JP2003172366A - Rolling bearing - Google Patents
Rolling bearingInfo
- Publication number
- JP2003172366A JP2003172366A JP2001373003A JP2001373003A JP2003172366A JP 2003172366 A JP2003172366 A JP 2003172366A JP 2001373003 A JP2001373003 A JP 2001373003A JP 2001373003 A JP2001373003 A JP 2001373003A JP 2003172366 A JP2003172366 A JP 2003172366A
- Authority
- JP
- Japan
- Prior art keywords
- rolling bearing
- cage
- impellers
- rolling
- ring
- 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.)
- Withdrawn
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
- F16C33/66—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
- 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
- F16C33/41—Ball cages comb-shaped
- F16C33/412—Massive or moulded comb cages, e.g. snap ball cages
- F16C33/414—Massive or moulded comb cages, e.g. snap ball cages formed as one-piece cages, i.e. monoblock comb cages
- F16C33/416—Massive or moulded comb cages, e.g. snap ball cages formed as one-piece cages, i.e. monoblock comb cages made from plastic, e.g. injection moulded comb cages
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
- F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
- F16C19/16—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls
- F16C19/163—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls with angular contact
- F16C19/166—Four-point-contact ball bearings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
- F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
- F16C19/18—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls
- F16C19/181—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact
- F16C19/183—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles
- F16C19/184—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement
-
- 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
- F16C2361/00—Apparatus or articles in engineering in general
- F16C2361/43—Clutches, e.g. disengaging bearing
-
- 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
- F16C41/00—Other accessories, e.g. devices integrated in the bearing not relating to the bearing function as such
- F16C41/008—Identification means, e.g. markings, RFID-tags; Data transfer means
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Rolling Contact Bearings (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、グリース封入型等
の転がり軸受に係り、詳しくは潤滑性能や耐久性を向上
させる技術に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rolling bearing such as a grease-filled type, and more particularly to a technique for improving lubrication performance and durability.
【０００２】[0002]
【従来の技術】自動車のエンジンには、オルタネータや
クーラコンプレッサ、ウォータポンプ等、種々の補機が
付設されている。通常、これら補機はマルチグルーブベ
ルト（多溝付ベルト）やＶベルト等を介してクランクシ
ャフトに駆動されており、ベルトが巻掛けられるプーリ
はメンテナンス性に優れたグリース封入式の転がり軸受
により支持されている。グリース封入式の転がり軸受
は、転がり軸受に規定量のグリースを注入した上でシー
ルやシールドにより軸封を行ったもので、軸受形式とし
ては単列深溝型や３，４点接触型、複列ラジアル型等が
採用されている。2. Description of the Related Art Various auxiliary machines such as an alternator, a cooler compressor and a water pump are attached to an engine of a vehicle. Usually, these accessories are driven by the crankshaft via a multi-groove belt (belt with multiple grooves) or a V-belt, and the pulley around which the belt is wound is supported by a grease-filled rolling bearing with excellent maintainability. Has been done. The grease-filled rolling bearing is a rolling bearing in which a specified amount of grease is injected and then the shaft is sealed by a seal or shield. Bearing types are single row deep groove type, 3, 4-point contact type, double row Radial type is used.
【０００３】[0003]
【発明が解決しようとする課題】上述したグリース封入
式の転がり軸受には、次に述べる問題があった。周知の
ように、転がり軸受の耐久性（実用寿命）を左右する要
素として内外軌道面と転動体との間の潤滑状態が挙げら
れるが、製造時に軸受内に封入されたグリースの一部が
潤滑に供されず、潤滑が必ずしも円滑に行われないこと
があった。本発明者等は、ベンチテストや実車走行試験
に供されたグリース封入式の転がり軸受を多数分解した
が、転動体と保持器に接触する部位のグリースにより潤
滑が専ら行われ、シールやシールドの壁面に付着したグ
リースは封入時の状態を保っているものが多かった。特
に、冠型の合成樹脂製保持器が採用されたものでは、爪
側のシールの壁面に比較的多量のグリースが付着してい
る事例が多かった。The grease-filled type rolling bearing described above has the following problems. As is well known, the lubrication condition between the inner and outer raceways and the rolling elements is one of the factors that affect the durability (practical life) of rolling bearings, but some of the grease filled in the bearing during manufacturing is lubricated. Therefore, lubrication may not always be performed smoothly. The present inventors disassembled many grease-filled type rolling bearings used in bench tests and actual vehicle running tests.However, lubrication is exclusively performed by the grease in the parts that come into contact with the rolling elements and the cage, and seals and shields In many cases, the grease that adhered to the wall surface maintained the state in which it was sealed. In particular, in the case where the crown type cage made of synthetic resin is adopted, there are many cases in which a relatively large amount of grease adheres to the wall surface of the claw-side seal.
