JP2857304B2 - Bearing device and method of manufacturing the same - Google Patents
Bearing device and method of manufacturing the sameInfo
- Publication number
- JP2857304B2 JP2857304B2 JP25780093A JP25780093A JP2857304B2 JP 2857304 B2 JP2857304 B2 JP 2857304B2 JP 25780093 A JP25780093 A JP 25780093A JP 25780093 A JP25780093 A JP 25780093A JP 2857304 B2 JP2857304 B2 JP 2857304B2
- Authority
- JP
- Japan
- Prior art keywords
- bearing
- rotating shaft
- oil
- dynamic pressure
- dynamic
- 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 - Lifetime
Links
- 238000004519 manufacturing process Methods 0.000 title claims description 7
- 230000003746 surface roughness Effects 0.000 claims description 19
- 239000007769 metal material Substances 0.000 claims description 12
- 229910045601 alloy Inorganic materials 0.000 claims description 10
- 239000000956 alloy Substances 0.000 claims description 10
- 230000002093 peripheral effect Effects 0.000 claims description 8
- 239000003921 oil Substances 0.000 description 41
- 229910000897 Babbitt (metal) Inorganic materials 0.000 description 22
- 239000002184 metal Substances 0.000 description 9
- 238000005461 lubrication Methods 0.000 description 8
- 230000000694 effects Effects 0.000 description 6
- 239000012530 fluid Substances 0.000 description 6
- 230000001050 lubricating effect Effects 0.000 description 6
- 239000004519 grease Substances 0.000 description 3
- 239000000314 lubricant Substances 0.000 description 3
- 238000000034 method Methods 0.000 description 3
- 238000005470 impregnation Methods 0.000 description 2
- 239000000463 material Substances 0.000 description 2
- 238000003825 pressing Methods 0.000 description 2
- 238000005086 pumping Methods 0.000 description 2
- 239000004575 stone Substances 0.000 description 2
- 208000031872 Body Remains Diseases 0.000 description 1
- CWYNVVGOOAEACU-UHFFFAOYSA-N Fe2+ Chemical compound [Fe+2] CWYNVVGOOAEACU-UHFFFAOYSA-N 0.000 description 1
- XUIMIQQOPSSXEZ-UHFFFAOYSA-N Silicon Chemical compound [Si] XUIMIQQOPSSXEZ-UHFFFAOYSA-N 0.000 description 1
- 238000005299 abrasion Methods 0.000 description 1
- 230000002411 adverse Effects 0.000 description 1
- 150000001875 compounds Chemical class 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 239000003305 oil spill Substances 0.000 description 1
- 238000005498 polishing Methods 0.000 description 1
- 239000011148 porous material Substances 0.000 description 1
- 238000003672 processing method Methods 0.000 description 1
- 230000000717 retained effect Effects 0.000 description 1
- 229910052710 silicon Inorganic materials 0.000 description 1
- 239000010703 silicon Substances 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
Landscapes
- Sliding-Contact Bearings (AREA)
Description
【発明の詳細な説明】DETAILED DESCRIPTION OF THE INVENTION
【０００１】[0001]
【産業上の利用分野】本発明は、軸受装置及びその製造
方法に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a bearing device and a method of manufacturing the same.
【０００２】[0002]
【従来の技術】従来の軸受装置として、軸受滑り面にヘ
リングボーン状やスパイラル状の所謂動圧発生溝が複数
形成された動圧グループ軸受が知られている。係る動圧
グループ軸受は滑り軸受の一種であり、回転に伴って滑
り面に設けた上記動圧発生溝に沿ってオイル等の潤滑材
（作動流体）を軸受内部に押し込み、潤滑材に高い圧力
を発生させ、この流体圧力により負荷を受けるようにし
たものである。2. Description of the Related Art As a conventional bearing device, there is known a dynamic pressure group bearing in which a plurality of so-called herringbone-shaped or spiral-shaped so-called dynamic pressure generating grooves are formed on a sliding surface of a bearing. Such a dynamic pressure group bearing is a kind of a sliding bearing, in which a lubricant (working fluid) such as oil is pushed into the bearing along the above-mentioned dynamic pressure generating groove provided on the sliding surface with rotation, and a high pressure is applied to the lubricant. And a load is received by the fluid pressure.
【０００３】しかしながら、これら軸受装置にあって
は、回転軸並びに軸受材料として金属または非鉄金属を
使用しているので、高速回転では該動圧発生溝に注油さ
れた潤滑材が遠心力により流出し、潤滑不足により軸受
剛性が不足し回転軸の振れが大きくなって、やがて焼付
けに至るという問題がある。However, in these bearing devices, metal or non-ferrous metal is used as the rotating shaft and the bearing material. Therefore, at high speed rotation, the lubricant injected into the dynamic pressure generating groove flows out due to centrifugal force. However, there is a problem in that the bearing rigidity is insufficient due to insufficient lubrication, the runout of the rotating shaft is increased, and eventually burning occurs.
