JP3480000B2 - Rolling bearing - Google Patents
Rolling bearingInfo
- Publication number
- JP3480000B2 JP3480000B2 JP17851993A JP17851993A JP3480000B2 JP 3480000 B2 JP3480000 B2 JP 3480000B2 JP 17851993 A JP17851993 A JP 17851993A JP 17851993 A JP17851993 A JP 17851993A JP 3480000 B2 JP3480000 B2 JP 3480000B2
- Authority
- JP
- Japan
- Prior art keywords
- guide
- guided
- raceway
- retainer
- guide surface
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/30—Parts of ball or roller bearings
- F16C33/46—Cages for rollers or needles
- F16C33/4605—Details of interaction of cage and race, e.g. retention or centring
-
- 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
- F16C33/3806—Details of interaction of cage and race, e.g. retention, centring
-
- 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
-
- 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
- F16C19/04—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly
- F16C19/06—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly with a single row or balls
-
- 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
- F16C19/24—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 radial load mainly
- F16C19/26—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 radial load mainly with a single row 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
- F16C2360/00—Engines or pumps
- F16C2360/23—Gas turbine engines
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Rolling Contact Bearings (AREA)
Description
【発明の詳細な説明】
【０００１】
【産業上の利用分野】この発明に係る転がり軸受は、ガ
スタービン、ジェットエンジン等の高速回転機械の回転
支持部分を構成する為に利用する。
【０００２】
【従来の技術】各種回転部分を支持する為に従来から、
図４〜５に示す様な転がり軸受が広く使用されている。
これら図４〜５に記載した転がり軸受は何れも、外周面
に内輪軌道１を有する内輪２と、内周面に外輪軌道３を
有する外輪４と、上記内輪軌道１と外輪軌道３との間に
転動自在に設けられた複数個の転動体５と、この複数個
の転動体５を保持した状態で、上記内輪軌道１と外輪軌
道３との間に回転自在に設けられた保持器６とを備えて
いる。
【０００３】この内の保持器６は、所謂もみ抜き保持器
と呼ばれるもので、合成樹脂又は金属により全体が円環
状に形成されている。この様な保持器６には、それぞれ
の内側に上記転動体５を転動自在に保持するポケット１
４を、円周方向に亙って複数個設けている。
【０００４】尚、図４に示した第１例の構造は、転動体
５として玉を使用し、内輪２を二分割構造とすると共
に、保持器６の内周面両端部に設けた被案内面７、７
と、内輪２の外周面両端部で上記内輪軌道１から外れた
部分に設けた案内面８、８とを近接対向させて、上記保
持器６の径方向に関する位置決めを図ったものである。
又、図５に示した第２例の構造は、転動体５としてころ
を使用し、内輪２の軸方向両端部内周面に鍔９、９を形
成して、両鍔９、９の間に上記転動体５を配置すると共
に、保持器６の外周面両端部に設けた被案内面７ａ、７
ａと、外輪４の外周面両端部で上記外輪軌道３から外れ
た部分に設けた案内面８ａ、８ａとを近接対向させて、
上記保持器６の径方向に関する位置決めを図ったもので
ある。従来これら各被案内面７、７ａ及び各案内面８、
８ａは、母線形状が直線である円筒面としていた。
【０００５】転がり軸受の使用時には、上記複数個の転
動体５の転動に伴って、上記内輪２と外輪４との相対回
転を自在とする。例えば、外輪４を固定し、内輪２を回
転させる場合には、上記複数の転動体５は、上記内輪２
の周囲を自転しつつ公転する。この際に上記保持器６
は、上記案内面８、８ａによって被案内面７、７ａを案
内されつつ、上記転動体５の公転速度（上記内輪２の回
転速度の半分程度）と同じ速度で、上記内輪２の周囲を
回転する。
【０００６】従って、転がり軸受の使用時には、上記各
被案内面７、７ａと上記各案内面８、８ａとの間には滑
り摩擦が生じる。そこで、転がり軸受潤滑用の潤滑油の
一部を、上記各被案内面７、７ａと上記各案内面８、８
ａとの間に導いて、これら両面７、７ａ、８、８ａ同士
の間に油膜を形成し、転がり軸受使用時の摩擦抵抗の低