【０００４】このような場合、限られた量のグリースの
みが持続的に機械的負荷（剪断等）や熱的負荷を受ける
ため、劣化によって比較的早期にグリースの潤滑性能が
低下し、転動体と保持器の転道面が摩耗・損傷する虞が
ある。近年、自動車の室内空間の容量増大やエンジンル
ームの狭隘化等から、クーラコンプレッサは、高速運転
化や大容量化が求められる一方、各構成部材の軸方向寸
法が小さくされる傾向もある。そのため、クーラコンプ
レッサのプーリを支持するグリース封入式の転がり軸受
では、転道体や軌道面の発熱が非常に大きくなり、上述
した摩耗・損傷が無視し得ない問題となっていた。本発
明は、上記状況に鑑みなされたもので、潤滑性能や耐久
性を向上させた転がり軸受を提供することを目的とす
る。In such a case, since only a limited amount of grease is continuously subjected to mechanical load (shearing etc.) or thermal load, deterioration of grease lubrication performance occurs relatively early due to deterioration, and the rolling element And the rolling surface of the cage may be worn or damaged. In recent years, due to the increase in the capacity of the interior space of automobiles and the narrowing of the engine room, the cooler compressor is required to operate at high speed and have a large capacity, while the axial dimension of each component tends to be reduced. Therefore, in the grease-filled type rolling bearing that supports the pulley of the cooler compressor, heat generation on the rolling elements and the raceway surface becomes extremely large, and the above-mentioned wear and damage have become a problem that cannot be ignored. The present invention has been made in view of the above circumstances, and an object of the present invention is to provide a rolling bearing having improved lubrication performance and durability.
【０００５】[0005]
【課題を解決するための手段】そこで、本発明では、上
記課題を解決するため、外周側に内軌道面を有する内輪
と、内周側に外軌道面を有する外輪と、前記内輪と前記
外輪との間に介装され、前記内軌道面と前記外軌道面と
に転接する多数の転動体と、これら転動体の保持に供さ
れる円環状の保持器とを備えた転がり軸受であって、前
記保持器の少なくとも一方の端面には、前記内輪と前記
外輪との間に貯留された潤滑剤を循環させるべく、略放
射状に配置された多数のインペラまたは溝が設けられた
ものを提案する。In order to solve the above problems, therefore, in the present invention, an inner ring having an inner raceway surface on the outer peripheral side, an outer ring having an outer raceway surface on the inner circumferential side, the inner ring and the outer ring. A rolling bearing provided between the inner raceway surface and the outer raceway surface, which is interposed between the rolling elements, and an annular retainer used to hold these rolling elements. It is proposed that at least one end surface of the cage is provided with a large number of impellers or grooves arranged substantially in a radial pattern in order to circulate the lubricant stored between the inner ring and the outer ring. .
【０００６】本発明によれば、内輪または外輪の回転に
伴って保持器が回転すると、内輪側の潤滑剤は、インペ
ラにより外輪側に送出され、外輪側の潤滑剤と入れ代わ
ることになる。これにより、転がり軸受内で潤滑剤が循
環することになり、比較的大量の潤滑剤が転動体や内外
輪の潤滑に供されることになる。According to the present invention, when the cage rotates with the rotation of the inner ring or the outer ring, the lubricant on the inner ring side is sent to the outer ring side by the impeller and replaces the lubricant on the outer ring side. As a result, the lubricant circulates in the rolling bearing, and a relatively large amount of lubricant is used to lubricate the rolling elements and the inner and outer races.