【０００４】また、起動時には、金属接触〜境界潤滑を
繰り返すことになるので、回転軸や軸受にキズが発生
し、動圧機能を失うという問題もある。[0004] In addition, at the time of startup, since metal contact to boundary lubrication is repeated, there is a problem that the rotating shaft and the bearing are damaged, and the dynamic pressure function is lost.
【０００５】そこで、本出願人は先に出願した特公昭６
３−６０２４７号公報の『動圧軸受装置』、特開平３−
１０７６１２号公報の『焼結含油軸受』、実開平３−９
６４２６号公報の『軸受装置』において、上記問題点の
解決を図った。Therefore, the present applicant has filed a Japanese Patent Application No. Sho 6
3-60247, "Dynamic pressure bearing device";
No. 107612, “Sintered oil-impregnated bearing”, Japanese Utility Model Laid-Open No. 3-9
In the "Bearing device" of JP-A-6426, the above problem was solved.
【０００６】特公昭６３−６０２４７号公報の動圧軸受
装置は、多孔質性の焼結合金よりなる軸受メタルの軸孔
に動圧発生溝を形成すると共に、該軸受メタルに含浸さ
せたオイルと、回転軸との間に介在させた油膜形成のた
めのグリースとを、同一動粘度且つ同一種としたもので
あり、動圧作用を生じない回転軸の始動時には、軸受メ
タルのオイルにより潤滑機能を達成し、始動後には、グ
リースにより流体膜を形成して潤滑機能を達成するとい
うものである。In the dynamic pressure bearing device disclosed in Japanese Patent Publication No. 63-60247, a dynamic pressure generating groove is formed in a shaft hole of a bearing metal made of a porous sintered alloy, and an oil impregnated in the bearing metal is formed. The grease interposed between the rotating shaft and the grease for forming an oil film has the same kinematic viscosity and the same kind. When starting the rotating shaft that does not generate a dynamic pressure effect, the lubrication function is provided by the oil of the bearing metal. After starting, a fluid film is formed by grease to achieve a lubricating function.
【０００７】特開平３−１０７６１２号公報の焼結含油
軸受は、内側に突出し、回転軸との間のクリアランスを
他の部分よりも小さくすると共に、該回転軸との間で楔
状の隙間を形成する突出部を３条以上等角度に配設する
ようにしたものであり、該突出部に、軸回転時に集まる
油で楔状の油膜を形成し、良好な潤滑機能を得るという
ものである。The sintered oil-impregnated bearing disclosed in Japanese Patent Application Laid-Open No. 3-107612 is designed to protrude inward, make the clearance between the bearing and the rotating shaft smaller than other parts, and form a wedge-shaped gap with the rotating shaft. The projecting portions are arranged at three or more equiangular angles, and a wedge-shaped oil film is formed on the projecting portions with oil collected during rotation of the shaft, thereby obtaining a good lubricating function.
【０００８】実開平３−９６４２６号公報の軸受装置
は、軸受または回転軸の何れか一方に該回転軸支承用の
突出部を設け、この突出部に所定以上の油動圧効果を生
じさせるべく、該突出部を所定の面積にて相手側に対向
させるようにしたものであり、各突出部とこれら突出部
に対向する相手方との間に常時良好な油膜を形成し、良
好な潤滑機能を得るというものである。In the bearing device disclosed in Japanese Utility Model Laid-Open Publication No. 3-96426, a protruding portion for supporting the rotary shaft is provided on one of the bearing and the rotary shaft. The projecting portions are opposed to each other with a predetermined area, and a good oil film is always formed between each projecting portion and the other party facing these projecting portions, so that a good lubrication function is provided. It is to get.
【０００９】[0009]
【発明が解決しようとする課題】しかしながら、上記各
提案装置においても、以下の問題点があった。すなわ
ち、回転軸の動圧摺動表面に対しては、通常超精密仕上
げ（研削）を行っており、従ってその表面粗さは凡そ
０．３Ｓ以下となっているが、このような表面粗さだと
回転軸の動圧摺動面への油の濡れ性が悪く、油膜が切れ
やすくなって、良好な潤滑機能が常時得られないといっ
た問題がある。However, each of the above proposed devices has the following problems. That is, the sliding surface of the dynamic pressure of the rotating shaft is usually subjected to ultra-precision finishing (grinding), so that the surface roughness is about 0.3 S or less. In addition, there is a problem that the wettability of the oil to the dynamic pressure sliding surface of the rotating shaft is poor, the oil film is easily cut, and a good lubricating function cannot always be obtained.
【００１０】また、超精密仕上げによれば、表面に生じ
る突起が鋭利となるので、接触キズがつきやすいという
問題がある。[0010] Further, according to the ultra-precision finishing, the projections formed on the surface become sharp, so that there is a problem that a contact flaw is easily formed.
【００１１】また、超精密仕上げによれば、金属接触時
における接触面が多いので、摩耗が生じやすく、回転精
度に悪影響を及ぼす畏れがある。Further, according to the ultra-precision finishing, since there are many contact surfaces at the time of metal contact, abrasion is likely to occur, and there is a fear that rotation accuracy may be adversely affected.