減を図ると共に、上記各面７、７ａ、８、８ａの摩耗防
止を図っている。
【０００７】
【発明が解決しようとする課題】ところが、上述の様に
構成され作用する転がり軸受に於いては、従来次に述べ
る様な解決すべき点があった。即ち、保持器６の重心位
置と回転中心位置とが完全に一致する事は稀であり、多
くの場合にはこれら両位置同士が僅かにずれている。
又、転がり軸受の運転時には内輪２、外輪４、保持器６
等の構成各部材の温度が、摩擦熱等に起因して上昇する
が、温度上昇が各部で不均一になる事が多い。
【０００８】この為、高速回転機械に組み込まれる転が
り軸受の作用時には、保持器６に加わる遠心力や熱膨張
差に起因し、図６〜７に誇張して示す様に保持器６が内
輪２及び外輪４に対し傾斜して、被案内面７、７ａと案
内面８、８ａとが非平行になる場合がある。この際に保
持器６は、内輪２の周囲でぶれる様な不均一な回転運動
をする。尚、各図は、前記各被案内面７、７ａと各案内
面８、８ａとが最も近付いた部分の断面を示している。
従って、図示しない直径方向反対位置でこれら各面７、
７ａ、８、８ａ同士の間隔は、図示の状態よりも大きく
なっている。
【０００９】従来の転がり軸受に於いては前述の様に、
各被案内面７、７ａ及び各案内面８、８ａを、母線形状
が直線である円筒面としていた為、これら被案内面７、
７ａと案内面８、８ａとが非平行になると、被案内面
７、７ａの片端縁のみが案内面８、８ａと当接し、当接
部に所謂エッヂロードが加わる。この様なエッヂロード
に基づく当接圧の過度の上昇により、当接部に存在する
油膜が破断し、上記被案内面７、７ａと案内面８、８ａ
とが、油膜を介する事なく直接接触して、当接部に摩耗
や焼き付き等の不具合が生じ易くなる。本発明の転がり
軸受は、この様な不都合を解消すべく考えたものであ
る。
【００１０】
【課題を解決するための手段】本発明の転がり軸受は、
前述した従来の転がり軸受と同様に、外周面に内輪軌道
を有する内輪と、内周面に外輪軌道を有する外輪と、円
周方向に亙って複数のポケットを有し、上記内輪軌道と
外輪軌道との間に回転自在に設けられた保持器と、上記
ポケット内に転動自在に保持された状態で上記内輪軌道
と外輪軌道とに当接する複数の転動体とを備えている。
そして、上記保持器の一方の周面で上記ポケットから軸
方向に外れた部分を被案内面とし、上記内輪の外周面と
上記外輪の内周面との内の一方の周面の一部でこの一方
の周面に形成された軌道から外れた部分を案内面とし
て、この案内面と上記被案内面とを近接対向させる事に
より、上記保持器の径方向に関する位置決めを図ってい
る。
【００１１】特に、本発明の転がり軸受に於いては、上
記被案内面と案内面との内の一方の面を、軸方向に亙る
母線形状が滑らかに、且つ、当該被案内面又は案内面の
軸方向中央部が相手面に向け最も突出する状態で湾曲し
た凸面とすると共に、この凸面の母線の曲率半径Ｒを、
保持器の最大傾斜角度θと上記案内面による上記保持器
の案内幅Ｌとから、Ｒ＝Ｌ／２・sinθなる式で求めら
れる値にほぼ一致させた事を特徴としている。
【００１２】
【作用】上述の様に構成される本発明の転がり軸受の場
合、運転時に保持器が傾斜しても、被案内面の端縁が案
内面に当接する事がなくなる。即ち、被案内面と案内面
との一方が、軸方向中央部が相手面に向け最も突出す
る、適切な曲率半径を有する滑らかな凸面である為、保
持器が傾斜した場合でもこの凸面の軸方向中間部が相手
面と当接する事で、上記端縁が相手面と当接する事を防
止する。この結果、被案内面と案内面との間に存在する
油膜が破れにくくなって、これら両面の摩耗及び焼き付
き防止が図られる。
【００１３】
【実施例】次に、図面に基づいて本発明の実施例を説明
するが、本発明の特徴は被案内面又は案内面の形状にあ
り、その他の構成及び作用は前述した従来構造と同様で
ある。よって、従来構造と同等部分には同一符号を付し
て重複する説明を省略し、以下、本発明の特徴部分に就
いて説明する。
【００１４】図１は本発明の第一実施例を示している。
外輪４の軸方向両端部内周面に形成した鍔９の内周面に
設けた案内面１０ａは、軸方向に亙る母線形状が滑らか
に湾曲し軸方向中央部が最も下記の被案内面１１ａに向
け突出した（案内面１０ａの軸方向中央部の内径が最も
小さくなった）、蒲鉾状凸面としている。そして、この
案内面１０ａと、保持器６の両端部外周面に設けた被案
内面１１ａとを近接対向させている。
【００１５】尚、上記母線の曲率半径Ｒは、次の（１）
式により求める。この（１）式中、θは保持器６の最大
傾斜角度、即ち、保持器６が最も傾斜した状態でこの保
持器６の中心軸と内輪２及び外輪４の中心軸とがなす角
度である。又、Ｌは上記案内面１０ａによる保持器６の
案内幅、即ち、鍔９の内端縁と保持器６の外端縁との距
離である。尚、図１は、保持器６の傾斜角度と案内面１
０ａの湾曲とを誇張して表している。
Ｒ＝Ｌ／２・sinθ−−−（１）
【００１６】上述の様に構成される本発明の転がり軸受
の場合、運転時に保持器６が傾斜しても、被案内面１１
ａの中間部が案内面１０ａに対し、この案内面１０ａの
接線方向に当接する。即ち、上記被案内面１１ａの端縁
が上記案内面１０ａに当接する事がなくなる。この結
果、従来構造の様にエッヂロードが発生する事がなくな
り、上記被案内面１１ａと案内面１０ａとの当接圧を低
く維持できる。そして、これら両面１１ａ、１０ａ間に
存在する油膜１２が破れにくくなって、これら両面の摩
耗及び焼き付き防止を確実に図れる。
【００１７】尚、上記各案内面１０ａの曲率半径Ｒを、
上記（１）式で求められる値よりも大きくすると、保持
器６が大きく傾斜した場合に、この保持器６の端縁が上
記案内面１０ａに当接する可能性が生じる。反対に、上
記曲率半径Ｒを上記（１）式で求められる値よりもあま
り小さくすると、案内面１０ａと被案内面１１ａとの当
接圧が大きくなり過ぎる。即ち、上記曲率半径Ｒが上記
（１）式で求められる値から何れの方向にずれた場合で
も、上記油膜１２が破れる可能性が大きくなる為、好ま
しくない。
【００１８】次に、図２は本発明の第二実施例を示して
いる。本実施例の場合、１対の半片１３ａ、１３ｂを組
