JP3199821U - Double row angular contact ball bearings - Google Patents

Double row angular contact ball bearings Download PDF

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JP3199821U
JP3199821U JP2015003313U JP2015003313U JP3199821U JP 3199821 U JP3199821 U JP 3199821U JP 2015003313 U JP2015003313 U JP 2015003313U JP 2015003313 U JP2015003313 U JP 2015003313U JP 3199821 U JP3199821 U JP 3199821U
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outer ring
angular contact
row angular
contact ball
double
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田邉　晃一
晃一 田邉
敏明 瀬戸
敏明 瀬戸
阿部　大輔
大輔 阿部
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NSK Ltd
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Abstract

【課題】軌道輪の真円度が優れている複列アンギュラ玉軸受を提供する。【解決手段】産業機械ポンプ用の複列アンギュラ玉軸受は、内輪１と、外輪２と、２列の玉３と、各列の玉３をそれぞれ保持する保持器４，４と、略円板状部材からなる非接触形の密封装置５，５と、を備えている。密封装置５の径方向外端部５ａは、略円板状部材の径方向最外端部を径方向反対側に折り返すことにより形成されており、外輪２の内周面の溝２ｂに嵌入され加締められることにより取り付けられている。また、玉３の直径が軸受幅の半分の７５％以上８３％以下とされている。さらに、密封装置５の厚さＴｓと、外輪２の外径面と溝２ｂの底部との間の径方向距離Ｔｒとの比Ｔｓ／Ｔｒは、０．０７以下とされている。外輪２の外径面と内周面との間の径方向距離は、軌道面２ａの軸方向外側に形成される外側肩部よりも２列の軌道面２ａの間に形成される内側肩部の方が大きくなっている。【選択図】図２A double-row angular contact ball bearing having excellent roundness of a raceway is provided. A double row angular contact ball bearing for an industrial machine pump includes an inner ring 1, an outer ring 2, two rows of balls 3, cages 4 and 4 for holding the balls 3 of each row, and a substantially disc. And non-contact type sealing devices 5 and 5 made of a member. The radially outer end portion 5 a of the sealing device 5 is formed by folding back the radially outermost end portion of the substantially disk-shaped member to the opposite side in the radial direction, and is fitted into the groove 2 b on the inner peripheral surface of the outer ring 2. It is attached by crimping. Further, the diameter of the balls 3 is 75% or more and 83% or less of half of the bearing width. Furthermore, the ratio Ts / Tr between the thickness Ts of the sealing device 5 and the radial distance Tr between the outer diameter surface of the outer ring 2 and the bottom of the groove 2b is 0.07 or less. The radial distance between the outer diameter surface and the inner peripheral surface of the outer ring 2 is such that the inner shoulder portion formed between the two raceway surfaces 2a rather than the outer shoulder portion formed on the outer side in the axial direction of the raceway surface 2a. Is bigger. [Selection] Figure 2

Description

本考案は複列アンギュラ玉軸受に関する。   The present invention relates to a double row angular contact ball bearing.

水中ポンプの回転軸を回転自在に支持する転がり軸受として、複列アンギュラ玉軸受が使用される。ポンプ用軸受に求められる性能としては長寿命があるが、長寿命を実現するための軸受性能として高定格荷重（高負荷容量）が要求される。そして、高負荷容量化の手段としては、従来から、転動体（玉）の大径化が知られている（例えば特許文献１を参照）。   A double-row angular contact ball bearing is used as a rolling bearing that rotatably supports the rotary shaft of the submersible pump. The performance required for the pump bearing has a long life, but a high rated load (high load capacity) is required as a bearing performance for realizing the long life. As a means for increasing the load capacity, it is conventionally known to increase the diameter of rolling elements (balls) (see, for example, Patent Document 1).

また、長寿命を実現するための軸受性能として、密封性も要求される。すなわち、ポンプ用軸受に密封装置を設けて、外部から内部への異物，塵埃の侵入の防止や、内部から外部への潤滑剤の漏洩の防止を行う必要がある。
密封装置としては、例えば、鋼板からなるシールドが知られている。シールドを転がり軸受に取り付ける場合には、例えば、シールドの径方向外端部を、外輪の内周面に形成されたシールド溝に嵌合した上、加締めて固定する。 In addition, sealing performance is also required as a bearing performance for realizing a long life. That is, it is necessary to provide a sealing device for the pump bearing to prevent foreign matter and dust from entering from the outside to the inside and to prevent leakage of the lubricant from the inside to the outside.
As a sealing device, for example, a shield made of a steel plate is known. When the shield is attached to the rolling bearing, for example, the outer end portion in the radial direction of the shield is fitted into a shield groove formed on the inner peripheral surface of the outer ring and then fixed by crimping.