【００１２】さらにまた、超精密仕上げによれば、動作
状態における回転軸への油の付着性が比較的悪く、安定
した動圧特性が得られないといった問題もある。Further, the ultra-precision finishing has a problem that oil adherence to a rotating shaft in an operating state is relatively poor and stable dynamic pressure characteristics cannot be obtained.
【００１３】そこで本発明は、油の濡れ性が良く常時良
好な動圧潤滑機能が得られると共に、表面に生じる突起
形状が鈍く接触キズの発生が防止され、しかも接触面が
少なく回転精度が良好に維持され、その上動作状態にお
ける回転軸への油の付着性が良好で安定した動圧特性が
得られる軸受装置及びその製造方法を提供することを目
的とする。Therefore, the present invention provides good hydrodynamic lubrication function with good oil wettability, and prevents the occurrence of contact flaws due to the dull projections formed on the surface. It is another object of the present invention to provide a bearing device in which oil is adhered to a rotating shaft in an operating state and good dynamic pressure characteristics can be obtained, and a method of manufacturing the same.
【００１４】[0014]
【課題を解決するための手段】本発明の軸受装置は、上
記目的を達成するために、軸受の内部に回転軸が配置さ
れ、前記軸受の内周側動圧摺動面と前記回転軸の外周側
動圧摺動面との間に、当該動圧摺動面に設けられた動圧
発生溝の加圧力により油膜を形成して前記回転軸を回転
自在に支承するようにした軸受装置において、前記軸受
または回転軸の何れか一方を、焼結含油合金より形成す
ると共に、他方を、表面粗さ０．３Ｓ〜０．５Ｓのラン
ダムな凹凸をその動圧摺動面に有する金属材としたこと
を特徴としている。The bearing device of the present invention SUMMARY OF THE INVENTION In order to achieve the above object, the rotation shaft disposed within the bearing, the inner circumferential Gawado圧摺dynamic surface of the bearing and the rotary shaft Outer side
Between the dynamic pressure sliding surface, the dynamic pressure provided to the dynamic圧摺dynamic surface
In a bearing device in which an oil film is formed by the pressing force of the generated groove to rotatably support the rotating shaft, one of the bearing and the rotating shaft is formed of a sintered oil-impregnated alloy, and the other is It is characterized in that a metal material having a random uneven surface roughness 0.3S~0.5S its dynamic pressure sliding surface.
【００１５】本発明の軸受装置の製造方法は、上記目的
を達成するために、上記手段における金属材の動圧摺動
面における表面粗さを、バレル仕上げにより得ることを
特徴としている。In order to achieve the above object, a method of manufacturing a bearing device according to the present invention is characterized in that a dynamic sliding of a metal material in the above means is performed.
The surface roughness of the surface is obtained by barrel finishing.
【００１６】[0016]
【作用】このような手段における軸受装置によれば、表
面粗さ０．３Ｓ〜０．５Ｓのランダムな凹凸を有する金
属材の動圧摺動面は、焼結含油合金との間に介在する油
の濡れ性を良好にするよう働く。また、動圧摺動面の表
面に生じる突起形状を鈍った形状にするようにも働く。
また、金属接触時における接触面を研削品に比べて少な
くするようにも働く。さらにまた、動作状態における油
の付着性を良好にするようにも働く。SUMMARY OF] According to the bearing apparatus in such a way, the dynamic pressure sliding surface of the metal material having a random uneven surface roughness 0.3S~0.5S is interposed between the oil-impregnated sintered alloy It works to improve oil wettability. Further, it also works to make the shape of the protrusion generated on the surface of the dynamic pressure sliding surface into a dull shape.
It also works to reduce the contact surface at the time of metal contact as compared to a ground product. Furthermore, it also works to improve the oil adhesion in the operating state.
【００１７】このような手段における軸受装置の製造方
法によれば、金属材にバレル仕上げを行えば、表面粗さ
０．３Ｓ〜０．５Ｓのランダムな凹凸を有する摺動面が
簡単に得られる。According to the method of manufacturing a bearing device in such a means, if a metal material is subjected to barrel finishing, a sliding surface having a random unevenness with a surface roughness of 0.3S to 0.5S can be easily obtained. .
【００１８】[0018]
【実施例】以下、本発明の実施例を図面に基づいて説明
する。図１は本発明の第１実施例を示す軸受装置の横断
面図、図２は図１に示される軸受の横断面図であり、図
１にあっては図が煩雑になるのを避けるためにその右半
分のみが示されている。Embodiments of the present invention will be described below with reference to the drawings. FIG. 1 is a cross-sectional view of a bearing device according to a first embodiment of the present invention, and FIG. 2 is a cross-sectional view of the bearing shown in FIG. 1. In FIG. Shows only the right half.