み合わせる事で内輪２を構成する内輪二分割構造に、本
発明を適用した例を示している。各半片１３ａ、１３ｂ
の外半部外周面に形成した案内面１０ｂ、１０ｂはそれ
ぞれ、軸方向に亙る母線形状が滑らかに湾曲し軸方向中
央部が最も下記の被案内面１ｂ、１１ｂに向け突出した
（案内面１０ｂの軸方向中央部の外径が最も大きくなっ
た）、蒲鉾状凸面としている。
【００１９】本実施例の場合、不均一な温度上昇に伴っ
て上記両半片１３ａ、１３ｂの熱膨張量に差が生じ、保
持器６が傾斜しても、上記各案内面１０ｂ、１０ｂの一
部が各被案内面１１ｂ、１１ｂに対して、各案内面１０
ｂ、１０ｂの接線方向に接し、上記各被案内面１１ｂ、
１１ｂの端縁が上記各案内面１０ｂ、１０ｂに当接する
事がなくなる。この結果、従来構造の様にエッヂロード
が発生する事がなくなり、上記各被案内面１１ｂ、１１
ｂと各案内面１０ｂ、１０ｂとの当接圧を低く維持し、
これら両面１１ｂ、１０ｂ間に存在する油膜１２を破れ
にくくして、これら両面１１ｂ、１０ｂの摩耗及び焼き
付き防止を確実に図れる。
【００２０】本実施例の様に、１対の半片１３ａ、１３
ｂを組み合わせた内輪２を使用した場合には、これら両
半片１３ａ、１３ｂの間に△Ｔだけ温度差を生じると、
両半片１３ａ、１３ｂの外周面に形成した案内面１０
ｂ、１０ｂの半径が、次の（２）式で表される△ｄだけ
異なる。
△ｄ＝α・Ｄ0 ・△Ｔ／２−−−（２）
尚、αは両半片１３ａ、１３ｂを構成する材料の線膨張
係数、Ｄ0 は常温時に於ける上記各案内面１０ｂ、１０
ｂの直径である。
【００２１】この状態で転がり軸受を使用すると、保持
器６は次の（３）式で表される角度θだけ傾斜したま
ま、内輪２の周囲で回転する。尚、この（３）式中でＷ
は、左右１対の被案内面１１ｂ、１１ｂと案内面１０
ｂ、１０ｂとの当接部同士の距離である。
θ＝tan-1 （△ｄ／Ｗ）−−−（３）
【００２２】例えば温度差△Ｔを８０℃、各案内面１０
ｂ、１０ｂの直径Ｄ0 を１５０mm、上記当接部同士の距
離Ｗを２０mm、構成材料の線膨張係数αを１２．５×１
０-6（１／℃）とした場合には、
θ＝tan-1 （12.5×10-6×150/2 ×80／20）≒０．２１
５（度）
となる。従って、前記各案内面１０ｂ、１０ｂの軸方向
に亙る母線形状の曲率半径Ｒ1 の最適値は、保持器６の
案内幅を６mmとすれば、前記（１）式より次の様に求め
られる。
Ｒ＝６／２・ sin0.215 °≒８００（mm）
【００２３】次に、図３は本発明の第三実施例を示して
いる。本実施例の場合、外輪４の両端部内周面に形成し
た１対の鍔９ａの内周面を案内面１０ｃとし、保持器６
の両端部外周面を被案内面１１ｃとしている。そして、
この被案内面１１ｃを、軸方向中央部が上記案内面１０
ｃに向け最も突出した、蒲鉾状の凸面としている。本実
施例の場合も、転がり軸受の使用時に保持器６が傾斜し
ても、上記案内面１０ｃと被案内面１１ｃとの当接圧が
過大とならず、両面１０ｃ、１１ｃ間の油膜１２の破断
を防止して、これら両面１０ｃ、１１ｃの摩耗及び焼き
付き防止を図れる。
【００２４】
【００２５】
【００２６】
【発明の効果】本発明の転がり軸受は、以上に述べた通
り構成され作用するが、案内面及び被案内面の摩耗並び
に焼き付き防止を確実に図れる為、転がり軸受並びにこ
の転がり軸受を組み込んだ機械装置の耐久性及び信頼性
の向上を図れる。Description: BACKGROUND OF THE INVENTION 1. Field of the Invention A rolling bearing according to the present invention is used for forming a rotation supporting portion of a high-speed rotating machine such as a gas turbine and a jet engine. 2. Description of the Related Art Conventionally, in order to support various rotating parts,
Rolling bearings as shown in FIGS. 4 and 5 are widely used.
Each of the rolling bearings described in FIGS. 4 and 5 has an inner race 2 having an inner raceway 1 on an outer peripheral surface, an outer race 4 having an outer raceway 3 on an inner peripheral surface, and a structure between the inner raceway 1 and the outer raceway 3. A plurality of rolling elements 5 rotatably provided on the inner ring raceway 1 and a retainer 6 rotatably provided between the inner raceway 1 and the outer raceway 3 while holding the plurality of rolling bodies 5. And [0003] The retainer 6 is a so-called machined retainer, and is entirely formed in an annular shape with synthetic resin or metal. Such cages 6 have pockets 1 inside each of them to hold the rolling elements 5 so as to freely roll.