【０００７】[0007]
【発明の実施の形態】以下、本発明の実施形態を図面に
基づき詳細に説明する。図１は本発明の第１実施形態に
係る転がり軸受の半裁縦断面図であり、図２は保持器の
正面図であり、図３は図２中のＡ−Ａ断面図であり、図
４は図３中のＢ矢視図である。BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of the present invention will be described in detail below with reference to the drawings. FIG. 1 is a semi-cut vertical sectional view of a rolling bearing according to a first embodiment of the present invention, FIG. 2 is a front view of a cage, FIG. 3 is a sectional view taken along line AA in FIG. FIG. 4 is a view on arrow B in FIG. 3.
【０００８】本実施形態は、本発明をグリース封入式の
４点接触玉軸受（以下、単に転がり軸受と記す）１に適
用したものであり、図１に示したように、外周側に内軌
道面３を有する内輪５と、内周側に外軌道面７を有する
外輪９と、内輪５外輪９との間に介装され、内軌道面３
と外軌道面７とに転接する多数（本実施形態では、９
個）の鋼球１１と、これら鋼球１１の保持に供される円
環状の保持器１３と、外輪９の両端部に取り付けられた
一対の弾性シール１５，１７と、内輪５と外輪９との間
に封入されたグリース１９とから構成されている。In this embodiment, the present invention is applied to a grease-filled type four-point contact ball bearing (hereinafter, simply referred to as a rolling bearing) 1, and as shown in FIG. The inner race 5 having the surface 3, the outer race 9 having the outer raceway surface 7 on the inner peripheral side, and the inner race 5 are interposed between the outer race 9 and the inner raceway 3
And the outer raceway surface 7 (in this embodiment, 9
Individual) steel balls 11, an annular cage 13 used for holding these steel balls 11, a pair of elastic seals 15 and 17 attached to both ends of the outer ring 9, an inner ring 5 and an outer ring 9. It is composed of grease 19 enclosed between the two.
【０００９】保持器１３は、合成樹脂を素材としたいわ
ゆる冠型であり、図２〜図４に示したように、リング部
２１と、リング部２１から図１，図３中左方に突設され
た９カ所の爪部２３とを有しており、隣り合う爪部２３
の間の空間が鋼球１１が嵌入・保持されるポケット２５
となっている。The retainer 13 is a so-called crown type made of synthetic resin, and as shown in FIGS. 2 to 4, the retainer 13 projects from the ring portion 21 and the ring portion 21 to the left in FIGS. 1 and 3. And the adjacent claw portions 23.
The space between is the pocket 25 into which the steel ball 11 is inserted and held.
Has become.
【００１０】第１実施形態の場合、爪部２３の先端から
は翼状断面の９枚の第１インペラ３１が突設され、リン
グ部２１の後端からも翼状断面の９枚の第２インペラ３
３が突設されている。第１，第２インペラ３１，３３
は、保持器１３の中心から各爪部２３の中心を通過する
放射線Ｌｒに略沿って配置されている。尚、両インペラ
３１，３３と弾性シール１５，１７との間隔ｔ１，ｔ２
は、鋼球１１の直径をＤとした場合、各構成要素の隙間
や寸法公差を考慮しても０．０３Ｄ以上となるように設
定されている。In the case of the first embodiment, nine first impellers 31 having a wing-shaped cross section are projected from the tip of the claw portion 23, and nine second impellers 3 having a wing-shaped cross section are also provided from the rear end of the ring portion 21.
3 is projected. First and second impellers 31, 33
Are arranged substantially along the radiation Lr passing from the center of the holder 13 to the center of each claw portion 23. In addition, the intervals t1 and t2 between the impellers 31 and 33 and the elastic seals 15 and 17, respectively.
Is set to be 0.03D or more when the diameter of the steel ball 11 is D and the gaps and dimensional tolerances of each component are taken into consideration.