【００１９】この第１実施例の軸受装置は、その基本構
造を特公昭６３−６０２４７号公報のそれと凡そ同じに
している。図１、図２において、符号３０で示される軸
受メタルは、従来技術で述べた動圧グループ軸受であ
る。軸受メタル３０は、スリーブ状に形成されており、
この軸孔の周囲の滑り面には、図２に示されるように、
複数の傾斜した、例えばヘリングボーン状の動圧発生溝
３０ａが形成されている。なお、この動圧発生溝は、複
数本のスパイラル状のものであっても良い。The basic structure of the bearing device of the first embodiment is substantially the same as that of Japanese Patent Publication No. 63-60247. In FIGS. 1 and 2, the bearing metal indicated by reference numeral 30 is the dynamic pressure group bearing described in the related art. The bearing metal 30 is formed in a sleeve shape,
As shown in FIG. 2, on the sliding surface around the shaft hole,
A plurality of inclined, for example, herringbone-shaped dynamic pressure generating grooves 30a are formed. The dynamic pressure generating groove may be a plurality of spiral grooves.
【００２０】軸受メタル３０は、多孔質性（ポーラス）
の焼結合金から成り、この多孔部分には、動粘度が例え
ば５０Ｃ／Ｓ相当のシリコン系のオイルが含浸されてい
る。すなわち、軸受メタル３０は所謂焼結含油軸受とな
っている。なお、このオイルの含浸は、例えば高温下で
の真空含浸法によって行われている。The bearing metal 30 is porous.
This porous portion is impregnated with a silicon-based oil having a kinematic viscosity of, for example, 50 C / S. That is, the bearing metal 30 is a so-called sintered oil-impregnated bearing. The oil impregnation is performed, for example, by a vacuum impregnation method at a high temperature.
【００２１】このように構成された軸受メタル３０の軸
孔には回転軸として、例えばキャプスタン軸２１が嵌挿
されている。A capstan shaft 21, for example, is fitted as a rotation shaft in the shaft hole of the bearing metal 30 thus configured.
【００２２】ここで、本実施例の特徴をなす点である
が、該回転軸２１は金属材より形成されていて、その表
面（動圧摺動面）には表面粗さ０．３Ｓ〜０．５Ｓのラ
ンダムな凹凸が形成されている。[0022] Here, although a point, which is the characteristic of the present embodiment, the rotary shaft 21 be formed from a metal material, its surface surface (the dynamic pressure sliding surface) roughness 0.3S~0 .5S random irregularities are formed.
【００２３】この動圧摺動面上の表面粗さ０．３Ｓ〜
０．５Ｓのランダムな凹凸は、回転軸２１の仕上げを超
精密仕上げではなく、バレル仕上げとすることにより、
得られるようになっている。The surface roughness on the dynamic pressure sliding surface 0.3S~
The random irregularities of 0.5S are obtained by making the rotating shaft 21 a barrel finish instead of an ultra-precision finish.
You can get it.
【００２４】このバレル仕上げ（バレル研磨）とは、バ
レル槽に仕上げ材としての回転軸２１、バラの研磨石、
コンパウンド、水を装入し、回転、振動、遠心流動、ジ
ャイロ（自公転）、ハイスピン（正逆転と公転）、レシ
プロ（左右往復）、エディーフロー（渦流）、トーナフ
ロー（意巻流動・乾式）の運動を与えて、回転軸２１と
研磨石との間に生じる相対運動差により、表面仕上げを
行う加工法のことであり、このようなバレル仕上げを行
うと、図５に示されるような、表面粗さ０．３Ｓ〜０．
５Ｓのランダムな凹凸が簡単に得られる。The barrel finishing (barrel polishing) means that a rotating shaft 21 as a finishing material, a loose polished stone,
Compound, water charged, rotation, vibration, centrifugal flow, gyro (self-revolution), high spin (forward and reverse rotation and revolving), reciprocating (left and right reciprocating), eddy flow (vortex flow), toner flow (involved flow, dry type) This is a processing method in which a surface is finished by giving a movement and a relative movement difference generated between the rotating shaft 21 and the grinding stone. When such a barrel finishing is performed, the surface as shown in FIG. Roughness 0.3S to 0.
5S random irregularities can be easily obtained.
【００２５】因に、本実施例においては、回転軸２１の
表面粗さは０．３３Ｓ（μｍ）となっている。In this embodiment, the surface roughness of the rotating shaft 21 is 0.33 S (μm).
【００２６】そして、軸受メタル３０の軸孔の一方の端
部側には、大きく面取りしたオイル溜り部３０ｂが形成
され、この部分にオイル３１の一部が溜められるように
なっている。A large chamfered oil reservoir 30b is formed at one end of the shaft hole of the bearing metal 30, and a part of the oil 31 is retained in this portion.
【００２７】ここで、モータが停止している時は回転軸
２１も停止した状態にあり、この状態においては、回転
軸２１の外周の一部は、軸受メタル３０の軸孔の滑り面
に当接している。Here, when the motor is stopped, the rotating shaft 21 is also stopped. In this state, a part of the outer periphery of the rotating shaft 21 contacts the sliding surface of the shaft hole of the bearing metal 30. In contact.