4 are provided in the circumferential direction. The structure of the first example shown in FIG. 4 uses a ball as the rolling element 5, the inner ring 2 has a two-part structure, and a guided member provided at both ends of the inner peripheral surface of the retainer 6. Surface 7, 7
The guide surfaces 8, 8 provided at portions deviated from the inner raceway 1 at both ends of the outer peripheral surface of the inner race 2 are brought into close proximity to each other, thereby positioning the retainer 6 in the radial direction.
The structure of the second example shown in FIG. 5 uses rollers as the rolling elements 5, and forms flanges 9, 9 on the inner peripheral surfaces of both ends in the axial direction of the inner ring 2. The rolling elements 5 are arranged and guided surfaces 7a, 7 provided at both ends of the outer peripheral surface of the retainer 6 are provided.
a, and guide surfaces 8a, 8a provided at portions deviating from the outer raceway 3 at both ends of the outer peripheral surface of the outer race 4 so as to be closely opposed to each other,
This is for positioning the retainer 6 in the radial direction. Conventionally, each of these guided surfaces 7, 7a and each of the guiding surfaces 8,
8a is a cylindrical surface whose bus shape is a straight line. When a rolling bearing is used, the relative rotation between the inner ring 2 and the outer ring 4 is made free with the rolling of the plurality of rolling elements 5. For example, when the outer race 4 is fixed and the inner race 2 is rotated, the plurality of rolling elements 5
Orbiting while rotating around. At this time, the cage 6
Rotates around the inner ring 2 at the same speed as the revolving speed of the rolling element 5 (about half the rotation speed of the inner ring 2) while being guided on the guided surfaces 7 and 7a by the guide surfaces 8 and 8a. I do. Therefore, when the rolling bearing is used, sliding friction occurs between the guided surfaces 7, 7a and the guide surfaces 8, 8a. Therefore, a part of the lubricating oil for lubricating the rolling bearings is transferred to the respective guided surfaces 7, 7a and the respective guide surfaces 8, 8 respectively.
a between the two surfaces 7, 7a, 8, 8a to form an oil film between the two surfaces 7, 7a, 8, 8a to reduce the frictional resistance when the rolling bearing is used. Abrasion is prevented. [0007] However, in the rolling bearing constructed and operated as described above, there have conventionally been the following problems to be solved. That is, it is rare that the position of the center of gravity of the retainer 6 coincides with the position of the rotation center completely, and in many cases, these two positions are slightly shifted from each other.