特開２００６−１０５３８４号公報JP 2006-105384 A

しかしながら、加締め時に外輪に大きな力が付加されるため、外輪が変形して外径面の真円度が悪化する場合があった。特に、シールド溝の底部から外輪の外径面までの径方向距離（すなわち、シールド溝の底部における外輪の厚さ）が小さい場合は、外輪の剛性が低いため真円度の悪化が生じやすかった。その結果、複列アンギュラ玉軸受をポンプのハウジングに取り付ける際の取付性が低下したり、複列アンギュラ玉軸受の回転時に異音が発生したりするおそれがあった。
そこで、本考案は上記のような従来技術が有する問題点を解決し、軌道輪の真円度が優れている複列アンギュラ玉軸受を提供することを課題とする。 However, since a large force is applied to the outer ring during caulking, the outer ring may be deformed and the roundness of the outer diameter surface may deteriorate. In particular, when the radial distance from the bottom of the shield groove to the outer diameter surface of the outer ring (that is, the thickness of the outer ring at the bottom of the shield groove) is small, the roundness is likely to deteriorate due to the low rigidity of the outer ring. . As a result, there is a possibility that the mounting property when mounting the double row angular ball bearing to the housing of the pump is deteriorated or abnormal noise is generated when the double row angular ball bearing rotates.
Therefore, the present invention has an object to solve the above-mentioned problems of the prior art and to provide a double-row angular contact ball bearing in which the roundness of the race is excellent.

前記課題を解決するため、本考案は次のような構成からなる。すなわち、本考案の一態様に係る複列アンギュラ玉軸受は、内輪と、外輪と、前記内輪の２列の軌道面と前記外輪の２列の軌道面との間に転動自在に配された２列の転動体と、前記外輪に取り付けられ前記内輪に滑り接触又は隙間を空けて対向する略円板状の密封装置と、前記内輪と前記外輪との間に前記転動体を保持する保持器と、を備え、前記転動体の直径が軸受幅の半分の７５％以上８３％以下である産業機械ポンプ用の複列アンギュラ玉軸受であって、前記密封装置の径方向一端部が、最端部を径方向反対側に折り返すことにより形成されて、前記外輪に設けられた凹部に加締めにより取り付けられており、前記密封装置の厚さＴｓと、前記外輪の外径面と前記凹部の底部との間の径方向距離Ｔｒとの比Ｔｓ／Ｔｒが、０．０７以下であり、前記外輪の外径面と内周面との間の径方向距離は、前記軌道面の軸方向外側に形成される外側肩部よりも２列の前記軌道面の間に形成される内側肩部の方が大きくなっていることを特徴とする。   In order to solve the above problems, the present invention has the following configuration. That is, the double-row angular contact ball bearing according to an aspect of the present invention is arranged to roll freely between an inner ring, an outer ring, two rows of raceway surfaces of the inner ring, and two rows of raceways of the outer ring. Two rows of rolling elements, a substantially disk-shaped sealing device that is attached to the outer ring and faces the inner ring with a sliding contact or a gap, and a cage that holds the rolling element between the inner ring and the outer ring And a double row angular contact ball bearing for an industrial machine pump in which the diameter of the rolling element is not less than 75% and not more than 83% of a half of the bearing width, wherein one end in the radial direction of the sealing device is the outermost end. Is formed by folding the portion back to the opposite side in the radial direction, and is attached by caulking to a recess provided in the outer ring, the thickness Ts of the sealing device, the outer diameter surface of the outer ring, and the bottom of the recess The ratio Ts / Tr with respect to the radial distance Tr is 0.07 or less And the radial distance between the outer diameter surface and the inner peripheral surface of the outer ring is an inner side formed between the two rows of the raceway surfaces rather than an outer shoulder portion formed on the outer side in the axial direction of the raceway surface. It is characterized in that the shoulder is larger.

上記複列アンギュラ玉軸受においては、前記密封装置は、金属材料製であるとともに、前記径方向一端部と、径方向に沿って配され前記内輪の外周面と前記外輪の内周面との間の開口を覆う平板部と、前記径方向一端部と前記平板部とを連結する連結部と、を有し、前記平板部と前記連結部の接続部分は軸方向外側に向かって凸をなす屈曲部となっており、該屈曲部が前記保持器の外径部よりも径方向外方に配されていてもよい。   In the double row angular contact ball bearing, the sealing device is made of a metal material, and is arranged along the radial direction end portion and between the outer peripheral surface of the inner ring and the inner peripheral surface of the outer ring. And a connecting portion that connects the one end portion in the radial direction and the flat plate portion, and the connecting portion between the flat plate portion and the connecting portion is a convex bent outward in the axial direction. The bent portion may be disposed radially outward from the outer diameter portion of the cage.

また、前記保持器が金属材料製の冠形保持器であってもよい。さらに、前記密封装置の径方向一端部の軸方向幅が２．７ｍｍ以下であってもよい。さらに、前記転動体の直径が軸受幅の半分の８０％以上８３％以下であってもよい。さらに、前記外輪の外径が５０ｍｍ以上１４０ｍｍ以下であってもよい。   Further, the cage may be a crown-shaped cage made of a metal material. Further, the axial width of one end portion in the radial direction of the sealing device may be 2.7 mm or less. Further, the diameter of the rolling element may be 80% or more and 83% or less of half of the bearing width. Furthermore, the outer diameter of the outer ring may be not less than 50 mm and not more than 140 mm.

