JP2005299702A - Automatic aligning roller bearing - Google Patents

Automatic aligning roller bearing Download PDF

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JP2005299702A
JP2005299702A JP2004112366A JP2004112366A JP2005299702A JP 2005299702 A JP2005299702 A JP 2005299702A JP 2004112366 A JP2004112366 A JP 2004112366A JP 2004112366 A JP2004112366 A JP 2004112366A JP 2005299702 A JP2005299702 A JP 2005299702A
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inner ring
spherical roller
spherical
raceway surface
roller
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Fukuji Yoshikawa
福二 吉川
Mikiaki Betsumiya
幹朗 別宮
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NSK Ltd
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NSK Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C23/00—Bearings for exclusively rotary movement adjustable for aligning or positioning
    • F16C23/06—Ball or roller bearings
    • F16C23/08—Ball or roller bearings self-adjusting
    • F16C23/088—Ball or roller bearings self-adjusting by means of crowning
    • 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
    • F16C33/34—Rollers; Needles
    • F16C33/36—Rollers; Needles with bearing-surfaces other than cylindrical, e.g. tapered; with grooves in the bearing surfaces
    • 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
    • F16C33/58—Raceways; Race rings
    • F16C33/583—Details of specific parts of races
    • F16C33/585—Details of specific parts of races of raceways, e.g. ribs to guide 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
    • 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
    • F16C19/34—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 for both radial and axial load
    • F16C19/38—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 for both radial and axial load with two or more rows of 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
    • F16C23/00—Bearings for exclusively rotary movement adjustable for aligning or positioning
    • F16C23/06—Ball or roller bearings
    • F16C23/08—Ball or roller bearings self-adjusting
    • F16C23/082—Ball or roller bearings self-adjusting by means of at least one substantially spherical surface
    • F16C23/086—Ball or roller bearings self-adjusting by means of at least one substantially spherical surface forming a track for rolling elements

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Support Of The Bearing (AREA)
  • Rolling Contact Bearings (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To prolong service life of an automatic aligning roller bearing by suppressing edge load and reducing bearing pressure in a central part of a spherical roller. <P>SOLUTION: A bus line of a raceway surface of an inner ring 2 has a hanging-down shape part 10 on an inner ring side for letting stress escape in which radius of curvature is smoothly and continuously changed in a section where it opposes to a head part side of the spherical roller 3 or an edge part 3a on an end part side. That is, in the hanging-down shape part 10 on the inner ring side, center of radius of curvature is set to an opposite side to center of radius of curvature of the raceway surface of the inner ring 2, and the radius of curvature is smoothly and continuously changed. Consequently, the hanging-down shape part 10 on the inner ring side can leave the head part side of the spherical roller 3 or the edge part 3a on the end part side gradually. Accordingly, contact excessive stress of the raceway surface 6 and the edge part 3a generated when heavy load condition is applied escapes effectively to prevent edge load. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

本発明は、各種機械装置に組み込み、重量が比較的嵩む回転軸を支承する自動調心ころ軸受に関する。   The present invention relates to a self-aligning roller bearing that is incorporated in various mechanical devices and supports a rotating shaft that is relatively heavy.

図１２は、従来に係る自動調心ころ軸受の断面図である。   FIG. 12 is a cross-sectional view of a conventional self-aligning roller bearing.

図１３（ａ）は、従来に係るころの拡大図であり、（ｂ）は、従来に係る内輪の拡大断面図である。   FIG. 13A is an enlarged view of a conventional roller, and FIG. 13B is an enlarged cross-sectional view of a conventional inner ring.

自動調心ころ軸受は、図１２に示すように、外輪１と、内輪２と、これら外内輪間に配置した２列の球面ころ３，３と、球面ころ３，３を保持する保持器４，４と、から構成してある。   As shown in FIG. 12, the self-aligning roller bearing includes an outer ring 1, an inner ring 2, two rows of spherical rollers 3 and 3 disposed between the outer and inner rings, and a cage 4 that holds the spherical rollers 3 and 3. , 4.

外輪１は、内周に単一円弧状の軌道面５を有している。また、内輪２は、その内周で、回転軸（図示略）に固定してあり、その外周には、外輪１の軌道面５に対向する２つの円弧状軌道面６，６が、軸方向中央部に所定間隔をおいて、形成してある。   The outer ring 1 has a single arc-shaped raceway surface 5 on the inner periphery. The inner ring 2 is fixed to a rotating shaft (not shown) at the inner periphery thereof, and two arcuate track surfaces 6 and 6 facing the track surface 5 of the outer ring 1 are axially disposed on the outer periphery thereof. A central portion is formed with a predetermined interval.

外輪１の軌道面５と、内輪２の軌道面６，６との間とには、それぞれ、２列の球面ころ３，３が介装してある。これら２列の球面ころ３，３は、それぞれ、保持器４，４により保持してある。
特公平３−５２７号公報 特開平９−７２３４２号公報 Two rows of spherical rollers 3, 3 are interposed between the raceway surface 5 of the outer ring 1 and the raceway surfaces 6, 6 of the inner ring 2, respectively. These two rows of spherical rollers 3 and 3 are held by cages 4 and 4, respectively.
Japanese Patent Publication No. 3-527 Japanese Patent Laid-Open No. 9-72342

ところで、自動調心ころ軸受において、従来、重荷重条件になると、内輪の軌道面６ところエッジ部３ａの接触応力が過大になってしまい、早期に損傷してしまうことがある。   By the way, in a self-aligning roller bearing, conventionally, under heavy load conditions, the contact stress of the edge 3a on the raceway surface 6 of the inner ring becomes excessive and may be damaged early.

すなわち、従来の自動調心ころ軸受は、重荷重が加わる場合、内輪２および外輪１の軌道面５，６のアール寸法に対して、球面ころ３の胴部アール寸法を小さくして、エッジロードを緩和している。   That is, the conventional self-aligning roller bearing has an edge load which is smaller than the radius of the raceway surfaces 5 and 6 of the inner ring 2 and the outer ring 1 when the heavy load is applied. Has eased.