【００１１】本実施形態では、転がり軸受１の回転に伴
って、保持器１３は、両インペラ３１，３３がグリース
１９をすくい上げるべく、図２，図４に示した方向に回
転する。すなわち、転がり軸受１は回転方向が規定され
ているのであるが、組み付け時における指示手段とし
て、両弾性シール１５，１７に異なる色（例えば、黒と
赤と）が使用されている。尚、指示手段としては、この
他に、内輪５や外輪９の端面に切欠きや刻印、電食ある
いは腐食による印等を設けるようにしてもよい。In this embodiment, with the rotation of the rolling bearing 1, the cage 13 rotates in the directions shown in FIGS. 2 and 4 so that the impellers 31 and 33 scoop up the grease 19. That is, although the rolling direction of the rolling bearing 1 is defined, different colors (for example, black and red) are used for both elastic seals 15 and 17 as an instruction means at the time of assembly. Other than this, as the indicating means, a notch, a marking, a mark due to electrolytic corrosion or corrosion, or the like may be provided on the end surfaces of the inner ring 5 and the outer ring 9.
【００１２】以下、第１実施形態の作用を述べる。転が
り軸受１が装置に取り付けられ、外輪９または内輪５が
回転を始めると、図２，図４に示したように、保持器１
３も回転する。すると、両インペラ３１，３３にすくい
上げられた内輪５側のグリース１９は、図３に示したよ
うに外輪９側に搬出されて該部のグリース１９と入れ代
わった後、両インペラ３１，３３と弾性シール１５，１
７との隙間や鋼球１１と保持器１３との隙間等から内輪
５側に還流する。The operation of the first embodiment will be described below. When the rolling bearing 1 is attached to the device and the outer ring 9 or the inner ring 5 starts to rotate, as shown in FIGS. 2 and 4, the cage 1
3 also rotates. Then, the grease 19 on the inner ring 5 side scooped up by both impellers 31 and 33 is carried out to the outer ring 9 side and replaced with the grease 19 on the inner ring 5 side as shown in FIG. Elastic seal 15,1
It recirculates to the inner ring 5 side through a gap between the inner ring 5 and the gap between the steel ball 11 and the cage 13.
【００１３】これにより、転がり軸受１内では、グリー
ス１９の循環が実現され、封入されたグリース１９の殆
ど全量が潤滑に供されることになる。その結果、従来装
置で問題となっていた、潤滑不良に起因する内外軌道面
３，７と鋼球１１との間の損傷や異常発熱が抑制され、
転がり軸受１の耐久性が大幅に向上した。この際、両イ
ンペラ３１，３３と弾性シール１５，１７との間隔ｔ
１，ｔ２が鋼球１１の直径をＤとして０．０３Ｄ以上と
なるように設定されているため、インペラ３１，３３と
弾性シール１５，１７との間からグリース１９が円滑に
還流する。As a result, the grease 19 is circulated in the rolling bearing 1, and almost all of the enclosed grease 19 is used for lubrication. As a result, damage and abnormal heat generation between the inner and outer raceway surfaces 3, 7 and the steel ball 11 due to poor lubrication, which are problems in the conventional device, are suppressed.
The durability of the rolling bearing 1 is significantly improved. At this time, the distance t between the impellers 31 and 33 and the elastic seals 15 and 17 is t.
Since 1 and t2 are set to be 0.03D or more with the diameter of the steel ball 11 being D, the grease 19 smoothly flows back between the impellers 31 and 33 and the elastic seals 15 and 17.
【００１４】図５（ａ）〜（ｈ）には、下方を内輪５側
として、保持器１３に形成されるインペラ３１，３３の
断面形状の例を示してある。これらの図に示したよう
に、インペラ３１，３３は、放射線Ｌｒに沿った直線的
なものであってもよいし、放射線Ｌｒに略沿った傾斜状
あるいは円弧状のものであってもよく、転がり軸受１の
使用形態や製造上の理由等により適宜選択可能である。FIGS. 5A to 5H show examples of the cross-sectional shapes of the impellers 31 and 33 formed in the retainer 13 with the lower side being the inner ring 5 side. As shown in these drawings, the impellers 31 and 33 may be linear along the radiation Lr, or may be inclined or arcuate along the radiation Lr, The rolling bearing 1 can be appropriately selected depending on the usage pattern, manufacturing reasons, and the like.
【００１５】一方、図６（ａ）〜（ｈ）には、インペラ
３３に代えて、保持器１３のリング部２１の端面に形成
される溝３５の例を示している。溝３５は、保持器１３
の回転に伴って、インペラ３１，３３と同様に、グリー
ス１９を内輪５側から外輪９側に移送する。これらの図
に示したように、溝３５についても、放射線Ｌｒに沿っ
た直線的なものであってもよいし、放射線Ｌｒに略沿っ
た傾斜状あるいは円弧状のものであってもよく、転がり
軸受１の使用形態や製造上の理由等により適宜選択可能
である。On the other hand, FIGS. 6A to 6H show an example of the groove 35 formed on the end surface of the ring portion 21 of the retainer 13 in place of the impeller 33. The groove 35 is used for the cage 13.
