JP4173342B2 - Grease filling structure and bearing lid - Google Patents

Grease filling structure and bearing lid Download PDF

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Publication number
JP4173342B2
JP4173342B2 JP2002286276A JP2002286276A JP4173342B2 JP 4173342 B2 JP4173342 B2 JP 4173342B2 JP 2002286276 A JP2002286276 A JP 2002286276A JP 2002286276 A JP2002286276 A JP 2002286276A JP 4173342 B2 JP4173342 B2 JP 4173342B2
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Prior art keywords
filling chamber
bearing
annular
grease
chamber
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JP2004124991A (en
Inventor
澄子 日比野
政治 鈴木
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Railway Technical Research Institute
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Railway Technical Research Institute
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/66—Special parts or details in view of lubrication
    • F16C33/6603—Special parts or details in view of lubrication with grease as lubricant
    • F16C33/6607—Retaining the grease in or near the bearing
    • F16C33/6618—Retaining the grease in or near the bearing in a reservoir in the sealing means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/66—Special parts or details in view of lubrication
    • F16C33/6603—Special parts or details in view of lubrication with grease as lubricant
    • F16C33/6629—Details of distribution or circulation inside the bearing, e.g. grooves on the cage or passages in the rolling elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • 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
    • F16C2380/00—Electrical apparatus
    • F16C2380/26—Dynamo-electric machines or combinations therewith, e.g. electro-motors and generators

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)
  • Motor Or Generator Frames (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)

Description

【０００１】
【発明の属する技術分野】
この発明は、軸受を潤滑するためのグリースを充填する充填室を備えるグリース充填構造及び軸受の端面に着脱自在に装着される軸受蓋に関する。
【０００２】
【従来の技術】
図７は、従来の軸受蓋の外観図であり、図７（Ａ）は平面図であり、図７（Ｂ）は図７（Ａ）のVII-VIIB線で切断した状態を示す断面図である。
従来の軸受蓋１１２は、軸受の端面に着脱自在に装着される部材である。この従来の軸受蓋１１２は、図７に示すように、グリースを充填する充填室１１２ａと、回転軸に固定されたカラーと嵌合する貫通孔１１２ｂと、この軸受蓋１１２を軸受に固定するためのボルトを挿入する貫通孔１１２ｃなどを備えている（例えば、特許文献１参照）。充填室１１２ａは、軸受の外輪と内輪との間の間隙部に沿って形成された環状充填室１１２ｄと、この環状充填室１１２ｄに沿って形成されておりこの環状充填室１１２ｄの一部と結合する外側充填室１１２ｅと、軸受の外輪の端面を抑える抑え部１１２ｆとを備えている、このような従来の軸受蓋１１２では、充填室１１２ａ内に封入するグリースの量が多いほど潤滑に有効であると考えられるため、環状充填室１１２ｄの水平方向の外側に外側充填室１１２ｅを２つ形成してグリースの充填量を増加させている。
【０００３】
【特許文献１】
特公昭52-27292号公報（第３頁第５欄第８行目〜第25行目、図４及び図８）
【０００４】
従来の軸受蓋は、環状の充填室と、この充填室の軸受側側面に形成され軸受の端面を抑える環状の隔壁と、この充填室の内径部と隔壁の内径部との間に形成された開口部とを備えている（例えば、特許文献２参照）。また、従来の軸受蓋は、これらの構成に加えて、充填室を円周方向に複数の部屋に仕切る仕切板とを備えている（例えば、特許文献３参照）。これらの従来の軸受蓋では、充填室から軸受内にグリース基油が円滑に流入するように、充填室の一部又は全部で軸受の外輪の内径に対して充填室の外径を同一又は小さく形成している。
【０００５】
【特許文献２】
特開平8-210362号公報（第３頁左欄第22行目〜第26行目、図２及び図４）
【特許文献３】
特開平8-338426号公報（第４頁右欄第16行目〜第25行目、図４）
【０００６】
【発明が解決しようとする課題】