軌道面５，６のアール寸法と、球面ころ３の胴部アール寸法との差が大きくなると、球面ころ３の中央部の面圧が高くなり、その部分での寿命が低下する。   When the difference between the radius dimension of the raceway surfaces 5 and 6 and the barrel radius dimension of the spherical roller 3 is increased, the surface pressure at the central portion of the spherical roller 3 is increased, and the life at that portion is decreased.

従って、エッジロード部の面圧と、球面ころ３の中央部の面圧とのバランスが、最も長寿命になる軌道面５，６のアール寸法と、球面ころ３の胴部アール寸法とを選定している。   Accordingly, the radius dimension of the raceway surfaces 5 and 6 and the barrel radius dimension of the spherical roller 3 are selected so that the balance between the surface pressure of the edge load portion and the surface pressure of the central portion of the spherical roller 3 is the longest. doing.

しかし、重荷重になればなる程、軌道面５，６のアール寸法と、球面ころ３の胴部アール寸法との差を大きくしなければならないため、軸受寿命の長寿命化は、望めないといったことがある。   However, as the load becomes heavier, the difference between the radius dimension of the raceway surfaces 5 and 6 and the barrel radius dimension of the spherical roller 3 must be increased. Sometimes.

本発明は、上述したような事情に鑑みてなされたものであって、エッジロードを抑制すると共に、球面ころ中央部の面圧をも低減して、長寿命化を図ることができる自動調心ころ軸受を提供することを目的とする。   The present invention has been made in view of the circumstances as described above, and is an automatic alignment capable of suppressing the edge load and reducing the surface pressure of the central portion of the spherical roller to extend the life. It aims at providing a roller bearing.

上記の目的を達成するため、本発明の請求項１に係る自動調心ころ軸受は、内周に円弧状の軌道を有する外輪と、
外周に外輪の軌道面に対向して配置した軌道面を有する内輪と、
外輪の軌道面と内輪の軌道面との間に介装した複数列の球面ころと、
これら複数列の球面ころを保持する保持器と、からなる、自動調心ころ軸受において、
前記内輪の軌道面の母線は、球面ころの頭部側又は端部側に対向する部位で、その曲率半径をなめらかに連続的に変化した内輪側ダラシ形状部を有することを特徴とする。 In order to achieve the above object, a self-aligning roller bearing according to claim 1 of the present invention includes an outer ring having an arcuate raceway on the inner periphery,
An inner ring having a raceway surface disposed on the outer periphery facing the raceway surface of the outer ring;
A plurality of rows of spherical rollers interposed between the raceway surface of the outer ring and the raceway surface of the inner ring,
In a self-aligning roller bearing composed of a cage for holding these multiple rows of spherical rollers,
The generatrix of the raceway surface of the inner ring has an inner ring side dull shape part in which the radius of curvature smoothly changes continuously at a portion facing the head side or end side of the spherical roller.

本発明の請求項２に係る自動調心ころ軸受は、前記球面ころの軌道面の母線は、球面ころの頭部側又は端部側のエッジ部に、その曲率半径をなめらかに連続的に変化した球面ころ側ダラシ形状部を有することを特徴とする。   In a self-aligning roller bearing according to a second aspect of the present invention, the generatrix of the raceway surface of the spherical roller smoothly and continuously changes its curvature radius at the head portion side or end portion side portion of the spherical roller. It has a spherical roller side drip-shaped portion.

本発明の請求項３に係る自動調心ころ軸受は、前記内輪側ダラシ形状部及び前記球面ころ側ダラシ形状部以外の箇所に於いて、前記外輪又は内輪の軌道面アール寸法（Ｒ１）に対する、球面ころの転動面アール寸法（Ｒ２）の比率は、Ｒ２／Ｒ１＞０．９５であることを特徴とする。   The self-aligning roller bearing according to claim 3 of the present invention is provided for the outer ring or inner ring raceway radius (R1) at a place other than the inner ring side dull shape part and the spherical roller side dull shape part. The ratio of the rolling surface radius dimension (R2) of the spherical roller is R2 / R1> 0.95.

本発明の請求項４に係る自動調心ころ軸受は、前記外輪、前記内輪、及び前記球面ころの少なくとも１つは、主として、Ｃ；０．３〜０．７重量％、及びＣｒ；１〜３重量％を含有する合金鋼、またはＪＩＳの高炭素クロム軸受鋼からなり、しかも、浸炭処理を施すことにより、表面層の残留オーステナイト量（γＲ）を、２０〜５０ｖｏｌ%とした軸受部材を用いたことを特徴とする。 In a self-aligning roller bearing according to a fourth aspect of the present invention, at least one of the outer ring, the inner ring, and the spherical roller is mainly C; 0.3 to 0.7% by weight, and Cr; A bearing member made of alloy steel containing 3% by weight or JIS high carbon chrome bearing steel and having a surface layer retained austenite (γ R ) of 20 to 50 vol% by carburizing treatment. It is used.

本発明の請求項５に係る自動調心ころ軸受は、前記内輪側ダラシ形状部、又は前記球面ころ側ダラシ形状部は、超仕上加工、又は、ロータリードレス加工により形成してあることを特徴とする。   The self-aligning roller bearing according to claim 5 of the present invention is characterized in that the inner ring side dull shape portion or the spherical roller side dashi shape portion is formed by super finishing or rotary dressing. To do.

以上説明したように、本発明によれば、内輪の軌道面の母線は、球面ころの頭部側又は端部側に対向する部位で、その曲率半径をなめらかに連続的に変化した内輪側ダラシ形状部を有しており、又は、球面ころの軌道面の母線は、球面ころの頭部側又は端部側に、その曲率半径をなめらかに連続的に変化した球面ころ側ダラシ形状部を有していることから、重荷重条件で発生するエッジロードを抑制すると共に、球面ころ中央部の面圧をも低減して、自動調心ころ軸受の長寿命化を図ることができる。   As described above, according to the present invention, the generatrix of the inner ring raceway surface is the portion facing the head side or the end side of the spherical roller, and the inner ring side dullness in which the curvature radius smoothly changes continuously. The generous part of the spherical roller raceway surface has a spherical roller side dull shape part whose radius of curvature changes smoothly and continuously on the head side or end side of the spherical roller. Therefore, it is possible to extend the life of the self-aligning roller bearing by suppressing the edge load that occurs under heavy load conditions and reducing the surface pressure at the center of the spherical roller.