本考案の複列アンギュラ玉軸受は、外輪に設けられた凹部に密封装置の径方向一端部が加締めにより取り付けられており、密封装置の厚さＴｓと外輪の外径面と凹部の底部との間の径方向距離Ｔｒとの比Ｔｓ／Ｔｒが０．０７以下とされているため、凹部の底部における外輪の厚さが大きい。よって、外輪の剛性が高いので、加締め時に外輪の真円度が悪化しにくく、本考案の複列アンギュラ玉軸受は、外輪の真円度が優れている。   In the double row angular contact ball bearing of the present invention, one end in the radial direction of the sealing device is attached by caulking to a recess provided in the outer ring, and the thickness Ts of the sealing device, the outer diameter surface of the outer ring, the bottom of the recess, Since the ratio Ts / Tr with respect to the radial distance Tr is 0.07 or less, the thickness of the outer ring at the bottom of the recess is large. Therefore, since the rigidity of the outer ring is high, the roundness of the outer ring is hardly deteriorated during caulking, and the double-row angular contact ball bearing of the present invention has an excellent roundness of the outer ring.

本考案に係る複列アンギュラ玉軸受の一実施形態を示す部分縦断面図である。It is a fragmentary longitudinal cross-section which shows one Embodiment of the double row angular contact ball bearing which concerns on this invention. 図１の複列アンギュラ玉軸受に組み込まれた密封装置及びその周辺部分の部分拡大断面図である。It is the elements on larger scale of the sealing device integrated in the double row angular contact ball bearing of Drawing 1, and its peripheral part. 実施例の軸受の外輪の真円度を測定した結果を示す図である。It is a figure which shows the result of having measured the roundness of the outer ring | wheel of the bearing of an Example. 比較例の軸受の外輪の真円度を測定した結果を示す図である。It is a figure which shows the result of having measured the roundness of the outer ring | wheel of the bearing of a comparative example. 参考例の軸受の外輪の真円度を測定した結果を示す図である。It is a figure which shows the result of having measured the roundness of the outer ring | wheel of the bearing of a reference example.

本考案に係る複列アンギュラ玉軸受の実施の形態を、図面を参照しながら詳細に説明する。図１は、本考案に係る複列アンギュラ玉軸受の一実施形態を示す部分縦断面図である。また、図２は、図１の複列アンギュラ玉軸受に組み込まれた密封装置及びその周辺部分の部分拡大断面図である。
図１の複列アンギュラ玉軸受は、内輪１と、外輪２と、内輪１の軌道面１ａ，１ａと外輪２の軌道面２ａ，２ａとの間に転動自在に配された２列の玉３（転動体）と、内輪１と外輪２との間に各列の玉３をそれぞれ保持する保持器４，４と、略円板状部材からなる非接触形の密封装置５，５と、を備えている。そして、内輪１と外輪２と密封装置５，５とで囲まれた空隙部（軸受内部空間）内には、両軌道面１ａ，２ａと転動体３の転動面３ａとの潤滑を行う図示しない潤滑剤（例えば潤滑油，グリース）が配されている。なお、密封装置５は、軌道輪（図１の場合は内輪１）に滑り接触する接触形の密封装置であってもよい。また、保持器４は備えていなくてもよい。 An embodiment of a double-row angular contact ball bearing according to the present invention will be described in detail with reference to the drawings. FIG. 1 is a partial longitudinal sectional view showing an embodiment of a double-row angular contact ball bearing according to the present invention. 2 is a partially enlarged cross-sectional view of the sealing device incorporated in the double row angular contact ball bearing of FIG. 1 and its peripheral portion.
The double-row angular contact ball bearing shown in FIG. 1 has two rows of balls which are arranged to roll freely between an inner ring 1, an outer ring 2, and raceway surfaces 1 a and 1 a of the inner ring 1 and raceway surfaces 2 a and 2 a of the outer ring 2. 3 (rolling elements), retainers 4 and 4 for holding the balls 3 in each row between the inner ring 1 and the outer ring 2, and non-contact type sealing devices 5 and 5 made of a substantially disk-shaped member, It has. And in the space | gap part (bearing internal space) enclosed with the inner ring | wheel 1, the outer ring | wheel 2, and the sealing devices 5 and 5, lubrication with both the raceway surfaces 1a and 2a and the rolling surface 3a of the rolling element 3 is shown. Do not use lubricants (for example, lubricating oil and grease). The sealing device 5 may be a contact-type sealing device that is in sliding contact with the raceway ring (inner ring 1 in the case of FIG. 1). Further, the cage 4 may not be provided.