従来の軸受蓋では、グリースの封入量を増やすために、実際の設計では充填室の深さ方向を大きくしたり、環状充填室に外側充填室を部分的に結合させたりしている。しかし、充填室の深さ方向を大きくすると充填室底から軸受までの距離が長くなり、グリース基油が円滑に軸受に到達しがたくなるという問題があった。さらに、軸受蓋の大きさには実際の設計上の制約があるため、充填室の深さ方向を大きくして充填室を大きくするのには限界があった。一方、従来の軸受蓋では、充填室の一部又は全部で軸受の外輪内径に対して充填室の外径を同一又は小さく形成しなければならないという設計思想であり、この設計思想によれば充填室を大きくするのには限界があった。その結果、充填室に封入されたグリースからグリース基油を軸受に長時間供給することができず、グリースによる潤滑寿命を延ばすことができなかった。
【０００７】
この発明の課題は、充填室内のグリースを有効に利用して潤滑寿命を延ばすことができるグリース充填構造及び軸受蓋を提供することである。
【０００８】
【課題を解決するための手段】
この発明は、以下に記載するような解決手段により、前記課題を解決する。
なお、この発明の実施形態に対応する符号を付して説明するが、この実施形態に限定するものではない。
請求項１の発明は、軸受（１０，１１）の外輪（１０ｃ，１１ｃ）と内輪（１０ｄ，１１ｄ）との間の間隙部に沿って形成された環状充填室（１２ｄ，１３ｄ）と、前記環状充填室の外側に拡大して形成された外側充填室（１２ｅ，１３ｅ）と、前記外輪の端面を抑える抑え部（１２ｆ，１３ｆ）とを有し、前記軸受を潤滑するためのグリースを充填する充填室（１２ａ，１３ａ）を備えるグリース充填構造において、前記環状充填室及び前記外側充填室は、前記軸受の端面側に開口部（１２ｇ，１３ｇ）を有し、前記外側充填室は、前記環状充填室に沿って形成されており、この環状充填室の略全周でこの環状充填室と結合し、かつ、この環状充填室の略全周で外側に拡大して形成されており、前記外側充填室の外径（Ｒ1 ）は、前記外輪の外径（Ｒ2 ）よりも大きく形成されており、前記抑え部は、前記外側充填室を複数の領域（Ａ 1 〜Ａ 6 ）に区画するように、この外側充填室の周方向に間隔をあけて複数形成されていることを特徴とするグリース充填構造である。
【００１２】
請求項２の発明は、請求項１に記載のグリース充填構造において、前記充填室は、前記環状充填室と前記外側充填室とが結合する結合部分（Ｐ1 〜Ｐ6 ）が略同一の幅（Ｗ）と深さ（Ｄ）で形成されていることを特徴とするグリース充填構造である。
【００１３】
請求項３の発明は、軸受（１０，１１）の端面に着脱自在に装着される軸受蓋であって、請求項１又は請求項２に記載のグリース充填構造を備えることを特徴とする軸受蓋（１２，１３）である。
【００１４】
【発明の実施の形態】
（第１実施形態）
以下、図面を参照して、この発明の第１実施形態について詳しく説明する。
図１は、この発明の第１実施形態に係る軸受蓋を備える電動機枠体の断面図である。
電動機枠体１は、電動機を収容する部材であり、鉄道車両の駆動用電動機（主電動機）を収容する外枠などである。電動機枠体１は、図１に示すように、フレーム２と、ブラケット３，４と、回転軸５と、カラー６〜９と、軸受１０，１１と、軸受蓋１２〜１５などから構成されている。
【００１５】
フレーム２は、図示しない電動機の固定子を固定し支持する部材であり、両端部にフランジ部２ａ，２ｂが形成されている。ブラケット３は、フレーム２と軸受蓋１４とを連結する部材であり、フランジ部２ａと接合するフランジ部３ａが形成されている。ブラケット４は、フレーム２と軸受蓋１５とを連結する部材であり、フランジ部２ｂと接合するフランジ部４ａが形成されている。回転軸５は、図示しない電動機の回転子を固定し支持する部材であり、カラー６〜９は回転軸５の両端部に嵌め込まれた円環状の部材である。軸受１０，１１は、回転軸５を回転自在に支持する部材であり、軸受１０は深溝玉軸受であり、軸受１１は円筒ころ軸受である。軸受１０，１１は、転動体１０ａ，１１ａと、この転動体１０ａ，１１ａを等間隔に保持する保持器１０ｂ，１１ｂと、この保持器１０ｂ，１１ｂの外側で回転する外輪１０ｃ，１１ｃと、この保持器１０ｂ，１１ｂの内側で回転する内輪１０ｄ，１１ｄとから構成されている。
【００１６】
図２は、この発明の第１実施形態に係る軸受蓋の平面図であり、図２（Ａ）は図１のIIA方向から見た平面図であり、図２（Ｂ）は図１のIIB方向から見た平面図であり、図２（Ｃ）は図１のIIC方向から見た平面図であり、図２（Ｄ）は図１のIID方向から見た平面図である。図３は、この発明の第１実施形態に係る軸受蓋の外観図であり、図３（Ａ）は平面図であり、図３（Ｂ）は図３（Ａ）のIII-IIIB線で切断した状態を示す断面図である。
【００１７】
軸受蓋１２〜１５は、軸受１０，１１の端面に着脱自在に装着される部材であり、アルミニウム又は鉄などからなる鋳造品や機械加工品である。軸受蓋１２，１３は、電動機枠体１の外側に装着される端蓋であり、軸受蓋１４，１５は電動機枠体１の内側に装着される油きりである。軸受蓋１２は、軸受蓋１４との間で軸受１０を挟み込むようにボルトによって軸受蓋１４に固定されており、軸受蓋１３は軸受１１を挟み込むようにボルトによって軸受蓋１５に固定されている。軸受蓋１２，１３は、図２（Ａ）（Ｄ）に示すように、いずれも略同一のグリース充填構造を備え、軸受蓋１４，１５は図２（Ｂ）（Ｃ）に示すように、いずれも略同一のグリース充填構造を備える。以下では、軸受蓋１２，１４側について説明し、軸受蓋１３，１５側の部分については軸受蓋１２，１４側の部分と対応する符号を付して詳細な説明を省略する。
【００１８】
軸受蓋１２は、図３に示すように、充填室１２ａと貫通孔１２ｂ，１２ｃとを備えている。充填室１２ａは、軸受１０を潤滑するためのグリースを充填する部分であり、環状充填室（第１グリース室）１２ｄと、外側充填室（第２グリース室）１２ｅと、抑え部１２ｆとを有する。充填室１２ａは、図３（Ｂ）に示すように、断面形状が四角形に形成されている。充填室１２ａは、環状充填室１２ｄと外側充填室１２ｅとが結合する結合部分Ｐ1 〜Ｐ6 が略同一の幅Ｗと深さＤになるように形成されている。充填室１２ａは、例えば、図１に示す環状充填室１２ｄの内周面の軸受１０と接触する接触部分Ｓから直径方向及び深さ方向の距離が略同一となるように形成されている。
【００１９】
環状充填室１２ｄは、外輪１０ｃと内輪１０ｄとの間の間隙部（軸受開口部）に沿って形成された部分であり、図３に示すように貫通孔１２ｂを囲むように円環状に形成された凹状の溝である。外側充填室１２ｅは、環状充填室１２ｄの外側に拡大して形成された部分であり環状充填室１２ｄと一体に形成されている。外側充填室１２ｅは、環状充填室１２ｄに沿って形成されており、抑え部１２ｆが形成された部分を除きこの環状充填室１２ｄと略全周で結合する凹状の溝である。図１及び図３（Ａ）に示すように、外側充填室１２ｅの外径Ｒ1 は、外輪１０ｃの外径Ｒ2 よりも大きく形成されている。環状充填室１２ｄ及び外側充填室１２ｅは、図３（Ｂ）に示すように、軸受１０の端面側に開口部１２ｇを有する。抑え部１２ｆは、外輪１０ｃの端面を抑える部分である。抑え部１２ｆは、図３（Ａ）に示すように、外側充填室１２ｅを６つの領域Ａ1 〜Ａ6 に区画するように、この外側充填室１２ｅの周方向に間隔をあけて６つ形成されている。貫通孔１２ｂは、図１に示すカラー６の外周部と嵌合する嵌合孔であり、貫通孔１２ｃは軸受蓋１２を軸受蓋１４に固定するためのボルトを挿入する挿入孔である。