When the rolling bearing is operated, the inner ring 2, the outer ring 4, the cage 6
Although the temperature of each component such as rises due to frictional heat or the like, the temperature rise often becomes non-uniform in each part. For this reason, when the rolling bearing incorporated in the high-speed rotating machine operates, the cage 6 is exaggerated as shown in FIGS. 6 and 7 due to the centrifugal force and the difference in thermal expansion applied to the cage 6. In addition, there is a case where the guided surfaces 7, 7a and the guide surfaces 8, 8a become non-parallel with each other by being inclined with respect to the outer ring 4. At this time, the retainer 6 makes a non-uniform rotational movement such as a shake around the inner ring 2. Each figure shows a cross section of a portion where the guided surfaces 7, 7a and the guide surfaces 8, 8a are closest to each other.
Therefore, these surfaces 7,
The intervals between 7a, 8, and 8a are larger than those shown in the figure. As described above, in a conventional rolling bearing,
Since each of the guided surfaces 7, 7a and each of the guiding surfaces 8, 8a were cylindrical surfaces whose bus shape was a straight line, these guided surfaces 7, 7a
When the guide surfaces 7 and 7a become non-parallel, only one edge of the guided surfaces 7 and 7a contacts the guide surfaces 8 and 8a, and a so-called edge load is applied to the contact portion. Due to such an excessive increase in the contact pressure based on the edge load, the oil film existing in the contact portion is broken, and the guided surfaces 7, 7a and the guide surfaces 8, 8a are broken.
Are in direct contact with each other without the aid of an oil film, and are likely to cause problems such as wear and seizure at the contact portion. The rolling bearing of the present invention has been made to solve such inconvenience. [0010] The rolling bearing of the present invention comprises:
Similar to the above-described conventional rolling bearing, the inner race having an inner raceway on an outer peripheral surface, an outer race having an outer raceway on an inner peripheral surface, and a plurality of pockets extending in a circumferential direction. A cage is provided rotatably between the raceway and a plurality of rolling elements abutting on the inner raceway and the outer raceway while being rotatably held in the pocket.
Then, a portion of one of the circumferential surfaces of the retainer that is deviated in the axial direction from the pocket is a guided surface, and a part of one of the outer circumferential surface of the inner ring and the inner circumferential surface of the outer ring. The portion of the one peripheral surface deviated from the orbit is used as a guide surface, and the guide surface and the guided surface are closely opposed to each other, thereby positioning the retainer in the radial direction. [0011] In particular, at the rolling bearing of the present invention, one surface of the said guided surface and the guide surface, the smooth generatrix shape over the axial direction and the guided surface or guide surface Is curved so that the axial center of the
And the radius of curvature R of the generatrix of the convex surface is
The cage by the maximum inclination angle θ of the cage and the guide surface
From the guide width L of R = L / 2 · sin θ
The feature is that it almost matches the value to be obtained . In the case of the rolling bearing of the present invention configured as described above, even if the cage is inclined during operation, the edge of the guided surface does not contact the guide surface. That is, one of the guided surface and the guide surface is a smooth convex surface having an appropriate radius of curvature, with the central portion in the axial direction most protruding toward the mating surface. By contacting the middle part in the direction with the mating surface, the edge is prevented from making contact with the mating surface. As a result, the oil film existing between the guided surface and the guide surface is less likely to be broken, and wear and seizure of these surfaces are prevented. Next, an embodiment of the present invention will be described with reference to the accompanying drawings. Is the same as Therefore, the same parts as those of the conventional structure are denoted by the same reference numerals, and redundant description will be omitted. Hereinafter, the characteristic parts of the present invention will be described. FIG. 1 shows a first embodiment of the present invention.