内輪１，外輪２，及び玉３は、転がり軸受の軌道輪や転動体の素材として一般的に採用される鉄鋼材料（例えばステンレス鋼，軸受鋼）で構成されている。また、保持器４は、転がり軸受の保持器の素材として一般的に採用される樹脂材料（例えばポリアミド，ポリフェニレンスルフィド）又は金属材料（例えば鋼，黄銅，アルミニウム合金）で構成されている。
さらに、密封装置５は、鋼等の金属材料で構成されており（このような密封装置の例としては、鋼板製のシールドがあげられる）、その径方向外端部５ａが外輪２の内周面の軸方向両端部に取り付けられている。詳述すると、外輪２の内周面の軸方向両端部に形成された溝２ｂ（凹部）に、密封装置５の径方向外端部５ａが嵌入され加締められることにより取り付けられている。 The inner ring 1, the outer ring 2, and the ball 3 are made of a steel material (for example, stainless steel or bearing steel) that is generally employed as a material for a bearing ring or rolling element of a rolling bearing. The cage 4 is made of a resin material (for example, polyamide, polyphenylene sulfide) or a metal material (for example, steel, brass, aluminum alloy) generally adopted as a material for the cage of the rolling bearing.
Furthermore, the sealing device 5 is made of a metal material such as steel (an example of such a sealing device is a steel plate shield), and its radially outer end 5a is the inner periphery of the outer ring 2. Attached to both axial ends of the surface. More specifically, the outer circumferential end 5a of the sealing device 5 is fitted into the grooves 2b (concave portions) formed at both axial ends of the inner peripheral surface of the outer ring 2 by being fitted and crimped.

密封装置５の径方向外端部５ａは、前記略円板状部材の径方向最外端部を径方向反対側（すなわち径方向内端側）に折り返すことにより形成されて、断面略Ｕ字状（軸方向に沿う平面による断面）をなしており、この断面略Ｕ字状の径方向外端部５ａが溝２ｂに嵌入され加締められている。
このとき、従来の同寸法の複列アンギュラ玉軸受と比べて、密封装置５を構成する前記略円板状部材の厚さＴｓは薄くなっているとともに、溝２ｂの底部における外輪２の厚さ（すなわち、外輪２の外径面と溝２ｂの底部との間の径方向距離）Ｔｒは大きくなっている。さらに、密封装置５の厚さＴｓと溝２ｂの底部における外輪２の厚さＴｒとの比Ｔｓ／Ｔｒは、０．０７以下とされている。また、断面略Ｕ字状の径方向外端部５ａの軸方向幅Ｔｃは、２．７ｍｍ以下とされている。 The radially outer end portion 5a of the sealing device 5 is formed by folding back the radially outermost end portion of the substantially disk-shaped member to the radially opposite side (that is, the radially inner end side), and has a substantially U-shaped cross section. A radially outer end 5a having a substantially U-shaped cross section is fitted into the groove 2b and crimped.
At this time, the thickness Ts of the substantially disk-shaped member constituting the sealing device 5 is thinner and the thickness of the outer ring 2 at the bottom of the groove 2b as compared with a conventional double row angular contact ball bearing of the same size. (That is, the radial distance between the outer diameter surface of the outer ring 2 and the bottom of the groove 2b) Tr is large. Furthermore, the ratio Ts / Tr between the thickness Ts of the sealing device 5 and the thickness Tr of the outer ring 2 at the bottom of the groove 2b is 0.07 or less. The axial width Tc of the radially outer end 5a having a substantially U-shaped cross section is set to 2.7 mm or less.

そして、密封装置５の径方向内端部５ｂが、内輪１の外周面に隙間（ラビリンス隙間）を空けて対向している。内輪１の外周面のうち径方向内端部５ｂに対向する部分である対向面１ｂは、径方向内端部５ｂと隙間を介して対向することによりラビリンスを形成している。
上記のように、本実施形態の複列アンギュラ玉軸受は、従来の同寸法の複列アンギュラ玉軸受と比べて、密封装置５を構成する略円板状部材の厚さＴｓが薄いので、溝２ｂの底部における外輪２の厚さを大きくすることができる。その結果、外輪２の剛性が高くなるので、密封装置５の加締め装着時に外輪２の変形が生じにくい。前記厚さの比Ｔｓ／Ｔｒが０．０７超過であると、外輪２の剛性が不十分となって、密封装置５の加締め装着時に外輪２の変形が生じるおそれがある。 The radially inner end 5b of the sealing device 5 is opposed to the outer peripheral surface of the inner ring 1 with a gap (labyrinth gap). A facing surface 1b, which is a portion facing the radially inner end portion 5b, of the outer peripheral surface of the inner ring 1 forms a labyrinth by facing the radially inner end portion 5b with a gap.
As described above, the double-row angular contact ball bearing of the present embodiment is thinner than the conventional double-row angular contact ball bearing of the same size because the thickness Ts of the substantially disk-shaped member constituting the sealing device 5 is thin. The thickness of the outer ring 2 at the bottom of 2b can be increased. As a result, since the rigidity of the outer ring 2 is increased, the outer ring 2 is not easily deformed when the sealing device 5 is caulked. If the thickness ratio Ts / Tr exceeds 0.07, the rigidity of the outer ring 2 becomes insufficient, and the outer ring 2 may be deformed when the sealing device 5 is caulked.