【００２８】係る停止状態から、モータが始動し、回転
軸２１が回転を始める初期の段階においては、軸受メタ
ル３０に含浸されているオイルにより、回転軸２１と軸
受メタル３０との間における潤滑機能が達成され、一方
モータの始動後、回転軸２１が回転を始めた後、軸受メ
タル３０の動圧発生溝３０ａ（図２参照）に沿って回転
軸２１と軸受メタル３０の軸孔との間にオイルが押し込
まれ、ポンピング作用により、両者の間に図１に示され
るように流体膜３１ａが形成され、この流体膜の圧力に
より、回転軸２１は軸孔から離間し、回転軸２１は軸孔
に対し非接触状態で回転する。このような機能が動圧軸
受作用と呼ばれている。In the initial stage of starting the motor and starting rotation of the rotating shaft 21 from the stopped state, the oil impregnated in the bearing metal 30 provides a lubricating function between the rotating shaft 21 and the bearing metal 30. On the other hand, after the start of the motor, after the rotating shaft 21 starts rotating, the gap between the rotating shaft 21 and the shaft hole of the bearing metal 30 along the dynamic pressure generating groove 30a of the bearing metal 30 (see FIG. 2). As shown in FIG. 1, a fluid film 31a is formed between the two by the pumping action, and the pressure of the fluid film causes the rotating shaft 21 to be separated from the shaft hole, and the rotating shaft 21 to rotate. It rotates without contact with the hole. Such a feature is dynamic pressure axis
It has been referred to as the receiving action.
【００２９】回転軸２１が軸孔に対し非接触状態で回転
する時、焼結合金より成る軸受メタル３０の多孔部内に
は充分にオイルが含浸されている。When the rotating shaft 21 rotates without contact with the shaft hole, oil is sufficiently impregnated in the porous portion of the bearing metal 30 made of a sintered alloy.
【００３０】流体膜３１ａは回転軸２１の回転に伴なっ
て移動するも、オイル溜り３０ｂが設けられていて、こ
の部分と、軸孔面との間でオイルが循環するようになる
ので、そのオイルの流出が防止される。Although the fluid film 31a moves with the rotation of the rotating shaft 21, an oil reservoir 30b is provided, and oil circulates between this portion and the shaft hole surface. Oil spill is prevented.
【００３１】一方、モータの始動時において、回転軸２
１が軸受メタル３０の軸孔面に接触している時は、摩擦
により、軸受メタル内のオイルが回転軸２１に向けて流
れ、このオイルにより、回転軸１１との間に潤滑機能が
達成される。そして、回転軸２１に向けて流れたオイル
は、軸受メタル３０の両端側に進行し、かつ、両端側か
ら軸受メタルの多孔部内に戻り、これによりポンプ作用
が行われる。On the other hand, when the motor is started, the rotating shaft 2
When 1 is in contact with the shaft hole surface of the bearing metal 30, oil in the bearing metal flows toward the rotating shaft 21 due to friction, and a lubricating function is achieved between the bearing metal 30 and the rotating shaft 11. You. Then, the oil flowing toward the rotating shaft 21 proceeds to both ends of the bearing metal 30 and returns from both ends to the porous portion of the bearing metal, thereby performing a pumping action.
【００３２】このように、本実施例においては、軸受３
０を焼結含油合金より形成すると共に、回転軸２１を、
表面粗さ０．３Ｓ〜０．５Ｓのランダムな凹凸をその動
圧摺動面に有する金属材としているので、上記動作が支
障なく行われるようになっている。As described above, in this embodiment, the bearing 3
0 is formed from a sintered oil-impregnated alloy, and the rotating shaft 21 is
Its dynamic random irregularities of surface roughness 0.3S~0.5S
Since a metal material having a pressure sliding surface, the operation is supported
It is to be performed without obstacles .
【００３３】すなわち、その理由を詳細に述べれば、表
面粗さ０．３Ｓ〜０．５Ｓのランダムな凹凸を有する動
圧摺動面は、軸受３０との間に介在する油の濡れ性を良
好にするので、油膜が切れなくなり、常時良好な動圧潤
滑機能を得ることができるからである。[0033] That is, Stated the reason in detail, dynamic with random irregularities in surface roughness 0.3S~0.5S
Pressure sliding surface, so to improve the wettability of the oil interposed between the bearing 30, no longer broken oil film, and can obtain a constantly good dynamic Jun <br/> lubricating function.
【００３４】また、該動圧摺動面は、表面に生じる突起
形状を鈍った形状にするので、接触キズの発生を防止す
ることができるからである。Further, the dynamic pressure sliding surface, since the shape of blunt projections shape generated on the surface, is because it is possible to prevent the occurrence of contact flaws.
【００３５】また、該動圧摺動面は、金属接触時におけ
る接触面を、超精密仕上げ等による研削品に比べて少な
くするので、摩耗が生じにくくなり、回転精度を良好に
維持することができるからである。Further, the dynamic pressure sliding surface, the contact surface when the metal contact, so that less than the grinding products according to ultra-precision finishing or the like, wear is less likely to occur, it is possible to maintain good rotational accuracy Because you can.