The guide surface 10a provided on the inner peripheral surface of the flange 9 formed on the inner peripheral surface of both ends in the axial direction of the outer ring 4 has a generatrix shape smoothly curved in the axial direction, and the central portion in the axial direction is the most guided surface 11a described below. The guide surface 10a has a semi-cylindrical convex surface (the inner diameter at the axial center of the guide surface 10a is the smallest). The guide surface 10a and the guided surfaces 11a provided on the outer peripheral surfaces of both ends of the retainer 6 are opposed to each other. The radius of curvature R of the above-mentioned bus is expressed by the following (1)
It is determined by the formula. In the expression (1), θ is the maximum inclination angle of the retainer 6, that is, the angle formed by the central axis of the retainer 6 and the central axes of the inner ring 2 and the outer ring 4 when the retainer 6 is inclined most. . L is the guide width of the retainer 6 by the guide surface 10a, that is, the distance between the inner edge of the flange 9 and the outer edge of the retainer 6. FIG. 1 shows the inclination angle of the cage 6 and the guide surface 1.
0a is exaggerated. R = L / 2 · sin θ-(1) In the case of the rolling bearing of the present invention configured as described above, even if the cage 6 is inclined during operation, the guided surface 11
The intermediate portion of a contacts the guide surface 10a in the tangential direction of the guide surface 10a. That is, the edge of the guided surface 11a does not contact the guide surface 10a. As a result, edge load does not occur unlike the conventional structure, and the contact pressure between the guided surface 11a and the guide surface 10a can be kept low. Then, the oil film 12 existing between the two surfaces 11a and 10a is hardly broken, and the wear and seizure of these two surfaces can be reliably prevented. The radius of curvature R of each guide surface 10a is
If the value is larger than the value obtained by the above equation (1), there is a possibility that the edge of the retainer 6 abuts on the guide surface 10a when the retainer 6 is greatly inclined. Conversely, if the radius of curvature R is much smaller than the value obtained by the above equation (1), the contact pressure between the guide surface 10a and the guided surface 11a becomes too large. That is, even if the radius of curvature R deviates in any direction from the value obtained by the above equation (1), the possibility that the oil film 12 is broken increases, which is not preferable. FIG. 2 shows a second embodiment of the present invention. In the case of the present embodiment, an example is shown in which the present invention is applied to an inner ring two-part structure in which the inner ring 2 is formed by combining a pair of halves 13a and 13b. Each half 13a, 13b
Each of the guide surfaces 10b, 10b formed on the outer peripheral surface of the outer half portion has a smoothly generated generatrix shape in the axial direction, and the central portion in the axial direction protrudes most toward the following guided surfaces 1b, 11b (the guide surface 10b). (The outer diameter at the central portion in the axial direction is largest). In the case of the present embodiment, a difference occurs in the amount of thermal expansion between the halves 13a and 13b due to the non-uniform temperature rise. The part is provided on each guide surface 10b for each guided surface 11b, 11b.
b, tangent to the tangential direction of 10b, each said guided surface 11b,
The edge of 11b does not contact the guide surfaces 10b, 10b. As a result, the edge load does not occur unlike the conventional structure, and each of the guided surfaces 11b, 11b
b and the contact pressure between each guide surface 10b and 10b is kept low,
The oil film 12 existing between the two surfaces 11b and 10b is hardly broken, and the wear and seizure of the two surfaces 11b and 10b can be reliably prevented. As in this embodiment, a pair of halves 13a, 13a
In the case where the inner ring 2 combining the two halves 13a and 13b is used, when a temperature difference ΔT occurs between the two halves 13a and 13b,
Guide surface 10 formed on the outer peripheral surface of both halves 13a, 13b
The radii of b and 10b differ by Δd expressed by the following equation (2). Δd = α · D 0 · ΔT / 2−2 (2) where α is the coefficient of linear expansion of the material forming the halves 13 a and 13 b, and D 0 is the guide surfaces 10 b and 10 at room temperature.
b is the diameter. When the rolling bearing is used in this state, the cage 6 rotates around the inner ring 2 while being inclined by the angle θ represented by the following equation (3). Note that W in the equation (3)
Are a pair of left and right guided surfaces 11b, 11b and a guiding surface 10
b, the distance between the contact portions with 10b. θ = tan -1 (△ d / W)-(3) For example, when the temperature difference ΔT is 80 ° C., each guide surface 10
b, 10b 150 mm diameter D 0 of the contact portion 20mm distance W between the linear expansion coefficient α of 12.5 × 1 of the material
If 0 -6 (1 / ° C.), θ = tan -1 (12.5 × 10 -6 × 150/2 × 80/20) ≒ 0.21
5 (degrees). Therefore, the optimum value of the radius of curvature R 1 of each guide surface 10b, bus shape over the axial direction of 10b, if the guide width of the cage 6 and 6 mm, determined as follows from the formula (1) . R = 6/2 · sin 0.215 ° ≒ 800 (mm) Next, FIG. 3 shows a third embodiment of the present invention. In the case of this embodiment, the inner peripheral surfaces of a pair of flanges 9a formed on the inner peripheral surfaces at both ends of the outer ring 4 are used as guide surfaces 10c,
Are formed as guide surfaces 11c. And
The guided surface 11c is positioned at the center in the axial direction.