さらに、断面略Ｕ字状の径方向外端部５ａの軸方向幅Ｔｃが小さいので、密封装置５の加締めに要する力が小さい。その結果、密封装置５の加締め装着時に外輪２に付加される力が小さくなるので、加締め装着時に外輪２の変形が生じにくい。径方向外端部５ａの軸方向幅Ｔｃが２．７ｍｍ超過であると、密封装置５の加締めに要する力が大きくなるため、密封装置５の加締め装着時に外輪２に付加される力が大きくなり、外輪２に変形が生じるおそれがある。   Furthermore, since the axial width Tc of the radially outer end 5a having a substantially U-shaped cross section is small, the force required for caulking the sealing device 5 is small. As a result, the force applied to the outer ring 2 when the sealing device 5 is caulked is reduced, so that the outer ring 2 is not easily deformed when caulking. If the axial width Tc of the radially outer end 5a exceeds 2.7 mm, the force required for caulking of the sealing device 5 increases, and therefore the force applied to the outer ring 2 when the sealing device 5 is caulked and mounted. There is a risk that the outer ring 2 will be deformed.

このように、本実施形態の複列アンギュラ玉軸受は、密封装置５の加締め装着時に外輪２の変形が生じにくいので、外輪２の外径面の真円度が優れている。よって、本実施形態の複列アンギュラ玉軸受は、ポンプ等のハウジングに取り付ける際の取付性が優れているとともに、回転時に異音が発生しにくい。
また、従来品の複列アンギュラ玉軸受における玉の直径は、通常、軸受幅の半分の６８％以上７１％以下であるが、本実施形態の複列アンギュラ玉軸受においては、玉３の直径を大径とし、複列アンギュラ玉軸受の軸受幅の半分の７５％以上８３％以下に設定している。 As described above, the double row angular contact ball bearing of this embodiment is excellent in the roundness of the outer diameter surface of the outer ring 2 because the outer ring 2 is not easily deformed when the sealing device 5 is caulked. Therefore, the double-row angular contact ball bearing of the present embodiment has excellent mountability when mounted on a housing such as a pump and is unlikely to generate abnormal noise during rotation.
In addition, the diameter of the ball in the conventional double-row angular contact ball bearing is usually 68% or more and 71% or less of half of the bearing width, but in the double-row angular contact ball bearing of this embodiment, the diameter of the ball 3 is The diameter is set to 75% or more and 83% or less of half of the bearing width of the double row angular contact ball bearing.

玉３を大径にして軸受幅に対する玉３の直径の割合を大きくすれば、複列アンギュラ玉軸受は高負荷容量で長寿命となる。玉３の直径が軸受幅の半分の７５％未満であると、複列アンギュラ玉軸受の負荷容量が十分に向上しないおそれがある。一方、８３％超過であると、密封装置５と保持器４（又は玉３）との間の軸方向隙間が十分に確保できずに干渉するおそれがある。このような不都合がより生じにくくするためには、玉３の直径を軸受幅の半分の８０％以上８３％以下に設定することがより好ましい。   If the diameter of the ball 3 is increased and the ratio of the diameter of the ball 3 to the bearing width is increased, the double-row angular contact ball bearing has a high load capacity and a long life. If the diameter of the ball 3 is less than 75% of half of the bearing width, the load capacity of the double row angular ball bearing may not be sufficiently improved. On the other hand, if it exceeds 83%, the axial clearance between the sealing device 5 and the retainer 4 (or the ball 3) cannot be sufficiently ensured and there is a risk of interference. In order to make such inconvenience less likely to occur, it is more preferable to set the diameter of the ball 3 to 80% or more and 83% or less of half of the bearing width.

なお、外輪２が本考案の構成要件である「一方の軌道輪（密封装置が取り付けられた軌道輪）」に相当し、内輪１が本考案の構成要件である「他方の軌道輪（密封装置が滑り接触又は隙間を空けて対向する軌道輪）」に相当する。もちろん、密封装置５の径方向内端部５ｂが内輪１に取り付けられ、径方向外端部５ａが外輪２の内周面に隙間を空けて対向している構成としても差し支えない。また、密封装置５は、外輪２の内周面の軸方向片側端部のみに取り付けられていてもよい。   The outer ring 2 corresponds to “one race ring (track ring to which a sealing device is attached)” which is a constituent requirement of the present invention, and the inner ring 1 corresponds to “the other race ring (sealing device) which is a constituent requirement of the present invention. Corresponds to the raceway facing each other with a sliding contact or a gap. Of course, the radially inner end 5b of the sealing device 5 may be attached to the inner ring 1 and the radially outer end 5a may be opposed to the inner peripheral surface of the outer ring 2 with a gap. Further, the sealing device 5 may be attached only to one end portion in the axial direction of the inner peripheral surface of the outer ring 2.