【００２０】
軸受蓋１４は、図２（Ｂ）に示すように、環状充填室１４ａと抑え部１４ｂと貫通孔１４ｃなどを備えている。環状充填室１４ａは、軸受１０を潤滑するためのグリースを充填する部分である。環状充填室１４ａは、外輪１０ｃと内輪１０ｄとの間の間隙部に沿って形成されており、貫通孔１４ｃを囲むように円環状に形成された凹部である。図１に示すように、環状充填室１４ａの外径Ｒ3 は、軸受１０の外輪１０ｃの内径Ｒ4 よりも大きく形成されている。図２（Ｂ）に示す抑え部１４ｂは、軸受１０の外輪１０ｃの端面を抑える部分であり、貫通孔１４ｃは図１に示すカラー７の外周部と嵌合する嵌合孔である。
【００２１】
この発明の第１実施形態に係る軸受蓋には、以下に記載する効果がある。
(1) この第１実施形態では、環状充填室１２ｄの外側に拡大して外側充填室１２ｅが形成されており、外側充填室１２ｅは環状充填室１２ｄに沿って形成されており、環状充填室１２ｄの略全周でこの環状充填室１２ｄと結合する。このため、図７に示す従来の軸受蓋１１２に比べて充填室１２ａ内に充填するグリース量を増加させることができる。また、外側充填室１２ｅと環状充填室１２ｄとが接する面積が増大するため、グリース基油の移動が活発になって充填室１２ａ内のグリースの総量を有効に使うことができる。その結果、軸受１０の潤滑寿命を延ばすことができるとともに、グリースの交換時期が延長するためメンテナンス作業などを減らすことができる。
【００２２】
(2) この第１実施形態では、環状充填室１２ｄ及び外側充填室１２ｅは軸受１０の端面側に開口部１２ｇを有する。このため、従来の軸受蓋のように充填室の軸受側側面に軸受の端面を抑える環状の隔壁を形成する場合に比べて、構造が簡単になり軸受蓋１２〜１５を簡単に製造することができる。
【００２３】
(3) この第１実施形態では、外側充填室１２ｅの外径Ｒ1 は、外輪１０ｃの外径Ｒ2 よりも大きく形成されており、この外輪１０ｃの端面を抑える抑え部１２ｆを充填室１２ａが有する。このため、充填室１２ａ内に充填するグリース量を増加させるとともに、抑え部１２ｆによって充填室１２ａ内に軸受１０が落ち込むのを防止することができる。
【００２４】
(4) この第１実施形態では、外側充填室１２ｅを複数の領域Ａ1 〜Ａ6 に区画するように、この外側充填室１２ｅの周方向に間隔をあけて抑え部１２ｆが複数形成されている。このため、外側充填室１２ｅ内に充填されたグリースが位置決めされてこのグリースの位置ずれを防止することができる。
【００２５】
(5) この第１実施形態では、環状充填室１２ｄと外側充填室１２ｅとが結合する結合部分Ｐ1 〜Ｐ6 が略同一の幅Ｗと深さＤで形成されている。その結果、充填室１２ａが直径方向及び深さ方向のいずれか一方に片寄ることなく略同等に拡大するため、充填室１２ａからのグリース基油の移動が活発になり、軸受１０の寿命を延ばすことができる。
【００２６】
【実施例】
次に、この発明の実施例について説明する。
図４は、この発明の実施例に係る軸受蓋の外観図であり、図４（Ａ）は基本型の外観図であり、図４（Ｂ）は実施例１，２の外観図であり、図４（Ｃ）は実施例３，４の外観図であり、図４（Ｄ）は実施例５，６の外観図であり、図４（Ｅ）は実施例７，８の外観図である。なお、図４（Ａ）に示す基本型の充填室は、図７に示す従来の軸受蓋１１２の充填室と同一構造である。
一般に、外側充填室１２ｅの構造が異なる場合には、封入されたグリースの挙動も異なることが知られている。そこで、外側充填室１２ｅの形状とこの外側充填室１２ｅに充填されたグリースの基油の移動しやすさとの関係を調査するために、小型の試験軸受（玉軸受6206）に合わせてアルミニウム製の小型の軸受蓋モデル（実施例１〜実施例８）を設計し製作した。但し、これらの実施例１〜実施例８には、図７に示す抑え部１１２ｆに対応する抑え部が設けられていない。
【００２７】
（実施例１，２）
実施例１，２は、環状充填室１２ｄに対する外側充填室１２ｅの結合角度を変化させた実施例である。実施例１は、環状充填室１２ｄの外周部接線上に外側充填室１２ｅを結合させた実施例であり、実施例２は環状充填室１２ｄの外周部に外側充填室１２ｅを水平に結合させた実施例である。
【００２８】
（実施例３，４）
実施例３，４は、外側充填室１２ｅから環状充填室１２ｄに通じる油道の数を変化させた実施例であり、実施例３は油道の数が両側に各２本（合計４本）の実施例であり、実施例４は油道の数が片側１本の実施例である。
【００２９】
（実施例５，６）
実施例５，６は、外側充填室１２ｅの直径方向の幅を変化させた実施例であり、実施例５は、外側充填室１２ｅの幅を１／２にした実施例であり、実施例６は外側充填室１２ｅの幅を２倍にした実施例である。
【００３０】
（実施例７，８）
実施例７，８は、外側充填室１２ｅの方向を変化させた実施例であり、実施例７は外側充填室１２ｅを上向きにした実施例であり、実施例８は外側充填室１２ｅを下向きにした実施例である。
【００３１】
実施例１〜８では、環状充填室１２ｄについては容積と形状とが同一であるが、外側充填室１２ｅについては容積を同一にして形状のみを変化させた。図４（Ｂ）〜図４（Ｅ）では、グリース基油の動き易さの観点から、図４（Ａ）に示す基本型の軸受蓋に比べて優れていると考えられる実施例を上段に示し、劣っていると考えられるものを下段に示している。
【００３２】
次に、トレーサ入りのグリースを用いてグリース基油の挙動試験を実施し、外側充填室１２ｅの形状による影響について検討した。先ず、実施例１〜８の環状充填室１２ｄには現行グリース（ちょう度２）を封入し、外側充填室１２ｅにはトレーサを混入した現行グリースを充填して、開口部１２ｇが地面に対して垂直になるように立て、温度１００°Ｃで１００時間の静置試験を行った。その後、外側充填室１２ｅ内のトレーサ入りのグリース基油が環状充填室１２ｄ内にどれだけ移動したか評価するために、図４に示すように環状充填室１２ｄ上の８箇所の測定箇所でトレーサ濃度を分析した。なお、実施例７，８については、トレーサ濃度測定時に方向を揃えて測定した。
【００３３】
図５は、この発明の実施例に係る軸受蓋のトレーサ濃度の測定結果を示すグラフであり、図５（Ａ）は実施例１，２の測定結果であり、図５（Ｂ）は実施例３，４の測定結果であり、図５（Ｃ）は実施例５，６の測定結果であり、図５（Ｄ）は実施例４，７，８の測定結果である。