【００３６】また、該動圧摺動面は、動作状態における
油の付着性を良好にするので、安定した動圧特性を得る
ことができるからである。Further, the dynamic pressure sliding surface, so to improve the adhesion of the oil in the operation state, and can obtain a stable dynamic pressure characteristics.
【００３７】また、本実施例においては、上述の摺動面
における表面粗さ０．３Ｓ〜０．５Ｓのランダムな凹凸
は、バレル仕上げにより、簡単に得ることができるよう
にもなっている。In this embodiment, the above-mentioned random irregularities having a surface roughness of 0.3S to 0.5S on the sliding surface can be easily obtained by barrel finishing.
【００３８】図３は本発明の第２実施例を示す軸受装置
の横断面図であり、その基本構造は特開平３−１０７６
１２号公報と凡そ同じとなっている。FIG. 3 is a cross-sectional view of a bearing device according to a second embodiment of the present invention.
It is almost the same as No. 12 publication.
【００３９】この焼結含油軸受１は、軸孔２の周面の少
なくとも３点以上の点に内側、すなわち回転軸５側に向
けて突出する面（突出部）３を構成している。この突出
部３は、回転軸５との間のクリアランスＣ1 を他の内周
面部分４におけるクリアランスＣ2 よりも小さくし、入
口側（回転方向において手前側）において回転軸５との
間に楔状の隙間Ｓを形成する。この実施例の場合、平坦
な面によって法線を軸として対称に突出部３を構成して
いるので、回転軸５が何れの方向に回転しても所定の効
果が得られる。The sintered oil-impregnated bearing 1 has a surface (projecting portion) 3 projecting inside at least three or more points on the peripheral surface of the shaft hole 2, that is, toward the rotating shaft 5 side. The protrusion 3 has a clearance C 1 between the rotating shaft 5 and the clearance C 2 at the other inner peripheral surface portion 4 smaller than the clearance C 2 between the rotating shaft 5 and the rotating shaft 5 on the inlet side (front side in the rotating direction). A wedge-shaped gap S is formed. In the case of this embodiment, since the protruding portion 3 is formed symmetrically about the normal line by a flat surface, a predetermined effect can be obtained even if the rotating shaft 5 rotates in any direction.
【００４０】突出部３を除く周面部分４は、滑り軸受と
して通常のクリアランス、例えば片側クリアランスＣ2
で１５μｍ以内、好ましくは５〜１０μｍ程度に設定さ
れ、突出部３では片側クリアランスＣ1 で２〜３μｍ程
度のクリアランスを構成するように形成されている。The peripheral surface portion 4 excluding the protruding portion 3 has a normal clearance as a sliding bearing, for example, a one-sided clearance C 2.
In within 15 [mu] m, preferably set to about 5 to 10 [mu] m, it is formed so as to constitute a clearance on the order 2~3μm in protrusion 3 at one side clearance C 1.
【００４１】この軸受は、静止時には回転軸５を３点の
突出部３で支持し、回転時には突出部３において高い油
圧を発生させなければならないので、突出部３の表面の
ポーラスが実質的になくなるように目潰しされている。In this bearing, the rotating shaft 5 is supported by the three projections 3 at rest and a high oil pressure must be generated at the projections 3 during rotation, so that the surface of the projection 3 has a substantially porous surface. It is crushed so that it disappears.
【００４２】そして、この第２実施例にあっても、回転
軸５は、第１実施例と同様に、金属材より形成されてい
て、その表面（摺動面）には表面粗さ０．３Ｓ〜０．５
Ｓのランダムな凹凸がバレル仕上げにより形成されてい
る。In the second embodiment, as in the first embodiment, the rotating shaft 5 is made of a metal material, and its surface (sliding surface) has a surface roughness of 0.1 mm. 3S to 0.5
Random irregularities of S are formed by barrel finishing.
【００４３】従って、回転軸５が回転することにより軸
受１内のポーラスから油が供給され、この油は回転軸５
の回転に伴って突出部３の楔状の隙間Ｓに集まり、楔状
の油膜を形成し、回転軸５を油圧により浮上させるが、
この楔状の隙間Ｓ・突出部３は円周上に３箇所均等配置
されているので、各突出部３における油圧Ｆ1 ，Ｆ2，
Ｆ3 の浮上効果により回転軸５は動圧軸受と同様に安定
支持されつつ回転するという動作が、回転軸５の摺動面
に表面粗さ０．３Ｓ〜０．５Ｓのランダムな凹凸をバレ
ル仕上げにより形成することにより、支承なく行われる
ようになっている。その詳細な理由は第１実施例と勿論
同じである。Accordingly, the rotation of the rotary shaft 5 causes oil to be supplied from the porous portion in the bearing 1, and this oil is supplied to the rotary shaft 5.
Gathers in the wedge-shaped gap S of the protruding portion 3 with the rotation of, forms a wedge-shaped oil film, and causes the rotating shaft 5 to float by hydraulic pressure.