As the impellers 31 and 33 rotate, the grease 19 is transferred from the inner ring 5 side to the outer ring 9 side. As shown in these drawings, the groove 35 may be linear along the radiation Lr, or may be inclined or arcuate substantially along the radiation Lr, and may be rolled. The bearing 1 can be appropriately selected depending on the usage pattern and manufacturing reasons.
【００１６】図７には、本発明の第２実施形態に係る転
がり軸受を示す半裁縦断面図である。本実施形態は、本
発明をグリース封入式の複列アンギュラ玉軸受（以下、
単に転がり軸受と記す）３７に適用したものであり、第
１実施形態と同様に、鋼球１１を保持する２つの保持器
１３には第１，第２インペラ３１，３３が形成され、こ
れらインペラ３１，３３の作用により転がり軸受３７内
でグリース１９が循環するようになっている。FIG. 7 is a semi-cut vertical sectional view showing a rolling bearing according to a second embodiment of the present invention. In this embodiment, the present invention is a grease-filled double-row angular contact ball bearing (hereinafter,
The first and second impellers 31 and 33 are formed in the two cages 13 for holding the steel balls 11 as in the first embodiment. By the action of 31, 33, the grease 19 circulates in the rolling bearing 37.
【００１７】図８には、本発明の第３実施形態に係るエ
ンジン補機を示す要部半裁縦断面図である。本実施形態
のエンジン補機は電磁クラッチ付のクーラコンプレッサ
４１であり、コンプレッサボディ４３とプーリ４５との
間に第１実施形態の転がり軸受１が介装されている。コ
ンプレッサシャフト４７の先端には板ばね４９を介して
フェライト系の環状板５１が取り付けられる一方、コン
プレッサボディ４３には電気式のクラッチマグネット５
３が固着されている。そして、クラッチマグネット５３
が励磁されると、多溝付ベルト５５を介してクランクシ
ャフト（図示せず）に回転駆動されるプーリ４５に環状
板５１が磁力吸着され、環状板５１と伴にコンプレッサ
シャフト４７が回転する。FIG. 8 is a half-cut longitudinal sectional view of essential parts showing an engine accessory according to a third embodiment of the present invention. The engine accessory of this embodiment is a cooler compressor 41 with an electromagnetic clutch, and the rolling bearing 1 of the first embodiment is interposed between a compressor body 43 and a pulley 45. A ferrite-based annular plate 51 is attached to the tip of the compressor shaft 47 via a plate spring 49, while an electric clutch magnet 5 is attached to the compressor body 43.
3 is fixed. And the clutch magnet 53
Is excited, the annular plate 51 is magnetically attracted to the pulley 45 that is rotationally driven by the crankshaft (not shown) via the multi-grooved belt 55, and the compressor shaft 47 rotates together with the annular plate 51.
【００１８】図９には、本発明の第４実施形態に係るエ
ンジン補機を示す要部半裁縦断面図である。本実施形態
のエンジン補機もクーラコンプレッサ４１であり、コン
プレッサボディ４３とプーリ４５との間に第１実施形態
の転がり軸受１が介装されている。コンプレッサシャフ
ト４７の先端にはトルクリミット機能付のプーリ４５が
ダンパ６１を介して締結されており、エンジンの運転時
にクーラコンプレッサ４１が駆動されるFIG. 9 is a half-cut longitudinal sectional view of essential parts showing an engine accessory according to a fourth embodiment of the present invention. The engine accessory of the present embodiment is also the cooler compressor 41, and the rolling bearing 1 of the first embodiment is interposed between the compressor body 43 and the pulley 45. A pulley 45 having a torque limit function is fastened to the tip of the compressor shaft 47 via a damper 61, and the cooler compressor 41 is driven during engine operation.