実施例１，２については、図５（Ａ）に示すように、環状充填室１２ｄ全体においてトレーサ濃度分布に大きな変化は見られなかった。実施例１については、基本型に比べてグリース基油の移動がやや優れているように見えるが、基本型との差は小さかった。実施例３，４については、図５（Ｂ）に示すように、基本型に比べて外側充填室１２ｅに近い部分では部分的にトレーサ濃度分布に変化が見られるが、環状充填室１２ｄ全体においてトレーサ濃度分布に大きな変化は見られなかった。実施例５，６については、図５（Ｃ）に示すように、グリース濃度分布に大きな変化が見られた。実施例５については、環状充填室１２ｄに外側充填室１２ｅが接する部分が大きいため、環状充填室１２ｄ全体として平均的にトレーサ濃度分布に変化が起きている。一方、実施例６については、環状充填室１２ｄに最も近い２点（０°，１８０°）以外の部分ではトレーサ濃度分布の変化が少なかった。実施例７，８については、図５（Ｄ）に示すように、実施例７（上向き）、実施例４（横向き）、実施例８（下向き）の順にグリース基油の移動が活発であったが、環状充填室１２ｄ全体としてはグリース濃度分布に大きな差が見られなかった。
【００３４】
以上の結果、グリース基油は、封入当初から外側充填室１２ｅと環状充填室１２ｄとの間で活発に移動しており、外側充填室１２ｅと環状充填室１２ｄとが接する面積が大きいほどグリース基油が移動する程度も大きくなることが確認された。このため、外側充填室１２ｅと環状充填室１２ｄとは部分的に結合させるよりも、図３に示す軸受蓋１２のように外側充填室１２ｅと環状充填室１２ｄとをできるだけ広い面積で結合させることが望ましいと考えられる。この場合には、外側充填室１２ｅと環状充填室１２ｄとの結合部分の中心角の合計が全周に近いほどグリース基油の移動が活発になると考えられる。また、従来の軸受蓋では、充填室の一部又は全部で軸受の外輪の内径よりも充填室の外径を同一又は小さくしているが、外輪１０ｃの内径Ｒ 4 よりも外側充填室１２ｅの外径Ｒ1 が大きくてもグリース基油が十分に移動することが実施例５の測定結果から確認された。さらに、従来、重力の方向にグリース基油が移動しやすいと考えられていたが、実施例７，８の測定結果からグリース基油の移動に重力の影響が少ないことが確認された。
【００３５】
（第２実施形態）
図６は、この発明の第２実施形態に係る軸受蓋の外観図であり、図６（Ａ）は平面図であり、図６（Ｂ）は図６（Ａ）のVI-VIB線で切断した状態を示す断面図である。図６では、図３に示す部分と同一の部分については、同一の番号を付して詳細な説明を省略する。
この第２実施形態では、環状充填室１２ｄと外側充填室１２ｅとの境界Ｌに沿って、この外側充填室１２ｅの周方向に間隔をあけて抑え部１２ｆが６つ形成されている。この第２実施形態では、抑え部１２ｆが外側充填室１２ｅの外周部と分離して薄板状に形成されているため、第１実施形態に比べて外側充填室１２ｅ内にグリースをより一層多く充填することができる。また、外側充填室１２ｅ側から、環状充填室１２ｄにグリースが落下するのを抑え部１２ｆが防止する。
【００３６】
（他の実施形態）
この発明は、以上説明した実施形態に限定するものではなく、以下に記載するように種々の変形又は変更が可能であり、これらもこの発明の範囲内である。
(1) この実施形態では、鉄道車両の主電動機の回転軸５を支持する軸受１０，１１を例に挙げて説明したがこれに限定するものではなく、この発明は軸受一般に適用することができる。また、この実施形態では、軸受蓋１２，１３側のグリース充填構造を例に挙げて説明したが、軸受蓋１４，１５側についてもこの発明を適用することができる。さらに、この実施形態では、環状充填室１２ｄと外側充填室１２ｅとの結合部分Ｐ1 〜Ｐ6 の幅Ｗ及び深さＤを同一にした場合を例に挙げて説明したが、構造上の制約を受けない場合にはいずれか一方を大きくすることができる。
【００３７】
(2) この実施形態では、充填室１２ａの断面形状が四角形である場合を例に挙げて説明したが、断面形状をＵ字状や半円状に形成してもよい。また、この実施形態では、環状充填室１２ｄと外側充填室１２ｅとを可能な限り全周で結合しているが、構造上の制約などによって両者が分断される場合にはこれらを接続する通路を形成しこの通路の断面積を可能な限り大きくすることが好ましい。
【００３８】
【発明の効果】
以上説明したように、この発明によると、充填室内のグリースを有効に利用して潤滑寿命を延ばすことができる。
【図面の簡単な説明】
【図１】この発明の第１実施形態に係る軸受蓋を備える電動機枠体の断面図である。
【図２】この発明の第１実施形態に係る軸受蓋の平面図であり、（Ａ）は図１のIIA方向から見た平面図であり、（Ｂ）は図１のIIB方向から見た平面図であり、（Ｃ）は図１のIIC方向から見た平面図であり、（Ｄ）は図１のIID方向から見た平面図である。
【図３】この発明の第１実施形態に係る軸受蓋の外観図であり、（Ａ）は平面図であり、（Ｂ）は（Ａ）のIII-IIIB線で切断した状態を示す断面図である。
【図４】この発明の実施例に係る軸受蓋の外観図であり、（Ａ）は基本型の外観図であり、（Ｂ）は実施例１，２の外観図であり、（Ｃ）は実施例３，４の外観図であり、（Ｄ）は実施例５，６の外観図であり、（Ｅ）は実施例７，８の外観図である。
【図５】この発明の実施例に係る軸受蓋のトレーサ濃度の測定結果を示すグラフであり、（Ａ）は実施例１，２の測定結果であり、（Ｂ）は実施例３，４の測定結果であり、（Ｃ）は実施例５，６の測定結果であり、（Ｄ）は実施例４，７，８の測定結果である。
【図６】この発明の第２実施形態に係る軸受蓋の外観図であり、（Ａ）は平面図であり、（Ｂ）は（Ａ）のVI-VIB線で切断した状態を示す断面図である。
【図７】従来の軸受蓋の外観図であり、（Ａ）は平面図であり、（Ｂ）は（Ａ）のVII-VIIB線で切断した状態を示す断面図である。
【符号の説明】
１ 電動機枠体
１０，１１ 軸受
１０ｃ，１１ｃ 外輪
１０ｄ，１１ｄ 内輪
１２〜１５ 軸受蓋
１２ａ 充填室
１２ｄ 環状充填室
１２ｅ 外側充填室
１２ｆ 抑え部
１２ｇ 開口部
Ｒ1 外側充填室の外径
Ｒ2 外輪の外径
Ｒ3 環状充填室の外径
Ｒ4 外輪の内径
Ａ1 〜Ａ6 領域
Ｐ1 〜Ｐ6 結合部分
Ｗ 幅
Ｄ 深さ
Ｌ 境界[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a grease filling structure including a filling chamber filled with grease for lubricating a bearing, and a bearing lid that is detachably attached to an end surface of the bearing.
[0002]
[Prior art]
7 is an external view of a conventional bearing lid, FIG. 7 (A) is a plan view, and FIG. 7 (B) is a cross-sectional view showing a state cut along line VII-VIIB in FIG. 7 (A). is there.