Since the wedge-shaped gaps S and the projections 3 are evenly arranged at three places on the circumference, the hydraulic pressures F 1 , F 2 ,
Due to the floating effect of F 3, the rotating shaft 5 rotates while being supported stably in the same manner as the dynamic pressure bearing. The sliding surface of the rotating shaft 5 has a random unevenness having a surface roughness of 0.3 S to 0.5 S in the barrel. By forming by finishing, it can be performed without bearing. The detailed reason is the same as that of the first embodiment.
【００４４】図４は本発明の第３実施例を示す軸受装置
の横断面図であり、その基本構造は実開平３−９６４２
６号公報と凡そ同じとなっている。図４において、焼結
含油合金を中空円筒状に形成してなる軸受１１の内部に
は、回転軸１２が遊嵌状態にて挿入されている。上記軸
受１１の内周面１１ａには３体の突出部１１ｂが半径方
向内側、すなわち回転軸１２側に向かって突設されてい
る。そして、これらの各突出部１１ｂと該突出部１１ｂ
に対向する相手方の回転軸１２との間に楔状の油膜１３
がそれぞれ形成されて、いわゆる自己潤滑が行われるよ
うになっている。FIG. 4 is a cross-sectional view of a bearing device according to a third embodiment of the present invention.
It is almost the same as that of JP-A-6. In FIG. 4, a rotating shaft 12 is loosely inserted into a bearing 11 formed of a sintered oil-impregnated alloy in a hollow cylindrical shape. On the inner peripheral surface 11a of the bearing 11, three protruding portions 11b are provided so as to protrude radially inward, that is, toward the rotating shaft 12 side. Then, each of these protrusions 11b and the protrusions 11b
Wedge-shaped oil film 13 between the rotating shaft 12 and the other
Are formed, and so-called self-lubrication is performed.
【００４５】この時、上記各突出部１１ｂにおける回転
軸１２への対向部分は、回転軸１２の外周面に沿った曲
面状をなすように形成されており、その対向面積は、上
記油膜１３の動圧効果を所定以上の大きさになすべく所
定以上の面積を備えるように形成されている。この突出
部１１ｂの回転軸１２への対向面積は、回転軸１２に負
荷される偏心荷重の大きさに比例して設定される。At this time, the portion of each of the protrusions 11 b facing the rotating shaft 12 is formed so as to form a curved surface along the outer peripheral surface of the rotating shaft 12. It is formed so as to have a predetermined area or more in order to make the dynamic pressure effect a predetermined size or more. The area of the protrusion 11b facing the rotation shaft 12 is set in proportion to the magnitude of the eccentric load applied to the rotation shaft 12.
【００４６】また、上記突出部１１ｂにおける回転軸１
２への対向表面部分には目潰しが施されており、ポーラ
スは存在しないようになされている。この目潰しは、軸
受１１の作成過程において中子に相当する棒部材を突出
部１１ｂの表面部分に押し付けることによって容易に形
成することができる。なお、上記軸受１１の内周面１１
ａのうち、突出部１１ｂを除く他の内壁部分にはポーラ
スはそのまま存在しており、ここから給油が行われるよ
うになっている。Further, the rotating shaft 1 at the projecting portion 11b
The facing surface portion to 2 is crushed so that no porous material exists. This crushing can be easily formed by pressing a rod member corresponding to the core against the surface portion of the protruding portion 11b in the process of producing the bearing 11. The inner peripheral surface 11 of the bearing 11
Among the parts a, the porous body remains as it is on the other inner wall part except for the protruding part 11b, from which the refueling is performed.
【００４７】そして、この第３実施例にあっても、回転
軸５は、第１、第２実施例と同様に、金属材より形成さ
れていて、その表面（摺動面）には表面粗さ０．３Ｓ〜
０．５Ｓのランダムな凹凸がバレル仕上げにより形成さ
れている。Also, in the third embodiment, the rotating shaft 5 is formed of a metal material as in the first and second embodiments, and its surface (sliding surface) has a rough surface. 0.3S ~
0.5S random irregularities are formed by barrel finishing.
【００４８】この第３実施例においては、回転軸１２に
対して所定以上の大きさの対向面積を突出部１１ｂが備
えることにより、その大きな対向面積に対応して大きな
油の動圧効果を生じるようになっている。すなわち上記
各突出部１１ｂの回転軸１２への対向面積が大きくなさ
れると、両者間に生じる油圧の逃げ量が小さくなってそ
の分動圧が大きくなり、さらにこの大きな動圧が、突出
部１１ｂの表面における目潰し部分によって安定して維
持されるようになっている。In the third embodiment, since the protruding portion 11b has an opposing area of a predetermined size or more with respect to the rotating shaft 12, a large oil dynamic pressure effect is produced corresponding to the large opposing area. It has become. That is, when the area of each of the protrusions 11b facing the rotation shaft 12 is increased, the relief amount of the hydraulic pressure generated between the two decreases, and the dynamic pressure increases accordingly. The surface is stably maintained by the crushed portion on the surface.