The convex shape is the semicylindrical shape that protrudes most toward c. Also in the case of the present embodiment, even if the cage 6 is inclined when the rolling bearing is used, the contact pressure between the guide surface 10c and the guided surface 11c does not become excessive, and the oil film 12 between the two surfaces 10c, 11c is formed. Breakage can be prevented to prevent wear and seizure of these two surfaces 10c and 11c. The rolling bearing according to the present invention is constructed and operates as described above. However, the rolling bearing is used in order to surely prevent wear and seizure of the guide surface and the guided surface. It is possible to improve the durability and reliability of the bearing and the mechanical device incorporating the rolling bearing.
【図面の簡単な説明】
【図１】本発明の第一実施例を示す部分断面図。
【図２】同第二実施例を示す部分断面図。
【図３】同第三実施例を示す部分断面図。
【図４】従来の転がり軸受の第１例を示す部分断面図。
【図５】同第２例を示す部分断面図。
【図６】保持器が傾斜した状態を示す、図４の左部に相
当する部分断面図。
【図７】保持器が傾斜した状態を示す、図５の左部に相
当する部分断面図。
【符号の説明】
１ 内輪軌道
２ 内輪
３ 外輪軌道
４ 外輪
５ 転動体
６ 保持器
７、７ａ 被案内面
８、８ａ 案内面
９、９ａ 鍔
１０ａ、１０ｂ、１０ｃ 案内面
１１ａ、１１ｂ、１１ｃ 被案内面
１２ 油膜
１３ａ、１３ｂ 半片
１４ ポケットBRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a partial sectional view showing a first embodiment of the present invention. FIG. 2 is a partial sectional view showing the second embodiment. FIG. 3 is a partial sectional view showing the third embodiment. FIG. 4 is a partial sectional view showing a first example of a conventional rolling bearing. FIG. 5 is a partial sectional view showing the second example. FIG. 6 shows a state in which the cage is inclined,
FIG. FIG. 7 shows a state in which the cage is inclined,
FIG. [Description of Signs] 1 inner raceway 2 inner race 3 outer raceway 4 outer race 5 rolling element 6 cage 7, 7a guided surface 8, 8a guide surface 9, 9a flange 10a, 10b, 10c guide surface 11a, 11b, 11c guided Surface 12 Oil film 13a, 13b Half piece 14 pocket
───────────────────────────────────────────────────── フロントページの続き (56)参考文献 特開 昭54−30338（ＪＰ，Ａ) 実開 平２−57253（ＪＰ，Ｕ) 実開 昭53−59048（ＪＰ，Ｕ) 実開 平３−84414（ＪＰ，Ｕ) 実開 平５−8040（ＪＰ，Ｕ) 実開 平５−96548（ＪＰ，Ｕ) 実開 平１−174629（ＪＰ，Ｕ) 実開 平３−55920（ＪＰ，Ｕ) (58)調査した分野(Int.Cl.7，ＤＢ名) F16C 33/38 F16C 33/46 ──────────────────────────────────────────────────続 き Continuation of the front page (56) References JP-A-54-30338 (JP, A) JP-A 2-57253 (JP, U) JP-A 53-59048 (JP, U) JP-A 3- 84414 (JP, U) Japanese Utility Model 5-8040 (JP, U) Japanese Utility Model 5-96548 (JP, U) Japanese Utility Model 1-174629 (JP, U) Japanese Utility Model 3-55920 (JP, U) (58) Field surveyed (Int. Cl. 7 , DB name) F16C 33/38 F16C 33/46
Claims (1)
面に外輪軌道を有する外輪と、円周方向に亙って複数の
ポケットを有し、上記内輪軌道と外輪軌道との間に回転
自在に設けられた保持器と、上記ポケット内に転動自在
に保持された状態で上記内輪軌道と外輪軌道とに当接す
る複数の転動体とを備え、上記保持器の一方の周面で上
記ポケットから軸方向に外れた部分を被案内面とし、上
記内輪の外周面と上記外輪の内周面との内の一方の周面
の一部でこの一方の周面に形成された軌道から外れた部
分を案内面として、この案内面と上記被案内面とを近接
対向させる事により、上記保持器の径方向に関する位置
決めを図った転がり軸受に於いて、上記被案内面と案内
面との内の一方の面を、軸方向に亙る母線形状が滑らか
に、且つ、当該被案内面又は案内面の軸方向中央部が相
手面に向け最も突出する状態で湾曲した凸面とすると共
に、この凸面の母線の曲率半径Ｒを、保持器の最大傾斜
角度θと上記案内面による上記保持器の案内幅Ｌとか
ら、Ｒ＝Ｌ／２・sinθなる式で求められる値にほぼ一