以下、本発明の実施の形態に係る自動調心ころ軸受を図面を参照しつつ説明する。   Hereinafter, a self-aligning roller bearing according to an embodiment of the present invention will be described with reference to the drawings.

（第１実施の形態）
図１は、本発明の第１実施の形態に係る自動調心ころ軸受の断面図である。 (First embodiment)
FIG. 1 is a sectional view of a self-aligning roller bearing according to a first embodiment of the present invention.

図２（ａ）は、本発明の第１実施の形態に係るころの拡大図であり、（ｂ）は、本発明の第１実施の形態に係る内輪の拡大断面図である。   FIG. 2A is an enlarged view of the roller according to the first embodiment of the present invention, and FIG. 2B is an enlarged cross-sectional view of the inner ring according to the first embodiment of the present invention.

図３（ａ）は、内輪の球面ころ頭部側の拡大断面図であり、（ｂ）は、内輪の球面ころ端部側の拡大断面図である。   FIG. 3A is an enlarged cross-sectional view of the inner ring on the spherical roller head side, and FIG. 3B is an enlarged cross-sectional view of the inner ring on the spherical roller end portion side.

自動調心ころ軸受は、図１に示すように、外輪１と、内輪２と、これら外内輪間に配置した２列の球面ころ３，３と、球面ころ３，３を保持する保持器４，４と、から構成してある。   As shown in FIG. 1, the self-aligning roller bearing includes an outer ring 1, an inner ring 2, two rows of spherical rollers 3 and 3 disposed between the outer and inner rings, and a cage 4 that holds the spherical rollers 3 and 3. , 4.

外輪１は、内周に単一円弧状の軌道面５を有している。また、内輪２は、その内周で、回転軸（図示略）に固定してあり、その外周には、外輪１の軌道面５に対向する２つの円弧状軌道面６，６が、軸方向中央部に所定間隔をおいて、形成してある。   The outer ring 1 has a single arc-shaped raceway surface 5 on the inner periphery. The inner ring 2 is fixed to a rotating shaft (not shown) at the inner periphery thereof, and two arcuate track surfaces 6 and 6 facing the track surface 5 of the outer ring 1 are axially disposed on the outer periphery thereof. A central portion is formed with a predetermined interval.

外輪１の軌道面５と、内輪２の軌道面６，６との間とには、それぞれ、２列の球面ころ３，３が介装してある。これら２列の球面ころ３，３は、それぞれ、保持器４，４により保持してある。   Two rows of spherical rollers 3, 3 are interposed between the raceway surface 5 of the outer ring 1 and the raceway surfaces 6, 6 of the inner ring 2, respectively. These two rows of spherical rollers 3 and 3 are held by cages 4 and 4, respectively.

本実施の形態では、内輪２の軌道面の母線は、球面ころ３の頭部側又は端部側のエッジ部３ａに対向する部位で、その曲率半径をなめらかに連続的に変化した応力逃がし用の内輪側ダラシ形状部１０を有している。   In the present embodiment, the generatrix of the raceway surface of the inner ring 2 is a part that faces the edge part 3a on the head side or the end part side of the spherical roller 3, and for the stress relief whose curvature radius has changed smoothly and continuously. The inner ring side drip-shaped portion 10 is provided.

すなわち、図３（ａ）（ｂ）に示すように、内輪側ダラシ形状部１０は、その曲率半径の中心が内輪２の軌道面の曲率半径の中心とは反対側に設定してあり、その曲率半径をなめらかに連続的に変化させている。   That is, as shown in FIGS. 3 (a) and 3 (b), the inner ring side dull shape portion 10 has its center of curvature radius set opposite to the center of curvature radius of the raceway surface of the inner ring 2, The radius of curvature is changed smoothly and continuously.

これにより、内輪側ダラシ形状部１０は、球面ころ３の頭部側又は端部側のエッジ部３ａから徐々に離間できるようになっている。従って、重荷重条件時に発生する軌道面６とエッジ部３ａとの接触過大応力を効果的に逃がして、エッジロードを防止することができ、自動調心ころ軸受の長寿命化を図ることができる。   Thereby, the inner ring side drip-shaped portion 10 can be gradually separated from the edge portion 3 a on the head side or end side of the spherical roller 3. Accordingly, excessive contact stress between the raceway surface 6 and the edge portion 3a generated under heavy load conditions can be effectively released to prevent edge loading, and the life of the self-aligning roller bearing can be extended. .

図１１（ａ）は、従来に係る内輪と球面ころとの面圧分布を示すグラフであり、（ｂ）は、本発明に係る内輪と球面ころとの面圧分布を示すグラフである。   FIG. 11A is a graph showing the surface pressure distribution between the inner ring and the spherical roller according to the prior art, and FIG. 11B is a graph showing the surface pressure distribution between the inner ring and the spherical roller according to the present invention.

図１１（ａ）（ｂ）を比較すれば明らかなように、本実施の形態では、軌道面６とエッジ部３ａとの接触過大応力を効果的に逃がして、エッジロードを著しく低減することができる。   As is clear from comparison between FIGS. 11A and 11B, in this embodiment, excessive contact stress between the raceway surface 6 and the edge portion 3a can be effectively released, and the edge load can be significantly reduced. it can.

図４（ａ）（ｂ）は、夫々、内輪側ダラシ形状部の超仕上加工の加工工程を示す模式図である。   4 (a) and 4 (b) are schematic views showing processing steps for super finishing of the inner ring side drip-shaped portion, respectively.