【００１９】図１０には、本発明の第５実施形態に係る
エンジン補機を示す要部半裁縦断面図である。本実施形
態のエンジン補機は第３実施形態と同様のクーラコンプ
レッサ４１であるが、コンプレッサボディ４３とプーリ
４５との間に第２実施形態の転がり軸受３７が介装され
ている。FIG. 10 is a half-cut longitudinal sectional view of an essential part showing an engine accessory according to a fifth embodiment of the present invention. The engine accessory of this embodiment is the cooler compressor 41 similar to that of the third embodiment, but the rolling bearing 37 of the second embodiment is interposed between the compressor body 43 and the pulley 45.
【００２０】図１１には、本発明の第６実施形態に係る
エンジン補機を示す要部半裁縦断面図である。本実施形
態のエンジン補機は第４実施形態と同様のクーラコンプ
レッサ４１であるが、コンプレッサボディ４３とプーリ
４５との間に第２実施形態の転がり軸受３７が介装され
ている。FIG. 11 is a half-cut longitudinal sectional view of an essential part showing an engine accessory according to a sixth embodiment of the present invention. The engine accessory of this embodiment is the same cooler compressor 41 as in the fourth embodiment, but the rolling bearing 37 of the second embodiment is interposed between the compressor body 43 and the pulley 45.
【００２１】図１２には、本発明の第７実施形態に係る
プーリを示す縦断面図である。本実施形態のプーリ４５
は、アイドラ用またはテンショナ用として用いられる鋼
板プレス成型品であり、その軸受保持部６３に第１実施
形態の転がり軸受１が内嵌・圧入されている。FIG. 12 is a vertical sectional view showing a pulley according to the seventh embodiment of the present invention. Pulley 45 of this embodiment
Is a steel plate press-molded product used for an idler or a tensioner, and the rolling bearing 1 of the first embodiment is internally fitted and press-fitted into the bearing holding portion 63 thereof.
【００２２】以上で具体的実施形態の説明を終えるが、
本発明の態様はこれら実施形態に限られるものではな
い。例えば、上記実施形態は、本発明をグリース封入式
の４点接触玉軸受や複列アンギュラ玉軸受に適用したも
のであるが、単列または複列の深溝玉軸受や複列円錐こ
ろ軸受等、種々の転がり軸受に適用可能であるし、弾性
シールに代えて鋼板製のシールドを有する転がり軸受
や、プランマブロック等に収納される開放型の転がり軸
受にも適用可能である。また、保持器としては、実施形
態で挙げた合成樹脂成型品の他、黄銅や鋼等を素材とす
るもみ抜き保持器やプレス成形保持器も選択可能であ
る。また、本発明の転がり軸受は、上述したクーラコン
プレッサの他、オルタネータやエアコンプレッサ、スー
パチャージャ等、種々のエンジン補機に採用可能である
し、エンジン補機以外の一般的な装置、機器に採用可能
である。更に、インペラや溝の形状や構成等について
も、上記実施形態に限られるものではなく、設計上の都
合等により適宜変更可能である。The description of the specific embodiment is finished above.
Aspects of the invention are not limited to these embodiments. For example, the above-described embodiment is one in which the present invention is applied to a grease-filled four-point contact ball bearing or a double-row angular contact ball bearing, but a single-row or double-row deep groove ball bearing or a double-row tapered roller bearing, The present invention can be applied to various rolling bearings, a rolling bearing having a shield made of a steel plate in place of the elastic seal, and an open type rolling bearing housed in a plummer block or the like. Further, as the cage, in addition to the synthetic resin moldings mentioned in the embodiments, a machined cage or a press-molded cage made of brass, steel or the like can be selected. In addition to the cooler compressor described above, the rolling bearing of the present invention can be used in various engine accessories such as alternators, air compressors, superchargers, etc., and is also used in general devices and equipment other than engine accessories. It is possible. Further, the shapes and configurations of the impeller and the groove are not limited to those in the above embodiment, and can be changed as appropriate for the convenience of design.