致させた事を特徴とする転がり軸受。(57) [Claim 1] An inner race having an inner raceway on an outer peripheral surface, an outer race having an outer raceway on an inner peripheral surface, and a plurality of pockets extending in a circumferential direction. A retainer rotatably provided between the inner raceway and the outer raceway, and a plurality of rolling elements abutting on the inner raceway and the outer raceway while being rotatably held in the pocket, A portion of one of the outer circumferential surfaces of the retainer that is axially deviated from the pocket is a guided surface, and a portion of one of the outer circumferential surface of the inner ring and the inner circumferential surface of the outer ring forms one of the outer circumferential surfaces. In a rolling bearing that positions the retainer in the radial direction by making the portion deviated from the track formed on the peripheral surface a guide surface and closely opposing the guide surface and the guided surface, one surface of the said guided surface and the guide surface, the generatrix shape over the axial direction synovial Crab, and, co the axially central portion of the guided surface or guide surface is a convex surface curved in a state that protrudes most toward the mating surface
In addition, the radius of curvature R of the bus of this convex surface is determined by the maximum inclination of the cage.
The angle θ and the guide width L of the cage by the guide surface
Is approximately equal to the value obtained by the equation of R = L / 2 · sin θ.
Rolling bearing, characterized in that was Itasa.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP17851993A JP3480000B2 (en) | 1993-06-28 | 1993-06-28 | Rolling bearing |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP17851993A JP3480000B2 (en) | 1993-06-28 | 1993-06-28 | Rolling bearing |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH0712132A JPH0712132A (en) | 1995-01-17 |
| JP3480000B2 true JP3480000B2 (en) | 2003-12-15 |
Family
ID=16049900
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP17851993A Expired - Fee Related JP3480000B2 (en) | 1993-06-28 | 1993-06-28 | Rolling bearing |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3480000B2 (en) |
Families Citing this family (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2007303558A (en) * | 2006-05-11 | 2007-11-22 | Jtekt Corp | Rolling bearing device |
| JP5145742B2 (en) * | 2007-03-26 | 2013-02-20 | 株式会社ジェイテクト | Ball bearing |
| JP2009079674A (en) * | 2007-09-26 | 2009-04-16 | Jtekt Corp | Roller bearing cage |
| JP5146269B2 (en) * | 2007-11-07 | 2013-02-20 | 日本精工株式会社 | Ball bearing |
| EP2071203B1 (en) * | 2007-12-10 | 2015-02-25 | JTEKT Corporation | Rolling bearing and rolling bearing assembly |
| GB0821324D0 (en) * | 2008-11-24 | 2008-12-31 | Rolls Royce Plc | A rolling-element bearing |
| JP2013002567A (en) * | 2011-06-17 | 2013-01-07 | Ntn Corp | Cylindrical roller bearing |
| FR3137729B1 (en) * | 2022-07-06 | 2024-07-26 | Skf Svenska Kullagerfab Ab | Bearing for motor or electric machine |
| CN118208497A (en) * | 2022-12-16 | 2024-06-18 | 舍弗勒技术股份两合公司 | Roller bearings and cages |
Family Cites Families (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5359048U (en) * | 1976-10-22 | 1978-05-19 | ||
| JPS6020603B2 (en) * | 1977-08-10 | 1985-05-23 | 日本精工株式会社 | Rolling bearing with cage |
| JPH0642099Y2 (en) * | 1988-05-31 | 1994-11-02 | 日本精工株式会社 | Tapered roller bearing |
| JPH0257253U (en) * | 1988-10-13 | 1990-04-25 | ||
| JPH0355920U (en) * | 1989-10-02 | 1991-05-29 | ||
| JPH0384414U (en) * | 1989-12-19 | 1991-08-27 | ||
| JPH058040U (en) * | 1991-07-19 | 1993-02-02 | 株式会社安川電機 | Anguilura Ball Bearing |
| JPH0596548U (en) * | 1992-05-29 | 1993-12-27 | いすゞ自動車株式会社 | Rolling bearing |
-
1993
- 1993-06-28 JP JP17851993A patent/JP3480000B2/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| JPH0712132A (en) | 1995-01-17 |
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