本実施の形態では、内輪側ダラシ形状部１０は、超仕上加工（スーパーフィニッシュ加工）により形成してある。即ち、図４（ａ）に示すように、鼓形状の超仕上砥石１１の両端部を、頭部側と端部側の内輪側ダラシ形状部１０に当接して押圧しながら、図４（ｂ）に示すように、超仕上砥石１１を往復動させて、内輪側ダラシ形状部１０を形成している。これにより、製造コストを低減しながら、簡易な工程により、内輪側ダラシ形状部１０を形成することができる。   In the present embodiment, the inner ring side drip-shaped portion 10 is formed by super finishing (super finish processing). That is, as shown in FIG. 4 (a), the both ends of the drum-shaped super finishing grindstone 11 are pressed against the head side and the inner ring side drip-shaped portion 10 on the side of the head while being pressed. As shown in FIG. 3, the super finishing grindstone 11 is reciprocated to form the inner ring side drip-shaped portion 10. Thereby, the inner ring side drip-shaped portion 10 can be formed by a simple process while reducing the manufacturing cost.

図５（ａ）（ｂ）は、夫々、内輪側ダラシ形状部のロータリードレス加工の加工工程を示す模式図である。   5 (a) and 5 (b) are schematic diagrams showing the processing steps of the rotary dress processing of the inner ring side drip-shaped portion, respectively.

本実施の形態では、内輪側ダラシ形状部１０は、ロータリードレス加工により形成してある。即ち、図５（ａ）に示すように、ドレス１２と砥石１３とを、頭部側と端部側の内輪側ダラシ形状部１０に当接して押圧しながら、図５（ｂ）に示すように、砥石１３を回転させて、内輪側ダラシ形状部１０を形成している。これにより、製造コストを低減しながら、簡易な工程により、内輪側ダラシ形状部１０を形成することができる。   In the present embodiment, the inner ring side drip-shaped portion 10 is formed by rotary dressing. That is, as shown in FIG. 5A, as shown in FIG. 5B, the dress 12 and the grindstone 13 are in contact with and pressed against the head-side and end-side inner ring side portion 10. Further, the inner ring side drip-shaped portion 10 is formed by rotating the grindstone 13. Thereby, the inner ring side drip-shaped portion 10 can be formed by a simple process while reducing the manufacturing cost.

また、ロータリードレス加工は、内輪２の軌道面６を加工する場合のみに用いるものであるが、ドレス１２の端を少しだらすだけで、図５（ｂ）に示すように、頭部側と端部側の内輪側ダラシ形状部１０と、軌道面６とを同時に加工することが出来る。   In addition, the rotary dressing is used only when the raceway surface 6 of the inner ring 2 is machined. However, as shown in FIG. The inner ring side drip-shaped portion 10 on the end side and the raceway surface 6 can be processed simultaneously.

さらに、自動調心ころ軸受の球面ころ３と内輪３は、ロータリードレスで加工する例が多いので、頭部側と端部側の内輪側ダラシ形状部１０と軌道面６とを同時加工できることにより、より効率的に加工が出来る。   Further, since the spherical roller 3 and the inner ring 3 of the self-aligning roller bearing are often processed by a rotary dress, the inner ring side drip-shaped portion 10 and the raceway surface 6 on the head side and the end side can be processed simultaneously. Can be processed more efficiently.

（第２実施の形態）
図６は、本発明の第２実施の形態に係る自動調心ころ軸受の断面図である。 (Second Embodiment)
FIG. 6 is a sectional view of a self-aligning roller bearing according to a second embodiment of the present invention.

図７（ａ）は、本発明の第２実施の形態に係るころの拡大図であり、（ｂ）は、本発明の第２実施の形態に係る内輪の拡大断面図である。   Fig.7 (a) is an enlarged view of the roller which concerns on 2nd Embodiment of this invention, (b) is an expanded sectional view of the inner ring | wheel which concerns on 2nd Embodiment of this invention.

図８（ａ）は、内輪の球面ころ頭部側の拡大断面図であり、（ｂ）は、内輪の球面ころ端部側の拡大断面図である。   FIG. 8A is an enlarged sectional view of the inner ring on the spherical roller head side, and FIG. 8B is an enlarged sectional view of the inner ring on the spherical roller end side.

本実施の形態は、その基本的構造が上記第１実施の形態と同様であり、その相違する点についてのみ説明する。   The basic structure of this embodiment is the same as that of the first embodiment, and only the differences will be described.

本実施の形態では、球面ころ３の軌道面の母線は、頭部側又は端部側のエッジ部３ａに、その曲率半径をなめらかに連続的に変化した応力逃がし用の球面ころ側ダラシ形状部２０を有している。   In the present embodiment, the generatrix of the raceway surface of the spherical roller 3 is a stress relief spherical roller side dull shape portion whose curvature radius changes smoothly and continuously at the edge portion 3a on the head side or the end portion side. 20.

すなわち、図８（ａ）（ｂ）に示すように、球面ころ側ダラシ形状部２０は、その曲率半径が球面ころ３の転動面の曲率半径より小さくなるように設定してあり、その曲率半径をなめらかに連続的に変化させている。   That is, as shown in FIGS. 8A and 8B, the spherical roller side dull shape portion 20 is set so that the radius of curvature thereof is smaller than the radius of curvature of the rolling surface of the spherical roller 3, and the curvature thereof. The radius is changed smoothly and continuously.

これにより、球面ころ側ダラシ形状部２０は、内輪２の軌道面６から徐々に離間できるようになっている。従って、重荷重条件時に発生する軌道面６とエッジ部３ａとの接触過大応力を効果的に逃がして、エッジロードを防止することができ、自動調心ころ軸受の長寿命化を図ることができる。   Thereby, the spherical roller side drip-shaped portion 20 can be gradually separated from the raceway surface 6 of the inner ring 2. Accordingly, excessive contact stress between the raceway surface 6 and the edge portion 3a generated under heavy load conditions can be effectively released to prevent edge loading, and the life of the self-aligning roller bearing can be extended. .

図１１（ａ）は、従来に係る内輪と球面ころとの面圧分布を示すグラフであり、（ｂ）は、本発明に係る内輪と球面ころとの面圧分布を示すグラフである。   FIG. 11A is a graph showing the surface pressure distribution between the inner ring and the spherical roller according to the prior art, and FIG. 11B is a graph showing the surface pressure distribution between the inner ring and the spherical roller according to the present invention.