The conventional bearing lid 112 is a member that is detachably attached to the end face of the bearing. As shown in FIG. 7, the conventional bearing lid 112 has a filling chamber 112a filled with grease, a through-hole 112b fitted with a collar fixed to the rotating shaft, and the bearing lid 112 for fixing the bearing lid 112 to the bearing. A through hole 112c for inserting the bolt is provided (for example, see Patent Document 1). The filling chamber 112a is formed along an annular filling chamber 112d formed along the gap between the outer ring and the inner ring of the bearing, and is formed along the annular filling chamber 112d and is coupled to a part of the annular filling chamber 112d. In such a conventional bearing lid 112 having an outer filling chamber 112e and a restraining portion 112f that suppresses the end face of the outer ring of the bearing, the larger the amount of grease enclosed in the filling chamber 112a, the more effective the lubrication. For this reason, two outer filling chambers 112e are formed outside the annular filling chamber 112d in the horizontal direction to increase the amount of grease filled.
[0003]
[Patent Document 1]
Japanese Examined Patent Publication No. 52-27292 (page 3, column 5, lines 8 to 25, FIGS. 4 and 8)
[0004]
A conventional bearing lid is formed between an annular filling chamber, an annular partition formed on the bearing side surface of the filling chamber to restrain the end face of the bearing, and an inner diameter portion of the filling chamber and an inner diameter portion of the partition wall. (For example, refer patent document 2). In addition to these configurations, the conventional bearing lid includes a partition plate that partitions the filling chamber into a plurality of chambers in the circumferential direction (see, for example, Patent Document 3). In these conventional bearing lids, the outer diameter of the filling chamber is the same or smaller than the inner diameter of the outer ring of the bearing in part or all of the filling chamber so that the grease base oil smoothly flows into the bearing from the filling chamber. Forming.
[0005]
[Patent Document 2]
JP-A-8-210362 (page 3, left column, lines 22-26, FIGS. 2 and 4)
[Patent Document 3]
JP-A-8-338426 (page 4, right column, lines 16 to 25, FIG. 4)
[0006]
[Problems to be solved by the invention]
In the conventional bearing lid, in order to increase the amount of grease filled, in the actual design, the depth direction of the filling chamber is increased, or the outer filling chamber is partially coupled to the annular filling chamber. However, when the depth direction of the filling chamber is increased, the distance from the bottom of the filling chamber to the bearing becomes longer, and there is a problem that the grease base oil does not easily reach the bearing. Furthermore, since the size of the bearing lid is limited in actual design, there is a limit to enlarging the filling chamber by increasing the depth direction of the filling chamber. On the other hand, the conventional bearing lid has a design concept that the outer diameter of the filling chamber must be the same or smaller than the inner diameter of the outer ring of the bearing in part or all of the filling chamber. There was a limit to the size of the room. As a result, the grease base oil could not be supplied to the bearing for a long time from the grease sealed in the filling chamber, and the lubrication life by the grease could not be extended.
[0007]
An object of the present invention is to provide a grease filling structure and a bearing lid capable of effectively utilizing the grease in the filling chamber and extending the lubrication life.
[0008]
[Means for Solving the Problems]
The present invention solves the above-mentioned problems by the solving means described below.
In addition, although the code | symbol corresponding to embodiment of this invention is attached | subjected and demonstrated, it is not limited to this embodiment.
The invention of claim 1 includes an annular filling chamber (12d, 13d) formed along a gap between the outer ring (10c, 11c) and the inner ring (10d, 11d) of the bearing (10, 11), An outer filling chamber (12e, 13e) formed outside the annular filling chamber and a holding portion (12f, 13f) for suppressing the end face of the outer ring are filled with grease for lubricating the bearing. In the grease filling structure including the filling chambers (12a, 13a), the annular filling chamber and the outer filling chamber have an opening (12g, 13g) on the end face side of the bearing, Formed along the annular filling chamber, is joined to the annular filling chamber at substantially the entire circumference of the annular filling chamber, and is formed to expand outward at substantially the entire circumference of the annular filling chamber, outer diameter of the outer filling chamber (R 1), the outer ring Outer diameter (R 2) is formed larger than the pressing section so as to partition the outer filling chamber into a plurality of areas (A 1 ~A 6), the intervals in the circumferential direction of the outer filling chamber The grease filling structure is characterized in that a plurality of gaps are formed .
[0012]
According to a second aspect of the present invention, in the grease filling structure according to the first aspect of the invention, the filling chamber has a width where coupling portions (P 1 to P 6 ) where the annular filling chamber and the outer filling chamber are coupled are substantially the same. It is a grease filling structure characterized by being formed with (W) and depth (D).
[0013]
The invention according to claim 3 is a bearing lid that is detachably attached to the end face of the bearing (10, 11), and comprises the grease filling structure according to claim 1 or claim 2. (12, 13).
[0014]
DETAILED DESCRIPTION OF THE INVENTION
(First embodiment)
Hereinafter, a first embodiment of the present invention will be described in detail with reference to the drawings.
FIG. 1 is a cross-sectional view of an electric motor frame including a bearing lid according to the first embodiment of the present invention.
The electric motor frame 1 is a member that accommodates the electric motor, such as an outer frame that accommodates a driving motor (main motor) for a railway vehicle. As shown in FIG. 1, the motor frame 1 includes a frame 2, brackets 3 and 4, a rotating shaft 5, collars 6 to 9, bearings 10 and 11, bearing lids 12 to 15, and the like. Yes.
[0015]
The frame 2 is a member that fixes and supports a stator of an electric motor (not shown), and flange portions 2a and 2b are formed at both ends. The bracket 3 is a member that connects the frame 2 and the bearing lid 14, and has a flange portion 3 a that is joined to the flange portion 2 a. The bracket 4 is a member that connects the frame 2 and the bearing lid 15, and has a flange portion 4 a that is joined to the flange portion 2 b. The rotating shaft 5 is a member that fixes and supports a rotor of an electric motor (not shown), and the collars 6 to 9 are annular members that are fitted into both ends of the rotating shaft 5. The bearings 10 and 11 are members that rotatably support the rotating shaft 5, the bearing 10 is a deep groove ball bearing, and the bearing 11 is a cylindrical roller bearing. The bearings 10 and 11 include rolling elements 10a and 11a, cages 10b and 11b that hold the rolling elements 10a and 11a at equal intervals, outer rings 10c and 11c that rotate outside the cages 10b and 11b, The inner rings 10d and 11d rotate inside the cages 10b and 11b.
[0016]
2 is a plan view of the bearing lid according to the first embodiment of the present invention, FIG. 2 (A) is a plan view seen from the IIA direction of FIG. 1, and FIG. 2 (B) is IIB of FIG. 2 (C) is a plan view seen from the IIC direction in FIG. 1, and FIG. 2 (D) is a plan view seen from the IID direction in FIG. 3 is an external view of the bearing lid according to the first embodiment of the present invention, FIG. 3 (A) is a plan view, and FIG. 3 (B) is cut along line III-IIIB in FIG. 3 (A). It is sectional drawing which shows the state which carried out.