【００２３】[0023]
【発明の効果】以上の説明から明らかなように、本発明
の転がり軸受によれば、外周側に内軌道面を有する内輪
と、内周側に外軌道面を有する外輪と、前記内輪と前記
外輪との間に介装され、前記内軌道面と前記外軌道面と
に転接する多数の転動体と、これら転動体の保持に供さ
れる円環状の保持器とを備えた転がり軸受であって、前
記保持器の少なくとも一方の端面には、前記内輪と前記
外輪との間に貯留された潤滑剤を循環させるべく、略放
射状に配置された多数のインペラまたは溝が設けられた
ものとしたため、内輪または外輪の回転に伴って保持器
が回転すると、内輪側の潤滑剤がインペラにより外輪側
に送出されて外輪側の潤滑剤と入れ代わることになる。
これにより、転がり軸受内で潤滑剤が循環することにな
り、比較的大量の潤滑剤が転動体や内外輪の潤滑に供さ
れ、転がり軸受の損傷防止や耐久性向上が実現される。As is apparent from the above description, according to the rolling bearing of the present invention, the inner race having the inner raceway surface on the outer peripheral side, the outer race having the outer raceway surface on the inner circumferential side, the inner race and the A rolling bearing provided with a large number of rolling elements interposed between an outer ring and rollingly contacting the inner raceway surface and the outer raceway surface, and an annular retainer used for holding these rolling elements. At least one end face of the cage is provided with a large number of substantially radially arranged impellers or grooves to circulate the lubricant stored between the inner ring and the outer ring. When the cage rotates as the inner ring or the outer ring rotates, the lubricant on the inner ring side is sent to the outer ring side by the impeller and replaces the lubricant on the outer ring side.
As a result, the lubricant circulates in the rolling bearing, and a relatively large amount of the lubricant is used to lubricate the rolling elements and the inner and outer races, thereby preventing the rolling bearing from being damaged and improving the durability.
【図１】本発明の第１実施形態に係る転がり軸受の半裁
縦断面図である。FIG. 1 is a semi-cut vertical sectional view of a rolling bearing according to a first embodiment of the present invention.
【図２】保持器の正面図である。FIG. 2 is a front view of a cage.
【図３】図２中のＡ−Ａ断面図である。3 is a cross-sectional view taken along the line AA in FIG.
【図４】図３中のＢ矢視図である。FIG. 4 is a view on arrow B in FIG.
【図５】保持器に形成されるインペラの断面形状の例を
示す図である。FIG. 5 is a diagram showing an example of a cross-sectional shape of an impeller formed in a cage.
【図６】保持器に形成される溝の断面形状の例を示す図
である。FIG. 6 is a diagram showing an example of a cross-sectional shape of a groove formed in a cage.
【図７】本発明の第２実施形態に係る転がり軸受を示す
半裁縦断面図である。FIG. 7 is a semi-cut vertical sectional view showing a rolling bearing according to a second embodiment of the present invention.
【図８】本発明の第３実施形態に係るエンジン補機を示
す要部半裁縦断面図である。FIG. 8 is a half-cut longitudinal sectional view of essential parts showing an engine accessory according to a third embodiment of the present invention.
【図９】本発明の第４実施形態に係るエンジン補機を示
す要部半裁縦断面図である。FIG. 9 is a half-cut longitudinal sectional view of essential parts showing an engine accessory according to a fourth embodiment of the present invention.
【図１０】本発明の第５実施形態に係るエンジン補機を
示す要部半裁縦断面図である。FIG. 10 is a half-cut longitudinal sectional view of essential parts showing an engine accessory according to a fifth embodiment of the present invention.
【図１１】本発明の第６実施形態に係るエンジン補機を
示す要部半裁縦断面図である。FIG. 11 is a half-cut vertical sectional view of essential parts showing an engine accessory according to a sixth embodiment of the present invention.
【図１２】本発明の第７実施形態に係るプーリを示す縦
断面図である。FIG. 12 is a vertical sectional view showing a pulley according to a seventh embodiment of the present invention.