図１１（ａ）（ｂ）を比較すれば明らかなように、本実施の形態では、軌道面６とエッジ部３ａとの接触過大応力を効果的に逃がして、エッジロードを著しく低減することができる。   As is clear from comparison between FIGS. 11A and 11B, in this embodiment, excessive contact stress between the raceway surface 6 and the edge portion 3a can be effectively released, and the edge load can be significantly reduced. it can.

図９（ａ）（ｂ）は、夫々、球面ころ側ダラシ形状部の超仕上加工の加工工程を示す模式図である。   FIGS. 9A and 9B are schematic views showing the processing steps for super finishing of the spherical roller side dull shape portion, respectively.

本実施の形態では、球面ころ側ダラシ形状部２０は、超仕上加工（スーパーフィニッシュ加工）により形成してある。即ち、図９（ａ）に示すように、鼓形状の超仕上砥石２１の両端部を、頭部側と端部側の球面ころ側ダラシ形状部２０に当接して押圧しながら、図９（ｂ）に示すように、超仕上砥石２１を往復動させて、球面ころ側ダラシ形状部２０を形成している。これにより、製造コストを低減しながら、簡易な工程により、球面ころ側ダラシ形状部２０を形成することができる。   In the present embodiment, the spherical roller side drip-shaped portion 20 is formed by super finishing (super finish). That is, as shown in FIG. 9A, while both end portions of the drum-shaped superfinishing grindstone 21 are pressed against the spherical roller side dart shape portions 20 on the head side and the end side, As shown in b), the super-finishing grindstone 21 is reciprocated to form the spherical roller side drip-shaped portion 20. Thereby, the spherical roller side drip-shaped portion 20 can be formed by a simple process while reducing the manufacturing cost.

図１０（ａ）（ｂ）は、夫々、球面ころ側ダラシ形状部のロータリードレス加工の加工工程を示す模式図である。   FIGS. 10A and 10B are schematic views showing the processing steps of the rotary dressing of the spherical roller side dull shape portion, respectively.

本実施の形態では、球面ころ側ダラシ形状部２０は、ロータリードレス加工により形成してある。即ち、図１０（ａ）に示すように、ドレス２２と砥石２３とを、頭部側と端部側の球面ころ側ダラシ形状部２０に当接して押圧しながら、図１０（ｂ）に示すように、砥石２３を回転させて、球面ころ側ダラシ形状部２０を形成している。これにより、製造コストを低減しながら、簡易な工程により、球面ころ側ダラシ形状部２０を形成することができる。   In the present embodiment, the spherical roller side drip-shaped portion 20 is formed by rotary dressing. That is, as shown in FIG. 10 (a), the dress 22 and the grindstone 23 are shown in FIG. 10 (b) while abutting and pressing the spherical roller side dull shape portion 20 on the head side and the end side. Thus, the grindstone 23 is rotated to form the spherical roller side drip-shaped portion 20. Thereby, the spherical roller side drip-shaped portion 20 can be formed by a simple process while reducing the manufacturing cost.

また、ロータリードレス加工は、ころ３の転道面２４を加工する場合のみに用いるものであるが、ドレス２２の端を少しだらすだけで、図１０（ｂ）に示すように、頭部側と端部側の球面ころ側ダラシ形状部２０と、球面ころ３の転動面とを同時に加工することが出来、より効率的に加工が出来る。   In addition, the rotary dressing is used only when the rolling surface 24 of the roller 3 is machined. However, as shown in FIG. And the spherical roller side drip-shaped portion 20 on the end side and the rolling surface of the spherical roller 3 can be processed at the same time, and the processing can be performed more efficiently.

（第３実施の形態）
図１４は、本発明の第３実施の形態に係る自動調心軸受の模式図であって、面圧分布を示すものである。 (Third embodiment)
FIG. 14 is a schematic diagram of a self-aligning bearing according to a third embodiment of the present invention, and shows a surface pressure distribution.

図１５（ａ）は、本発明の第３実施の形態に係る自動調心軸受の模式図であって、中央面圧が高い場合の面圧分布を示すものであり、（ｂ）は、本発明の第３実施の形態に係る自動調心軸受の模式図であって、エッジロードと中央面圧とを低くした場合の面圧分布を示すものである。   FIG. 15A is a schematic diagram of a self-aligning bearing according to a third embodiment of the present invention, and shows a surface pressure distribution when the center surface pressure is high, and FIG. It is a schematic diagram of the self-aligning bearing according to the third embodiment of the invention, and shows the surface pressure distribution when the edge load and the center surface pressure are lowered.

自動調心ころ軸受は、図１４に示すように、外輪１と、内輪２と、これら外内輪間に配置した２列の球面ころ３，３と、球面ころ３，３を保持する保持器（図示略）と、から構成してある。   As shown in FIG. 14, the self-aligning roller bearing includes an outer ring 1, an inner ring 2, two rows of spherical rollers 3 and 3 disposed between the outer and inner rings, and a cage (which holds the spherical rollers 3 and 3. (Not shown).

外輪１は、内周に単一円弧状の軌道面５を有している。また、内輪２は、その内周で、回転軸（図示略）に固定してあり、その外周には、外輪１の軌道面５に対向する２つの円弧状軌道面６，６が、軸方向中央部に所定間隔をおいて、形成してある。   The outer ring 1 has a single arc-shaped raceway surface 5 on the inner periphery. The inner ring 2 is fixed to a rotating shaft (not shown) at the inner periphery thereof, and two arcuate track surfaces 6 and 6 facing the track surface 5 of the outer ring 1 are axially disposed on the outer periphery thereof. A central portion is formed with a predetermined interval.

ところで、従来の自動調心ころ軸受は、重荷重が加わる場合、内輪２および外輪１の軌道面５，６のアール寸法に対して、球面ころ３の胴部アール寸法を小さくして、エッジロードを緩和している。   By the way, the conventional self-aligning roller bearing, when a heavy load is applied, reduces the body radius dimension of the spherical roller 3 relative to the radius dimensions of the raceway surfaces 5 and 6 of the inner ring 2 and the outer ring 1, thereby reducing the edge load. Has eased.