[0017]
The bearing lids 12 to 15 are members that are detachably attached to the end surfaces of the bearings 10 and 11, and are cast products or machined products made of aluminum or iron. The bearing lids 12 and 13 are end lids attached to the outside of the electric motor frame 1, and the bearing lids 14 and 15 are oil drains attached to the inner side of the electric motor frame 1. The bearing lid 12 is fixed to the bearing lid 14 with bolts so as to sandwich the bearing 10 with the bearing lid 14, and the bearing lid 13 is fixed to the bearing lid 15 with bolts so as to sandwich the bearing 11. As shown in FIGS. 2 (A) and 2 (D), the bearing lids 12 and 13 have substantially the same grease filling structure, and the bearing lids 14 and 15 are as shown in FIGS. 2 (B) and 2 (C). Both have substantially the same grease filling structure. Below, the bearing lids 12 and 14 side will be described, and the portions corresponding to the bearing lids 13 and 15 are denoted by the same reference numerals as those of the bearing lids 12 and 14 and detailed description thereof will be omitted.
[0018]
As shown in FIG. 3, the bearing lid 12 includes a filling chamber 12a and through holes 12b and 12c. The filling chamber 12a is a portion filled with grease for lubricating the bearing 10, and includes an annular filling chamber (first grease chamber) 12d, an outer filling chamber (second grease chamber) 12e, and a restraining portion 12f. . As shown in FIG. 3B, the filling chamber 12a has a quadrangular cross-sectional shape. Filling chamber 12a is formed such that binding moiety P 1 to P 6 for coupling the annular chamber filled 12d and the outer filling chamber 12e becomes the width W and depth D of approximately the same. The filling chamber 12a is formed, for example, so that the distance in the diameter direction and the depth direction is substantially the same from the contact portion S in contact with the bearing 10 on the inner peripheral surface of the annular filling chamber 12d shown in FIG.
[0019]
The annular filling chamber 12d is a portion formed along the gap (bearing opening) between the outer ring 10c and the inner ring 10d, and is formed in an annular shape so as to surround the through hole 12b as shown in FIG. It is a concave groove. The outer filling chamber 12e is an enlarged portion formed outside the annular filling chamber 12d, and is formed integrally with the annular filling chamber 12d. The outer filling chamber 12e is formed along the annular filling chamber 12d, and is a concave groove that is coupled to the annular filling chamber 12d at substantially the entire circumference except for a portion where the holding portion 12f is formed. As shown in FIGS. 1 and 3A, the outer diameter R 1 of the outer filling chamber 12e is formed larger than the outer diameter R 2 of the outer ring 10c. The annular filling chamber 12d and the outer filling chamber 12e have an opening 12g on the end face side of the bearing 10, as shown in FIG. The restraining part 12f is a part that restrains the end face of the outer ring 10c. Suppressing unit 12f, as shown in FIG. 3 (A), so as to define an outer filling chamber 12e into six areas A 1 to A 6, six at intervals in the circumferential direction of the outer filling chamber 12e formed Has been. The through hole 12 b is a fitting hole that fits with the outer peripheral portion of the collar 6 shown in FIG. 1, and the through hole 12 c is an insertion hole into which a bolt for fixing the bearing lid 12 to the bearing lid 14 is inserted.
[0020]
As shown in FIG. 2B, the bearing lid 14 includes an annular filling chamber 14a, a holding portion 14b, a through hole 14c, and the like. The annular filling chamber 14 a is a portion that is filled with grease for lubricating the bearing 10. The annular filling chamber 14a is a concave portion formed along the gap between the outer ring 10c and the inner ring 10d and formed in an annular shape so as to surround the through hole 14c. As shown in FIG. 1, the outer diameter R 3 of the annular filling chamber 14 a is formed larger than the inner diameter R 4 of the outer ring 10 c of the bearing 10. 2B is a portion that suppresses the end face of the outer ring 10c of the bearing 10, and the through hole 14c is a fitting hole that fits with the outer peripheral portion of the collar 7 shown in FIG.
[0021]
The bearing lid according to the first embodiment of the present invention has the effects described below.
(1) In the first embodiment, an outer filling chamber 12e is formed to expand outside the annular filling chamber 12d, and the outer filling chamber 12e is formed along the annular filling chamber 12d. The annular filling chamber 12d is coupled to the entire circumference of 12d. For this reason, compared with the conventional bearing lid 112 shown in FIG. 7, the amount of grease filled in the filling chamber 12a can be increased. Further, since the area where the outer filling chamber 12e and the annular filling chamber 12d are in contact with each other increases, the movement of the grease base oil becomes active and the total amount of grease in the filling chamber 12a can be used effectively. As a result, the lubrication life of the bearing 10 can be extended, and maintenance work and the like can be reduced because the replacement time of the grease is extended.
[0022]
(2) In the first embodiment, the annular filling chamber 12 d and the outer filling chamber 12 e have an opening 12 g on the end face side of the bearing 10. For this reason, the structure is simplified and the bearing lids 12 to 15 can be easily manufactured as compared with the case where an annular partition wall is formed on the bearing-side side surface of the filling chamber as in the conventional bearing lid. it can.
[0023]
(3) In the first embodiment, the outer diameter R 1 of the outer filling chamber 12e is formed larger than the outer diameter R 2 of the outer ring 10c, and the holding portion 12f that suppresses the end face of the outer ring 10c is provided as the filling chamber 12a. Have. Therefore, the amount of grease filled in the filling chamber 12a can be increased and the bearing 10 can be prevented from falling into the filling chamber 12a by the restraining portion 12f.
[0024]
(4) In the first embodiment, so as to define an outer filling chamber 12e into a plurality of regions A 1 to A 6, pressing section 12f is formed with a plurality at intervals in the circumferential direction of the outer filling chamber 12e Yes. For this reason, the grease filled in the outer filling chamber 12e can be positioned to prevent the grease from being displaced.
[0025]
(5) In the first embodiment, the coupling portions P 1 to P 6 where the annular filling chamber 12d and the outer filling chamber 12e are coupled are formed with substantially the same width W and depth D. As a result, the filling chamber 12a expands substantially equally without being displaced in either the diametrical direction or the depth direction, so that the movement of the grease base oil from the filling chamber 12a becomes active, thereby extending the life of the bearing 10. Can do.
[0026]
【Example】
Next, examples of the present invention will be described.
4 is an external view of a bearing lid according to an embodiment of the present invention, FIG. 4 (A) is an external view of a basic type, and FIG. 4 (B) is an external view of Embodiments 1 and 2, 4C is an external view of Examples 3 and 4, FIG. 4D is an external view of Examples 5 and 6, and FIG. 4E is an external view of Examples 7 and 8. FIG. . The basic filling chamber shown in FIG. 4A has the same structure as the filling chamber of the conventional bearing lid 112 shown in FIG.