１‥‥転がり軸受（グリース封入式の４点接触玉軸受）
３‥‥内軌道面
５‥‥内輪
７‥‥外軌道面
９‥‥外輪
１１‥‥鋼球
１３‥‥保持器
１５，１７‥‥弾性シール
１９‥‥グリース
２１‥‥リング部
２３‥‥爪部
２５‥‥ポケット
３１‥‥第１インペラ
３３‥‥第２インペラ
３５‥‥溝
３７‥‥転がり軸受（グリース封入式の複列アンギュラ
玉軸受）
４１‥‥クーラコンプレッサ
４３‥‥コンプレッサボディ
４５‥‥プーリ
４７‥‥コンプレッサシャフト
４９‥‥板ばね
５１‥‥環状板
５３‥‥クラッチマグネット
５５‥‥多溝付ベルト
ｔ１，ｔ２‥‥インペラと弾性シールとの間隔1 ... Rolling bearing (Grease-filled 4-point contact ball bearing) 3 ... Inner raceway surface 5 ... Inner ring 7 ... Outer raceway surface 9 ... Outer ring 11 ... Steel ball 13 ... Cages 15, 17 ... Elastic seal 19 Grease 21 Ring 23 Claw 25 Pocket 31 First impeller 33 Second impeller 35 Groove 37 Rolling bearing (grease-filled double-row angular contact) Ball bearing 41 Cooler compressor 43 Compressor body 45 Pulley 47 Compressor shaft 49 Leaf spring 51 Annular plate 53 Clutch magnet 55 Multi-grooved belt t1, t2 Impeller And the distance between the elastic seal
Claims (4)
前記外軌道面とに転接する多数の転動体と、 これら転動体の保持に供される円環状の保持器とを備え
た転がり軸受であって、 前記保持器の少なくとも一方の端面には、前記内輪と前
記外輪との間に貯留された潤滑剤を循環させるべく、略
放射状に配置された多数のインペラまたは溝が設けられ
たことを特徴とする転がり軸受。1. An inner ring having an inner raceway surface on the outer peripheral side, an outer race having an outer raceway surface on the inner circumferential side, and an intermediate ring interposed between the inner race and the outer race, and the inner raceway surface and the outer raceway surface. A rolling bearing comprising a large number of rolling elements rollingly contacting with each other, and an annular cage used for holding these rolling elements, wherein at least one end surface of the cage has the inner ring and the outer ring. A rolling bearing, characterized in that a large number of impellers or grooves arranged substantially radially are provided in order to circulate the stored lubricant between the bearing and the bearing.
斜または湾曲をもって形成されると共に、回転方向を規
定するための指示手段を有することを特徴とする、請求
項１記載の転がり軸受。2. The rolling bearing according to claim 1, wherein the impeller or groove is formed to be inclined or curved with respect to radiation and has an indicating means for defining a rotation direction.
剤を封入するためのシール手段が設けられたことを特徴
とする、請求項１または２記載の転がり軸受。3. The rolling bearing according to claim 1, wherein a seal means for enclosing the lubricant is provided between the inner ring and the outer ring.
記保持器におけるインペラまたは溝が形成された側の外
端と前記シール手段との間隔が０．０３Ｄ以上に設定さ
れたことを特徴とする、請求項３記載の転がり軸受。4. The rolling element is a sphere having a diameter D, and the distance between the outer end of the cage on the side where the impeller or groove is formed and the sealing means is set to 0.03D or more. The rolling bearing according to claim 3, characterized in that.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2001373003A JP2003172366A (en) | 2001-12-06 | 2001-12-06 | Rolling bearing |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2001373003A JP2003172366A (en) | 2001-12-06 | 2001-12-06 | Rolling bearing |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JP2003172366A true JP2003172366A (en) | 2003-06-20 |
Family
ID=19181789
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2001373003A Withdrawn JP2003172366A (en) | 2001-12-06 | 2001-12-06 | Rolling bearing |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2003172366A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR100799640B1 (en) | 2006-07-19 | 2008-01-30 | 셰플러코리아(유) | Seal with protrusions for bearing and the bearing comprising the seal |
| CN106050930A (en) * | 2015-04-16 | 2016-10-26 | 斯凯孚公司 | Rolling element bearing |
-
2001
- 2001-12-06 JP JP2001373003A patent/JP2003172366A/en not_active Withdrawn
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR100799640B1 (en) | 2006-07-19 | 2008-01-30 | 셰플러코리아(유) | Seal with protrusions for bearing and the bearing comprising the seal |
| CN106050930A (en) * | 2015-04-16 | 2016-10-26 | 斯凯孚公司 | Rolling element bearing |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| A300 | Withdrawal of application because of no request for examination |
Free format text: JAPANESE INTERMEDIATE CODE: A300 Effective date: 20050301 |