軌道面５，６のアール寸法と、球面ころ３の胴部アール寸法との差が大きくなると、球面ころ３の中央部の面圧が高くなり、その部分での寿命が低下する。   When the difference between the rounded dimension of the raceway surfaces 5 and 6 and the barrel rounded dimension of the spherical roller 3 is increased, the surface pressure at the central part of the spherical roller 3 is increased, and the life at that part is decreased.

従って、エッジロード部の面圧と、球面ころ３の中央部の面圧とのバランスが、最も長寿命になる軌道面５，６のアール寸法と、球面ころ３の胴部アール寸法とを選定している。   Accordingly, the radius dimension of the raceway surfaces 5 and 6 and the barrel radius dimension of the spherical roller 3 are selected so that the balance between the surface pressure of the edge load portion and the surface pressure of the central portion of the spherical roller 3 is the longest. doing.

しかし、重荷重になればなる程、軌道面５，６のアール寸法と、球面ころ３の胴部アール寸法との差を大きくしなければならないため、軸受寿命の長寿命化は、望めないといったことがある。   However, as the load becomes heavier, the difference between the radius dimension of the raceway surfaces 5 and 6 and the barrel radius dimension of the spherical roller 3 must be increased. Sometimes.

本実施の形態は、重荷重が加わって、球面ころ３のエッジ部にエッジロードが生じた時、使用初期の段階で、球面ころ３のエッジ部および外輪軌道面５（又は、内輪軌道面６）がエッジロードの高面圧によって、適度に塑性変形させることによって、エッジロードを緩和するように構成してある。   In the present embodiment, when a heavy load is applied and an edge load is generated at the edge portion of the spherical roller 3, the edge portion of the spherical roller 3 and the outer ring raceway surface 5 (or the inner ring raceway surface 6) at the initial stage of use. ) Is moderately plastically deformed by the high surface pressure of the edge load so as to relieve the edge load.

これにより、軌道面５，６のアール寸法と胴部アール寸法の差を大きくする必要がなくなり、球面ころ３の中央部の面圧を、従来軸受に比べて小さくすることが出来る。従って、軸受寿命を従来軸受より長くすることが可能となる。   Thereby, it is not necessary to increase the difference between the radius dimension of the raceway surfaces 5 and 6 and the barrel radius dimension, and the surface pressure of the central portion of the spherical roller 3 can be reduced as compared with the conventional bearing. Therefore, the bearing life can be made longer than that of the conventional bearing.

エッジロードの高面圧によって適度に塑性変形させる方法として、中炭素軸受用鋼（主として、Ｃ；０．３〜０．７重量％、及びＣｒ；１〜３重量％を含有する合金鋼）、またはＪＩＳの高炭素クロム軸受鋼を浸炭した後、焼入れ・焼き戻しした軸受部材を用いる。   As a method of appropriately plastically deforming by high surface pressure of edge load, steel for medium carbon bearings (mainly alloy steel containing C: 0.3 to 0.7 wt% and Cr: 1 to 3 wt%), Alternatively, a JIS high carbon chrome bearing steel is carburized and then quenched and tempered.

中炭素軸受用鋼または高炭素クロム軸受鋼を浸炭することにより、表面層における残留オーステナイト量（γＲ）を２０〜５０ｖｏｌ％にして、塑性変形しやすくする。又、残留オーステナイトは、塑性変形部から亀裂が発生したり、亀裂が進展することを抑制する効果がある。 By carburizing the medium carbon bearing steel or the high carbon chromium bearing steel, the amount of retained austenite (γ R ) in the surface layer is set to 20 to 50 vol% to facilitate plastic deformation. Residual austenite has an effect of suppressing the occurrence of cracks from the plastically deformed portion and the progress of the cracks.

従来の浸炭軸受でも、表面層における残留オーステナイト量を得られるが、中炭素軸受用鋼または高炭素クロム軸受鋼に比べ、低炭素の鋼材を用いるため、内部硬さが低い。そのため重荷重が加わる用途には適さない。   Even with a conventional carburized bearing, the amount of retained austenite in the surface layer can be obtained, but the internal hardness is low because a low carbon steel material is used as compared with a medium carbon bearing steel or a high carbon chromium bearing steel. Therefore, it is not suitable for applications where heavy loads are applied.

このように、本実施の形態では、球面ころ３に重荷重が加わった場合のエッジロードを小さくして、軸受寿命を従来より長くすることが出来る。   As described above, in the present embodiment, the edge load when a heavy load is applied to the spherical roller 3 can be reduced, and the bearing life can be extended as compared with the prior art.

図１４は、軌道輪の軌道面５，６のアール寸法（Ｒ１）に対する、球面ころ３の転動面アール寸法（Ｒ２）の比率が、Ｒ２／Ｒ１＞０．９５である自動調心ころ軸受に、基本静定格荷重の５０％以上の荷重が加わった場合の、外輪軌道面５と球面ころ３の胴部の接触面圧分布、および、内輪軌道面５と球面ころ３の胴部の接触面圧分布を示し、エッジロードが生じることを説明している。   FIG. 14 shows a spherical roller bearing in which the ratio of the rolling surface radius dimension (R2) of the spherical roller 3 to the radius dimension (R1) of the raceway surfaces 5 and 6 of the raceway is R2 / R1> 0.95. In addition, when a load of 50% or more of the basic static load rating is applied, the contact surface pressure distribution between the outer ring raceway surface 5 and the body portion of the spherical roller 3 and the contact between the inner ring raceway surface 5 and the body portion of the spherical roller 3 are contacted. The surface pressure distribution is shown, explaining that edge loading occurs.

図１５（ａ）は、エッジロードを下げるため、軌道面６のアール寸法（Ｒ１）に対して、転動面アール寸法（Ｒ２）を、図１５（ｂ）の（Ｒ３）寸法より小さくしている。そのため、球面ころ３の中央部の面圧が高くなり、軸受寿命が短い。   In FIG. 15A, in order to lower the edge load, the rolling surface radius dimension (R2) is made smaller than the dimension (R3) of FIG. 15B with respect to the radius dimension (R1) of the raceway surface 6. Yes. Therefore, the surface pressure at the center of the spherical roller 3 is increased, and the bearing life is short.