In general, it is known that when the structure of the outer filling chamber 12e is different, the behavior of the enclosed grease is also different. Therefore, in order to investigate the relationship between the shape of the outer filling chamber 12e and the ease of movement of the base oil of the grease filled in the outer filling chamber 12e, it is made of aluminum in accordance with a small test bearing (ball bearing 6206). A small bearing lid model (Examples 1 to 8) was designed and manufactured. However, these Example 1 to Example 8 are not provided with a restraining part corresponding to the restraining part 112f shown in FIG.
[0027]
(Examples 1 and 2)
In the first and second embodiments, the coupling angle of the outer filling chamber 12e with respect to the annular filling chamber 12d is changed. The first embodiment is an embodiment in which the outer filling chamber 12e is coupled to the outer peripheral portion tangent to the annular filling chamber 12d. In the second embodiment, the outer filling chamber 12e is horizontally coupled to the outer circumferential portion of the annular filling chamber 12d. This is an example.
[0028]
(Examples 3 and 4)
Examples 3 and 4 are examples in which the number of oil passages leading from the outer filling chamber 12e to the annular filling chamber 12d is changed, and in Example 3, the number of oil passages is two on each side (four in total). Example 4 is an example in which the number of oil passages is one on one side.
[0029]
(Examples 5 and 6)
Examples 5 and 6 are examples in which the width in the diameter direction of the outer filling chamber 12e is changed, and Example 5 is an example in which the width of the outer filling chamber 12e is halved. Is an embodiment in which the width of the outer filling chamber 12e is doubled.
[0030]
(Examples 7 and 8)
Examples 7 and 8 are examples in which the direction of the outer filling chamber 12e is changed. Example 7 is an example in which the outer filling chamber 12e faces upward, and Example 8 has the outer filling chamber 12e facing downward. This is an example.
[0031]
In Examples 1 to 8, the volume and shape of the annular filling chamber 12d are the same, but only the shape of the outer filling chamber 12e is changed with the same volume. 4 (B) to 4 (E), an embodiment considered to be superior to the basic type bearing cover shown in FIG. 4 (A) from the viewpoint of ease of movement of the grease base oil is shown in the upper stage. What is considered inferior is shown below.
[0032]
Next, a grease base oil behavior test was conducted using grease with a tracer, and the influence of the shape of the outer filling chamber 12e was examined. First, the current grease (consistency 2) is sealed in the annular filling chamber 12d of the first to eighth embodiments, the outer filling chamber 12e is filled with the current grease mixed with the tracer, and the opening 12g is in contact with the ground. A standing test was conducted for 100 hours at a temperature of 100 ° C. Then, in order to evaluate how much the grease base oil containing the tracer in the outer filling chamber 12e has moved into the annular filling chamber 12d, the tracer is used at eight measurement points on the annular filling chamber 12d as shown in FIG. The concentration was analyzed. In Examples 7 and 8, measurements were made with the directions aligned when measuring the tracer concentration.
[0033]
FIG. 5 is a graph showing the measurement result of the tracer concentration of the bearing lid according to the embodiment of the present invention, FIG. 5 (A) is the measurement result of Embodiments 1 and 2, and FIG. 5 (B) is the embodiment. FIG. 5 (C) shows the measurement results of Examples 5 and 6, and FIG. 5 (D) shows the measurement results of Examples 4, 7, and 8.
In Examples 1 and 2, as shown in FIG. 5A, no significant change was observed in the tracer concentration distribution in the entire annular filling chamber 12d. Regarding Example 1, although the movement of the grease base oil seems to be slightly better than the basic type, the difference from the basic type was small. In Examples 3 and 4, as shown in FIG. 5B, a change in the tracer concentration distribution is partially observed in the portion closer to the outer filling chamber 12e compared to the basic type, but in the entire annular filling chamber 12d. There was no significant change in the tracer concentration distribution. In Examples 5 and 6, as shown in FIG. 5C, a large change was observed in the grease concentration distribution. In the fifth embodiment, since the portion where the outer filling chamber 12e is in contact with the annular filling chamber 12d is large, the tracer concentration distribution changes on average in the entire annular filling chamber 12d. On the other hand, in Example 6, the change in the tracer concentration distribution was small at portions other than the two points (0 °, 180 °) closest to the annular filling chamber 12d. In Examples 7 and 8, as shown in FIG. 5D, the grease base oil was actively moved in the order of Example 7 (upward), Example 4 (laterally), and Example 8 (downward). However, no significant difference was observed in the grease concentration distribution in the entire annular filling chamber 12d.
[0034]
As a result, the grease base oil is actively moving between the outer filling chamber 12e and the annular filling chamber 12d from the beginning of the filling, and the grease base oil increases as the area where the outer filling chamber 12e and the annular filling chamber 12d come into contact with each other. It was confirmed that the degree to which the oil moved increased. For this reason, the outer filling chamber 12e and the annular filling chamber 12d are joined to each other in the widest possible area as in the bearing lid 12 shown in FIG. 3 rather than the outer filling chamber 12e and the annular filling chamber 12d are partially joined. Is considered desirable. In this case, it is considered that the movement of the grease base oil becomes more active as the total central angle of the joint portion between the outer filling chamber 12e and the annular filling chamber 12d is closer to the entire circumference. In the conventional bearing lid, the outer diameter of the filling chamber is the same or smaller than the inner diameter of the outer ring of the bearing in part or all of the filling chamber, but the inner diameter R 4 of the outer ring 10c. From the measurement results of Example 5, it was confirmed that the grease base oil sufficiently moved even when the outer diameter R 1 of the outer filling chamber 12e was larger. Furthermore, conventionally, it was considered that the grease base oil easily moved in the direction of gravity, but it was confirmed from the measurement results of Examples 7 and 8 that the influence of gravity on the movement of the grease base oil was small.
[0035]
(Second Embodiment)
6 is an external view of a bearing lid according to a second embodiment of the present invention, FIG. 6 (A) is a plan view, and FIG. 6 (B) is cut along the line VI-VIB in FIG. 6 (A). It is sectional drawing which shows the state which carried out. In FIG. 6, the same parts as those shown in FIG. 3 are denoted by the same reference numerals and detailed description thereof is omitted.
In the second embodiment, six restraining portions 12f are formed along the boundary L between the annular filling chamber 12d and the outer filling chamber 12e at intervals in the circumferential direction of the outer filling chamber 12e. In the second embodiment, the holding portion 12f is separated from the outer peripheral portion of the outer filling chamber 12e and formed in a thin plate shape, so that more grease is filled in the outer filling chamber 12e than in the first embodiment. can do. Further, the restraining portion 12f prevents the grease from dropping from the outer filling chamber 12e side into the annular filling chamber 12d.
