保持器。   The rolling bearing retainer according to any one of claims 1 to 4, wherein the cage is used for an angular ball bearing. 請求項１ないし請求項５のいずれか１項において、密封形の軸受で使用されたものである転がり軸受用保持器。   The rolling bearing retainer according to any one of claims 1 to 5, which is used in a sealed bearing.
JP2005149241A 2005-05-23 2005-05-23 Rolling bearing cage Pending JP2006329218A (en)

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Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2009162341A (en) * 2008-01-09 2009-07-23 Ntn Corp Rolling bearing
WO2010088363A1 (en) * 2009-01-28 2010-08-05 The Timken Company Oscillating ball bearing
WO2012108508A1 (en) * 2011-02-09 2012-08-16 株式会社ジェイテクト Rolling bearing device for wheel
EP2386772A3 (en) * 2010-05-12 2013-05-15 Jtekt Corporation Rolling bearing with internal lubrication
EP2835545A3 (en) * 2013-08-06 2015-06-03 Rolls-Royce plc Bearing cage with oil circulation means
JP2015129547A (en) * 2014-01-07 2015-07-16 日本精工株式会社 rolling bearing
JP2016106207A (en) * 2016-03-14 2016-06-16 日本精工株式会社 Angular ball bearing
JP2016130583A (en) * 2016-03-14 2016-07-21 日本精工株式会社 Angular ball bearing
CN108368882A (en) * 2015-12-10 2018-08-03 舍弗勒技术股份两合公司 Ball-bearing retainer
WO2020090572A1 (en) * 2018-10-29 2020-05-07 Ntn株式会社 Ball bearing

Cited By (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2009162341A (en) * 2008-01-09 2009-07-23 Ntn Corp Rolling bearing
WO2010088363A1 (en) * 2009-01-28 2010-08-05 The Timken Company Oscillating ball bearing
EP2386772A3 (en) * 2010-05-12 2013-05-15 Jtekt Corporation Rolling bearing with internal lubrication
US8523449B2 (en) 2010-05-12 2013-09-03 Jtekt Corporation Rolling bearing
WO2012108508A1 (en) * 2011-02-09 2012-08-16 株式会社ジェイテクト Rolling bearing device for wheel
JP2012167683A (en) * 2011-02-09 2012-09-06 Jtekt Corp Rolling bearing device for wheel
CN103348152A (en) * 2011-02-09 2013-10-09 株式会社捷太格特 Rolling bearing device for wheel
US8882359B2 (en) 2011-02-09 2014-11-11 Jtekt Corporation Wheel rolling bearing unit
EP2835545A3 (en) * 2013-08-06 2015-06-03 Rolls-Royce plc Bearing cage with oil circulation means
US9194432B2 (en) 2013-08-06 2015-11-24 Rolls-Royce Plc Tapered oil feed bearing cage
JP2015129547A (en) * 2014-01-07 2015-07-16 日本精工株式会社 rolling bearing
WO2015104943A1 (en) * 2014-01-07 2015-07-16 日本精工株式会社 Rolling bearing
CN108368882A (en) * 2015-12-10 2018-08-03 舍弗勒技术股份两合公司 Ball-bearing retainer
US20180363706A1 (en) * 2015-12-10 2018-12-20 Schaeffler Technologies AG & Co. KG Ball bearing cage
JP2016106207A (en) * 2016-03-14 2016-06-16 日本精工株式会社 Angular ball bearing
JP2016130583A (en) * 2016-03-14 2016-07-21 日本精工株式会社 Angular ball bearing
WO2020090572A1 (en) * 2018-10-29 2020-05-07 Ntn株式会社 Ball bearing
JP2020070814A (en) * 2018-10-29 2020-05-07 Ntn株式会社 Ball bearing
JP7186061B2 (en) 2018-10-29 2022-12-08 Ntn株式会社 ball bearing

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