図１５（ｂ）は、図１４の状態で使用を開始し、球面ころ３のエッジ部および外輪軌道面５（又は、内輪軌道面６）がエッジロードの高面圧（図１４）になった後、使用初期の段階で高面圧のエッジロードによって適度に塑性変形することにより、エッジ部の形状がダレルことによって、エッジロードが緩和される（図１５（ｂ）)。   FIG. 15B starts use in the state of FIG. 14, and the edge portion of the spherical roller 3 and the outer ring raceway surface 5 (or the inner ring raceway surface 6) become a high surface pressure (FIG. 14) of the edge load. Thereafter, the edge load is alleviated due to the fact that the shape of the edge portion is a Darrell by appropriately plastically deforming with an edge load having a high surface pressure in the initial stage of use (FIG. 15B).

従って、図１５（ａ）の（Ｒ２）寸法より（Ｒ３）寸法を大きくすることが出来るので、球面ころ３の中央部の面圧を下げることが出来て、従来軸受より長寿命にすることが可能になる。   Accordingly, since the dimension (R3) can be made larger than the dimension (R2) in FIG. 15A, the surface pressure at the central portion of the spherical roller 3 can be lowered, and the service life can be made longer than that of the conventional bearing. It becomes possible.

また、特許文献２は、高炭素クロム軸受鋼を浸炭した軸受部材についての特許出願であるが、重荷重用にエッジロードを緩和させることを目的にしたものではない。本実施の形態は、重荷重の状態で高面圧のエッジロードを生じる状態と組合せたことを特徴としている。   Moreover, although patent document 2 is a patent application about the bearing member which carburized the high carbon chromium bearing steel, it is not aimed at relieving edge load for heavy loads. The present embodiment is characterized in that it is combined with a state in which a high surface pressure edge load is generated in a heavy load state.

なお、本発明は、上述した実施の形態に限定されず、種々変形可能である。   In addition, this invention is not limited to embodiment mentioned above, A various deformation | transformation is possible.

本発明の第１実施の形態に係る自動調心ころ軸受の断面図である。It is sectional drawing of the self-aligning roller bearing which concerns on 1st Embodiment of this invention. （ａ）は、本発明の第１実施の形態に係るころの拡大図であり、（ｂ）は、本発明の第１実施の形態に係る内輪の拡大断面図である。(A) is an enlarged view of the roller which concerns on 1st Embodiment of this invention, (b) is an expanded sectional view of the inner ring | wheel which concerns on 1st Embodiment of this invention. （ａ）は、内輪の球面ころ頭部側の拡大断面図であり、（ｂ）は、内輪の球面ころ端部側の拡大断面図である。(A) is an enlarged sectional view of the inner ring on the spherical roller head side, and (b) is an enlarged sectional view of the inner ring on the spherical roller end side. （ａ）（ｂ）は、夫々、内輪側ダラシ形状部の超仕上加工の加工工程を示す模式図である。(A) (b) is a schematic diagram which respectively shows the process of the super finishing of an inner ring | wheel side dashi shape part. （ａ）（ｂ）は、夫々、内輪側ダラシ形状部のロータリードレス加工の加工工程を示す模式図である。(A) (b) is a schematic diagram which shows the processing process of the rotary dressing of an inner ring | wheel side drape shape part, respectively. 本発明の第２実施の形態に係る自動調心ころ軸受の断面図である。It is sectional drawing of the self-aligning roller bearing which concerns on 2nd Embodiment of this invention. （ａ）は、本発明の第２実施の形態に係るころの拡大図であり、（ｂ）は、本発明の第２実施の形態に係る内輪の拡大断面図である。(A) is an enlarged view of the roller which concerns on 2nd Embodiment of this invention, (b) is an expanded sectional view of the inner ring | wheel which concerns on 2nd Embodiment of this invention. （ａ）は、内輪の球面ころ頭部側の拡大断面図であり、（ｂ）は、内輪の球面ころ端部側の拡大断面図である。(A) is an enlarged sectional view of the inner ring on the spherical roller head side, and (b) is an enlarged sectional view of the inner ring on the spherical roller end side. （ａ）（ｂ）は、夫々、球面ころ側ダラシ形状部の超仕上加工の加工工程を示す模式図である。(A) (b) is a schematic diagram which shows the process of super finishing of a spherical-roller side drip-shaped part, respectively. （ａ）（ｂ）は、夫々、球面ころ側ダラシ形状部のロータリードレス加工の加工工程を示す模式図である。(A) and (b) are the schematic diagrams which show the process of the rotary dressing of the spherical roller side dashi shape part, respectively. （ａ）は、従来に係る内輪と球面ころとの面圧分布を示すグラフであり、（ｂ）は、本発明に係る内輪と球面ころとの面圧分布を示すグラフである。(A) is a graph which shows the surface pressure distribution of the inner ring and spherical roller which concerns on the past, (b) is a graph which shows the surface pressure distribution of the inner ring and spherical roller which concerns on this invention. 従来に係る自動調心ころ軸受の断面図である。It is sectional drawing of the self-aligning roller bearing which concerns on the past. （ａ）は、従来に係るころの拡大図であり、（ｂ）は、従来に係る内輪の拡大断面図である。(A) is an enlarged view of the roller which concerns on the past, (b) is an expanded sectional view of the inner ring which concerns on the past. 本発明の第３実施の形態に係る自動調心軸受の模式図であって、面圧分布を示すものである。It is a schematic diagram of the self-aligning bearing which concerns on 3rd Embodiment of this invention, Comprising: Surface pressure distribution is shown. （ａ）は、本発明の第３実施の形態に係る自動調心軸受の模式図であって、中央面圧が高い場合の面圧分布を示すものであり、（ｂ）は、本発明の第３実施の形態に係る自動調心軸受の模式図であって、エッジロードと中央面圧とを低くした場合の面圧分布を示すものである。(A) is a schematic diagram of the self-aligning bearing according to the third embodiment of the present invention, and shows a surface pressure distribution when the central surface pressure is high, and (b) is a diagram of the present invention. It is a schematic diagram of the self-aligning bearing according to the third embodiment, and shows the surface pressure distribution when the edge load and the center surface pressure are lowered.