[0036]
(Other embodiments)
The present invention is not limited to the embodiment described above, and various modifications or changes can be made as described below, and these are also within the scope of the present invention.
(1) In this embodiment, the bearings 10 and 11 that support the rotating shaft 5 of the main motor of the railway vehicle have been described as examples. However, the present invention is not limited to this, and the present invention can be applied to general bearings. . In this embodiment, the grease filling structure on the bearing lids 12 and 13 side has been described as an example, but the present invention can also be applied to the bearing lids 14 and 15 side. Further, in this embodiment, has been described as an example a case where the width W and the depth D of the coupling portion P 1 to P 6 of the annular injection chamber 12d and the outer filling chamber 12e in the same, structural restrictions If you do not receive one, you can enlarge either one.
[0037]
(2) In this embodiment, the case where the filling chamber 12a has a quadrangular cross-sectional shape has been described as an example, but the cross-sectional shape may be formed in a U shape or a semicircular shape. Further, in this embodiment, the annular filling chamber 12d and the outer filling chamber 12e are connected as much as possible around the circumference. However, when the two are separated due to structural restrictions, a passage for connecting them is provided. It is preferable to form and make the cross-sectional area of this passage as large as possible.
[0038]
【The invention's effect】
As described above, according to the present invention, the lubrication life can be extended by effectively using the grease in the filling chamber.
[Brief description of the drawings]
FIG. 1 is a cross-sectional view of an electric motor frame including a bearing lid according to a first embodiment of the present invention.
2 is a plan view of the bearing lid according to the first embodiment of the present invention, (A) is a plan view seen from the IIA direction of FIG. 1, and (B) is seen from the IIB direction of FIG. It is a top view, (C) is the top view seen from the IIC direction of FIG. 1, (D) is the top view seen from the IID direction of FIG.
FIGS. 3A and 3B are external views of the bearing lid according to the first embodiment of the present invention, in which FIG. 3A is a plan view and FIG. 3B is a cross-sectional view showing a state cut along line III-IIIB in FIG. It is.
4A and 4B are external views of a bearing lid according to an embodiment of the present invention, in which FIG. 4A is an external view of a basic type, FIG. 4B is an external view of Embodiments 1 and 2, and FIG. It is an external view of Example 3, 4, (D) is an external view of Example 5, 6, (E) is an external view of Example 7,8.
FIG. 5 is a graph showing the measurement results of the tracer concentration of a bearing lid according to an embodiment of the present invention, (A) is the measurement results of Examples 1 and 2, and (B) is the measurement results of Examples 3 and 4. It is a measurement result, (C) is a measurement result of Examples 5 and 6, and (D) is a measurement result of Examples 4, 7, and 8.
6A and 6B are external views of a bearing lid according to a second embodiment of the present invention, in which FIG. 6A is a plan view and FIG. 6B is a cross-sectional view showing a state cut along line VI-VIB in FIG. It is.
7A and 7B are external views of a conventional bearing lid, in which FIG. 7A is a plan view and FIG. 7B is a cross-sectional view showing a state cut along line VII-VIIB in FIG.
[Explanation of symbols]
1 motor frame 10 and 11 bearing 10c, 11c outer ring 10d, the 11d inner ring 12-15 bearing cap 12a filled chamber 12d annular filling chamber 12e outer filling chamber 12f suppressing portion 12g openings R 1 outer filling chamber of the outer diameter R 2 outer ring the inner diameter a 1 to a 6 regions P 1 to P 6 binding portion W width D depth L boundary of the outer diameter R 4 outer ring having an outer diameter R 3 cyclic filling chamber

Claims (3)

軸受の外輪と内輪との間の間隙部に沿って形成された環状充填室と、
前記環状充填室の外側に拡大して形成された外側充填室と、
前記外輪の端面を抑える抑え部とを有し、
前記軸受を潤滑するためのグリースを充填する充填室を備えるグリース充填構造において、
前記環状充填室及び前記外側充填室は、前記軸受の端面側に開口部を有し、
前記外側充填室は、前記環状充填室に沿って形成されており、この環状充填室の略全周でこの環状充填室と結合し、かつ、この環状充填室の略全周で外側に拡大して形成されており、
前記外側充填室の外径は、前記外輪の外径よりも大きく形成されており、
前記抑え部は、前記外側充填室を複数の領域に区画するように、この外側充填室の周方向に間隔をあけて複数形成されていること、
を特徴とするグリース充填構造。An annular filling chamber formed along the gap between the outer ring and the inner ring of the bearing;
An outer filling chamber formed outside the annular filling chamber;
A holding portion that holds down the end face of the outer ring,
In a grease filling structure comprising a filling chamber filled with grease for lubricating the bearing,
The annular filling chamber and the outer filling chamber have an opening on the end face side of the bearing,
The outer filling chamber is formed along the annular filling chamber. The outer filling chamber is connected to the annular filling chamber on substantially the entire circumference of the annular filling chamber, and expands outward on substantially the entire circumference of the annular filling chamber. Formed,
The outer diameter of the outer filling chamber is larger than the outer diameter of the outer ring,
A plurality of the restraining portions are formed at intervals in the circumferential direction of the outer filling chamber so as to divide the outer filling chamber into a plurality of regions;
Grease filling structure characterized by 請求項１に記載のグリース充填構造において、
前記充填室は、前記環状充填室と前記外側充填室とが結合する結合部分が略同一の幅と深さで形成されていること、
を特徴とするグリース充填構造。The grease filling structure according to claim 1,
In the filling chamber, the coupling portion where the annular filling chamber and the outer filling chamber are joined is formed with substantially the same width and depth,
Grease filling structure characterized by 軸受の端面に着脱自在に装着される軸受蓋であって、
請求項１又は請求項２に記載のグリース充填構造を備えること、
を特徴とする軸受蓋。A bearing lid that is detachably attached to the end face of the bearing,
Comprising the grease filling structure according to claim 1 or 2 ,
Bearing lid characterized by.
JP2002286276A 2002-09-30 2002-09-30 Grease filling structure and bearing lid Expired - Fee Related JP4173342B2 (en)

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103026593A (en) * 2010-10-06 2013-04-03 三菱电机株式会社 Rotary electrical device, bearing attachment and detachment tool, and bearing replacement method

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPWO2012164726A1 (en) 2011-06-02 2014-07-31 三菱電機株式会社 Rotating electrical machine and bearing replacement method

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103026593A (en) * 2010-10-06 2013-04-03 三菱电机株式会社 Rotary electrical device, bearing attachment and detachment tool, and bearing replacement method
CN103026593B (en) * 2010-10-06 2015-06-17 三菱电机株式会社 Rotary electrical device, bearing attachment and detachment tool, and bearing replacement method

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