また、本実施形態の複列アンギュラ玉軸受は、密封装置５を構成する略円板状部材の厚さＴｓが薄いので、密封装置５と保持器４（又は玉３）との間の軸方向隙間が十分に確保されやすい。したがって、玉３が大径であっても密封装置５と保持器４（又は玉３）とが干渉しにくいので、本実施形態の複列アンギュラ玉軸受は、玉３の直径の大径化による高負荷容量化を適用しやすい。   Moreover, since the thickness Ts of the substantially disc-shaped member which comprises the sealing device 5 is thin, the double row angular contact ball bearing of this embodiment is the axial direction between the sealing device 5 and the holder | retainer 4 (or ball | bowl 3). Sufficient clearance is easily secured. Therefore, even if the ball 3 has a large diameter, the sealing device 5 and the retainer 4 (or the ball 3) are unlikely to interfere with each other. Therefore, the double-row angular contact ball bearing of the present embodiment is based on an increase in the diameter of the ball 3. Easy to apply high load capacity.

さらに、密封装置５と保持器４（又は玉３）との間の軸方向隙間が十分に確保されていれば、玉３が大径であっても密封装置５と保持器４（又は玉３）とが干渉しにくいので、本実施形態の複列アンギュラ玉軸受は密封性に優れている（すなわち、軸受の外部から内部への異物，塵埃の侵入や、内部から外部への潤滑剤の漏洩が生じにくい）。さらに、密封装置５と保持器４（又は玉３）とが干渉しにくいため、密封装置５の脱落、潤滑剤の漏出、複列アンギュラ玉軸受からの異音、複列アンギュラ玉軸受の異常摩耗が生じにくい。   Furthermore, if the axial clearance between the sealing device 5 and the cage 4 (or ball 3) is sufficiently secured, the sealing device 5 and the cage 4 (or ball 3) even if the ball 3 has a large diameter. The double-row angular contact ball bearing of this embodiment has excellent sealing performance (that is, foreign matter and dust intrude from the outside to the inside of the bearing, and leakage of lubricant from the inside to the outside). Is less likely to occur). Further, since the sealing device 5 and the cage 4 (or the ball 3) do not easily interfere with each other, the sealing device 5 falls off, the lubricant leaks, the noise from the double row angular ball bearing, the abnormal wear of the double row angular ball bearing. Is unlikely to occur.

さらに、本実施形態の複列アンギュラ玉軸受は高負荷タイプの軸受であるので、外輪２の外径は５０ｍｍ以上１４０ｍｍ以下とすることが好ましい。
上記のような優れた特性を有していることから、本実施形態の複列アンギュラ玉軸受は、水中ポンプ等のポンプの回転軸を回転自在に支持する転がり軸受として好適に使用可能である。 Furthermore, since the double row angular contact ball bearing of this embodiment is a high load type bearing, it is preferable that the outer diameter of the outer ring 2 be 50 mm or more and 140 mm or less.
Because of the excellent characteristics as described above, the double-row angular contact ball bearing of the present embodiment can be suitably used as a rolling bearing that rotatably supports a rotary shaft of a pump such as a submersible pump.

水中ポンプ等の産業機械ポンプには、主に省スペース（コンパクト性）、メンテナンス費削減が強く要求されている。このためポンプメーカーは、ポンプの大容量化（送液量向上）、小型軽量化、高効率化、及び高信頼性化を目指している。特に、水中ポンプのように容易にメンテナンスできない用途には、給脂を必要としない転がり軸受が要求されている。   Industrial machine pumps such as submersible pumps are strongly required mainly to save space (compactness) and reduce maintenance costs. For this reason, pump manufacturers are aiming to increase the capacity of pumps (improving the amount of liquid delivered), to reduce the size and weight, to improve efficiency, and to improve reliability. In particular, rolling bearings that do not require lubrication are required for applications that cannot be easily maintained, such as submersible pumps.

本実施形態の複列アンギュラ玉軸受は、前述したように高負荷容量で長寿命であるため、産業機械ポンプに好適に使用可能である。特に水中ポンプは、モーターの回転軸を鉛直にした状態で使用するので、本実施形態の複列アンギュラ玉軸受は、該回転軸を回転自在に支持する軸受として好適に使用可能である。また、本実施形態の複列アンギュラ玉軸受は、前述したように密封性に優れているため、軸受の外部から内部への異物，塵埃の侵入や、内部から外部への潤滑剤の漏洩が生じにくい。よって、給脂等のメンテナンスをほとんど必要としないので、この点からも水中ポンプ等の産業機械ポンプに好適に使用可能である。   Since the double-row angular contact ball bearing of this embodiment has a high load capacity and a long life as described above, it can be suitably used for an industrial machine pump. In particular, since the submersible pump is used in a state where the rotation shaft of the motor is vertical, the double-row angular contact ball bearing of the present embodiment can be suitably used as a bearing that rotatably supports the rotation shaft. In addition, since the double row angular contact ball bearing of this embodiment has excellent sealing performance as described above, foreign matter and dust intrude from the outside to the inside of the bearing and leakage of lubricant from the inside to the outside occurs. Hateful. Therefore, since almost no maintenance such as lubrication is required, it can be suitably used for industrial machine pumps such as submersible pumps.