符号の説明Explanation of symbols

１ 外輪
２ 内輪
３ 球面ころ
４ 保持器
５ 軌道面
６ 軌道面
１０ 内輪側ダラシ形状部
１１ 超仕上砥石
１２ ドレス
１３ 砥石
２０ 球面ころ側ダラシ形状部
２１ 超仕上砥石
２２ ドレス
２３ 砥石
２４ ころ転動面 DESCRIPTION OF SYMBOLS 1 Outer ring 2 Inner ring 3 Spherical roller 4 Cage 5 Raceway 6 Raceway 10 Inner ring side dull shape part 11 Super finishing whetstone 12 Dress 13 Whetstone 20 Spherical roller side dart shape part 21 Super finishing whetstone 22 Dress 23 Whetstone 24 Rolling surface

Claims (5)

内周に円弧状の軌道を有する外輪と、
外周に外輪の軌道面に対向して配置した軌道面を有する内輪と、
外輪の軌道面と内輪の軌道面との間に介装した複数列の球面ころと、
これら複数列の球面ころを保持する保持器と、からなる、自動調心ころ軸受において、
前記内輪の軌道面の母線は、球面ころの頭部側又は端部側に対向する部位で、その曲率半径をなめらかに連続的に変化した内輪側ダラシ形状部を有することを特徴とする自動調心ころ軸受。 An outer ring having an arcuate track on the inner circumference;
An inner ring having a raceway surface disposed on the outer periphery facing the raceway surface of the outer ring;
A plurality of rows of spherical rollers interposed between the raceway surface of the outer ring and the raceway surface of the inner ring,
In a self-aligning roller bearing composed of a cage for holding these multiple rows of spherical rollers,
A self-adjusting characterized in that the generatrix of the raceway surface of the inner ring has an inner ring side dull shape portion whose radius of curvature changes smoothly and continuously at a portion facing the head side or end side of the spherical roller. Center roller bearing. 前記球面ころの軌道面の母線は、球面ころの頭部側又は端部側のエッジ部に、その曲率半径をなめらかに連続的に変化した球面ころ側ダラシ形状部を有することを特徴とする請求項１に記載の自動調心ころ軸受。   The generatrix of the raceway surface of the spherical roller has a spherical roller side dull shape portion whose radius of curvature changes smoothly and continuously at an edge portion on the head side or end side of the spherical roller. The self-aligning roller bearing according to Item 1. 前記内輪側ダラシ形状部及び前記球面ころ側ダラシ形状部以外の箇所に於いて、前記外輪又は内輪の軌道面アール寸法（Ｒ１）に対する、球面ころの転動面アール寸法（Ｒ２）の比率は、Ｒ２／Ｒ１＞０．９５であることを特徴とする請求項１又は２に記載の自動調心ころ軸受。   The ratio of the rolling surface radius dimension (R2) of the spherical roller to the raceway radius dimension (R1) of the outer ring or the inner ring at a place other than the inner ring side drag shape portion and the spherical roller side drag shape portion is: The self-aligning roller bearing according to claim 1 or 2, wherein R2 / R1> 0.95. 前記外輪、前記内輪、及び前記球面ころの少なくとも１つは、主として、Ｃ；０．３〜０．７重量％、及びＣｒ；１〜３重量％を含有する合金鋼、またはＪＩＳの高炭素クロム軸受鋼からなり、しかも、浸炭処理を施すことにより、表面層の残留オーステナイト量（γＲ）を、２０〜５０ｖｏｌ%とした軸受部材を用いたことを特徴とする請求項１乃至３のいずれか１項に記載の自動調心ころ軸受。 At least one of the outer ring, the inner ring, and the spherical roller is mainly made of an alloy steel containing C; 0.3 to 0.7% by weight and Cr; 1 to 3% by weight, or JIS high carbon chromium. 4. A bearing member comprising a bearing steel and having a surface layer retained austenite (γ R ) of 20 to 50 vol% by carburizing treatment. Spherical roller bearings according to item 1. 前記内輪側ダラシ形状部、又は前記球面ころ側ダラシ形状部は、超仕上加工、又は、ロータリードレス加工により形成してあることを特徴とする請求項１乃至４のいずれか１項に記載の自動調心ころ軸受。   The automatic according to any one of claims 1 to 4, wherein the inner ring side portion or the spherical roller side portion is formed by super finishing or rotary dressing. Spherical roller bearing.
JP2004112366A 2004-04-06 2004-04-06 Automatic aligning roller bearing Withdrawn JP2005299702A (en)

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Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2007263194A (en) * 2006-03-28 2007-10-11 Ntn Corp Rocking bearing
JP2008032224A (en) * 2006-07-31 2008-02-14 Snr Roulements Thin plate cage and spherical roller bearing equipped therewith
JP2013100837A (en) * 2011-11-07 2013-05-23 Ntn Corp Self-aligning roller bearing
CN103758867A (en) * 2014-01-03 2014-04-30 河南三维重工有限公司 Rolling body structure of self-aligning roller bearing
JP2015152084A (en) * 2014-02-14 2015-08-24 日本精工株式会社 Self-aligning roller bearing for elevator hoisting machine

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2007263194A (en) * 2006-03-28 2007-10-11 Ntn Corp Rocking bearing
JP4536675B2 (en) * 2006-03-28 2010-09-01 Ｎｔｎ株式会社 Swing bearing
JP2008032224A (en) * 2006-07-31 2008-02-14 Snr Roulements Thin plate cage and spherical roller bearing equipped therewith
JP2013100837A (en) * 2011-11-07 2013-05-23 Ntn Corp Self-aligning roller bearing
CN103758867A (en) * 2014-01-03 2014-04-30 河南三维重工有限公司 Rolling body structure of self-aligning roller bearing
JP2015152084A (en) * 2014-02-14 2015-08-24 日本精工株式会社 Self-aligning roller bearing for elevator hoisting machine

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