なお、本実施形態は本考案の一例を示したものであって、本考案は本実施形態に限定されるものではない。例えば、本実施形態においては、全体が金属で構成された密封装置５の例をあげて説明したが、外輪２に取り付けられる径方向外端部５ａが略板状をなし且つ金属材料製であればよく、径方向内端部５ｂ等の他の部位については、略板状以外の形状でもよいし、ゴム，プラスチック等の高分子材料で構成されていてもよい。   In addition, this embodiment shows an example of this invention and this invention is not limited to this embodiment. For example, in the present embodiment, the example of the sealing device 5 made entirely of metal has been described, but the radially outer end 5a attached to the outer ring 2 may be substantially plate-shaped and made of a metal material. The other portions such as the radially inner end portion 5b may have a shape other than a substantially plate shape, or may be made of a polymer material such as rubber or plastic.

また、本実施形態においては、転がり軸受が複列アンギュラ玉軸受である例をあげて説明したが、本考案は、複列アンギュラ玉軸受以外の種類の転がり軸受、例えば単列アンギュラ玉軸受にも適用可能であるし、深溝玉軸受，自動調心玉軸受，円筒ころ軸受，円すいころ軸受，針状ころ軸受，自動調心ころ軸受等にも適用可能である。
次に、実施例を示して、本考案をさらに具体的に説明する。外輪の内周面の軸方向両端部に形成された溝に、鋼板製のシールドの径方向外端部を嵌入し加締めることにより、外輪にシールドを取り付けて、図１，２の複列アンギュラ玉軸受とほぼ同様の構成の複列アンギュラ玉軸受を製造した。シールドの径方向外端部は、前述のような断面略Ｕ字状とされている。 In the present embodiment, the example in which the rolling bearing is a double-row angular contact ball bearing has been described. However, the present invention can be applied to other types of rolling bearings, such as a single-row angular contact ball bearing. It can be applied to deep groove ball bearings, self-aligning ball bearings, cylindrical roller bearings, tapered roller bearings, needle roller bearings, and self-aligning roller bearings.
Next, the present invention will be described more specifically with reference to examples. The double-row angular contact shown in FIGS. 1 and 2 is attached to the outer ring by inserting the radial outer ends of the steel plate shields into the grooves formed at both axial ends of the inner peripheral surface of the outer ring and crimping. A double-row angular contact ball bearing having the same configuration as the ball bearing was manufactured. The radially outer end of the shield has a substantially U-shaped cross section as described above.

実施例の複列アンギュラ玉軸受は、シールドの厚さＴｓが０．２３ｍｍであり、溝の底部における外輪の厚さＴｒが４ｍｍであって、両厚さの比Ｔｓ／Ｔｒが０．０５８である。一方、比較例の複列アンギュラ玉軸受は、シールドの厚さＴｓが０．３ｍｍであり、溝の底部における外輪の厚さＴｒが３．３ｍｍであって、両厚さの比Ｔｓ／Ｔｒが０．０９である。また、２つの参考例の複列アンギュラ玉軸受は、実施例，比較例それぞれに対してシールドが取り付けられていないものである。   In the double-row angular contact ball bearing of the example, the shield thickness Ts is 0.23 mm, the outer ring thickness Tr at the bottom of the groove is 4 mm, and the ratio Ts / Tr of both thicknesses is 0.058. is there. On the other hand, the double row angular contact ball bearing of the comparative example has a shield thickness Ts of 0.3 mm, an outer ring thickness Tr at the bottom of the groove of 3.3 mm, and a ratio Ts / Tr of both thicknesses. 0.09. Further, the double-row angular contact ball bearings of the two reference examples are those in which no shield is attached to each of the example and the comparative example.

これら４つの複列アンギュラ玉軸受の外輪の外径面の真円度を測定した。実施例の真円度の測定結果を図３に、比較例の真円度の測定結果を図４に、参考例の真円度の測定結果を図５に示す。２つの参考例の真円度はほぼ同一であるため、一方のみを代表して図５に示す。
参考例の真円度を１とした場合の相対値で示すと、実施例の真円度は１．８で、比較例の真円度は５．３であった。これらの結果から、シールドを取り付けた状態の実施例と比較例では、実施例の複列アンギュラ玉軸受の方が、比較例の複列アンギュラ玉軸受よりも、外輪の外径面の真円度が大幅に良好であることが分かる。 The roundness of the outer diameter surface of the outer ring of these four double-row angular contact ball bearings was measured. FIG. 3 shows the measurement result of the roundness of the example, FIG. 4 shows the measurement result of the roundness of the comparative example, and FIG. 5 shows the measurement result of the roundness of the reference example. Since the roundness of the two reference examples is almost the same, only one of them is shown in FIG.
When shown by relative values when the roundness of the reference example is 1, the roundness of the example was 1.8 and the roundness of the comparative example was 5.3. From these results, in the example and the comparative example with the shield attached, the roundness of the outer surface of the outer ring is larger in the double row angular contact ball bearing of the example than in the double row angular contact ball bearing of the comparative example. Can be seen to be significantly better.

１ 内輪
１ａ 軌道面
２ 外輪
２ａ 軌道面
２ｂ 溝
３ 玉（転動体）
３ａ 転動面
４ 保持器
５ 密封装置
５ａ 径方向外端部
５ｂ 径方向内端部
Ｔｓ 密封装置を構成する略円板状部材の厚さ
Ｔｒ 溝の底部における外輪の厚さ
Ｔｃ 断面略Ｕ字状の径方向外端部の軸方向幅 Reference Signs List 1 inner ring 1a raceway surface 2 outer ring 2a raceway surface 2b groove 3 ball (rolling element)
3a Rolling surface 4 Cage 5 Sealing device 5a Radial outer end 5b Radial inner end Ts Thickness of substantially disk-shaped member constituting sealing device Tr Thickness of outer ring at bottom of groove Tc Cross section substantially U-shaped Axial width of the outer radial end

Claims (6)

内輪と、外輪と、前記内輪の２列の軌道面と前記外輪の２列の軌道面との間に転動自在に配された２列の転動体と、前記外輪に取り付けられ前記内輪に滑り接触又は隙間を空けて対向する略円板状の密封装置と、前記内輪と前記外輪との間に前記転動体を保持する保持器と、を備え、前記転動体の直径が軸受幅の半分の７５％以上８３％以下である産業機械ポンプ用の複列アンギュラ玉軸受であって、
前記密封装置の径方向一端部が、最端部を径方向反対側に折り返すことにより形成されて、前記外輪に設けられた凹部に加締めにより取り付けられており、
前記密封装置の厚さＴｓと、前記外輪の外径面と前記凹部の底部との間の径方向距離Ｔｒとの比Ｔｓ／Ｔｒが、０．０７以下であり、
前記外輪の外径面と内周面との間の径方向距離は、前記軌道面の軸方向外側に形成される外側肩部よりも２列の前記軌道面の間に形成される内側肩部の方が大きくなっていることを特徴とする複列アンギュラ玉軸受。 An inner ring, an outer ring, two rows of rolling elements arranged in a freely rotatable manner between the two rows of raceway surfaces of the inner ring and the two rows of raceways of the outer ring, and slips on the inner ring attached to the outer race A substantially disc-shaped sealing device that is opposed to each other with a contact or a gap, and a cage that holds the rolling element between the inner ring and the outer ring, and the diameter of the rolling element is half the bearing width. It is a double row angular contact ball bearing for industrial machine pumps that is 75% or more and 83% or less,
One end in the radial direction of the sealing device is formed by folding the outermost end to the opposite side in the radial direction, and is attached by crimping to a recess provided in the outer ring,
The ratio Ts / Tr of the thickness Ts of the sealing device and the radial distance Tr between the outer diameter surface of the outer ring and the bottom of the recess is 0.07 or less,
The radial distance between the outer diameter surface and the inner peripheral surface of the outer ring is such that the inner shoulder portion formed between the two raceway surfaces rather than the outer shoulder portion formed on the outer side in the axial direction of the raceway surface. Double-row angular contact ball bearings characterized in that is larger. 前記密封装置は、金属材料製であるとともに、前記径方向一端部と、径方向に沿って配され前記内輪の外周面と前記外輪の内周面との間の開口を覆う平板部と、前記径方向一端部と前記平板部とを連結する連結部と、を有し、前記平板部と前記連結部の接続部分は軸方向外側に向かって凸をなす屈曲部となっており、該屈曲部が前記保持器の外径部よりも径方向外方に配されていることを特徴とする請求項１に記載の複列アンギュラ玉軸受。   The sealing device is made of a metal material, the radial end, a flat plate portion arranged along the radial direction and covering an opening between the outer peripheral surface of the inner ring and the inner peripheral surface of the outer ring, A connecting portion that connects the one end portion in the radial direction and the flat plate portion, and the connecting portion of the flat plate portion and the connecting portion is a bent portion that protrudes outward in the axial direction. The double row angular contact ball bearing according to claim 1, wherein is arranged radially outward from the outer diameter portion of the cage. 前記保持器が金属材料製の冠形保持器であることを特徴とする請求項１又は請求項２に記載の複列アンギュラ玉軸受。   The double-row angular contact ball bearing according to claim 1 or 2, wherein the cage is a crown-shaped cage made of a metal material. 前記密封装置の径方向一端部の軸方向幅が２．７ｍｍ以下であることを特徴とする請求項１〜３のいずれか一項に記載の複列アンギュラ玉軸受。   The double-row angular contact ball bearing according to any one of claims 1 to 3, wherein an axial width of one end portion in a radial direction of the sealing device is 2.7 mm or less. 前記転動体の直径が軸受幅の半分の８０％以上８３％以下であることを特徴とする請求項１〜４のいずれか一項に記載の複列アンギュラ玉軸受。   The double row angular contact ball bearing according to any one of claims 1 to 4, wherein a diameter of the rolling element is 80% or more and 83% or less of a half of a bearing width. 前記外輪の外径が５０ｍｍ以上１４０ｍｍ以下であることを特徴とする請求項１〜５のいずれか一項に記載の複列アンギュラ玉軸受。   The double-row angular contact ball bearing according to any one of claims 1 to 5, wherein an outer diameter of the outer ring is 50 mm or more and 140 mm or less.
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