【００４９】このため、回転軸１２に対して偏心方向の
大荷重が加えられる場合であっても、各突出部１１ｂと
該突出部１１ｂに対向する相手方の回転軸１２との間に
は良好に油膜１３が形成されることとなり、これによる
自己潤滑によって回転軸１２は軸受１１に金属接触する
ことなく安定して支承・維持されるようになっている。Therefore, even when a large load in the eccentric direction is applied to the rotating shaft 12, a good fit is provided between each protruding portion 11b and the counterpart rotating shaft 12 facing the protruding portion 11b. The oil film 13 is formed, and by this self-lubrication, the rotating shaft 12 is stably supported and maintained without metallic contact with the bearing 11.
【００５０】また、万一両者が金属接触を起こしても、
各突出部１１ｂの回転軸１２への対向面積が大きいため
に、接触時における単位面積あたりの荷重（面圧）は小
さく抑えられることとなり、従って軸受１１の摩擦は進
行しにくくなっている。Also, even if the two make metal contact,
Since the area of each projection 11b facing the rotation shaft 12 is large, the load per unit area (surface pressure) at the time of contact can be kept small, so that the friction of the bearing 11 does not easily progress.
【００５１】これら動作・効果は、回転軸５の摺動面に
表面粗さ０．３Ｓ〜０．５Ｓのランダムな凹凸をバレル
仕上げにより形成することにより、支承なく得られるよ
うになっている。その詳細な理由は第１実施例と勿論同
じである。These operations and effects can be obtained without bearing by forming random irregularities having a surface roughness of 0.3S to 0.5S on the sliding surface of the rotating shaft 5 by barrel finishing. The detailed reason is the same as that of the first embodiment.
【００５２】以上本発明者によってなされた発明を各実
施例に基づき具体的に説明したが、本発明は上記各実施
例に限定されるものではなく、その要旨を逸脱しない範
囲で種々変形可能であるというのはいうまでもなく、例
えば第１実施例においては、軸受メタルに含浸させるオ
イルや回転軸との間に介在させるオイルの動粘度を限定
しているが、本発明は限定されていない軸受装置に対し
ても同様に適用可能である。Although the invention made by the inventor has been specifically described based on the embodiments, the present invention is not limited to the above embodiments and can be variously modified without departing from the gist thereof. Needless to say, for example, in the first embodiment, the kinematic viscosity of the oil impregnated in the bearing metal or the oil interposed between the bearing metal and the rotary shaft is limited, but the present invention is not limited. The present invention can be similarly applied to a bearing device.
【００５３】また、第２、第３実施例においては、軸受
１，１１側に突出部３，１１ｂを設けるようにしている
が、回転軸５，１２側に突出部を設ける構成とすること
も可能である。In the second and third embodiments, the protruding portions 3 and 11b are provided on the bearings 1 and 11 side. However, the protruding portions may be provided on the rotating shafts 5 and 12 side. It is possible.
【００５４】さらにまた、上記各実施例においては、軸
受を焼結含油合金より形成し、回転軸を、表面粗さ０．
３Ｓ〜０．５Ｓのランダムな凹凸をその摺動面に有する
金属材としているが、その逆とすることも可能である。Further, in each of the above embodiments, the bearing is formed of a sintered oil-impregnated alloy, and the rotating shaft is provided with a surface roughness of 0.1 mm.
Although a metal material having random irregularities of 3S to 0.5S on its sliding surface is used, the reverse is also possible.
【００５５】[0055]
【発明の効果】以上述べたように本発明の軸受装置によ
れば、軸受または回転軸の何れか一方を、焼結含油合金
より形成すると共に、他方を、表面粗さ０．３Ｓ〜０．
５Ｓのランダムな凹凸をその動圧摺動面に有する金属材
としたので、該動圧摺動面は、焼結含油合金との間に介
在する油の濡れ性を良好にするよう働き、油膜が切れな
いようになって、常時良好な動圧潤滑機能を得ることが
可能となる。また、該動圧摺動面は、表面に生じる突起
形状を鈍った形状にするよう働き、接触キズの発生を防
止することが可能となる。また、該動圧摺動面は、金属
接触時における接触面を研削品に比べて少なくするよう
働き、摩耗が生じにくくなって、回転精度を良好に維持
することが可能となる。さらにまた、該動圧摺動面は、
動作状態における油の付着性を良好にするよう働き、安
定した動圧特性を得ることが可能となる。また、本発明
の軸受装置の製造方法によれば、バレル仕上げにより、
上記金属動圧材摺動面の表面粗さを簡単に得ることがで
きる。As described above, according to the bearing device of the present invention, one of the bearing and the rotating shaft is formed of a sintered oil-impregnated alloy, and the other is formed of a surface roughness of 0.3S to 0.
Since the metal material having 5S random irregularities in their dynamic pressure sliding surface, the hydrodynamic sliding surface serves as to improve the wettability of the oil interposed between the oil-impregnated sintered alloy, oil film , So that a good dynamic pressure lubrication function can always be obtained. Also, the dynamic pressure sliding surface serves to the shape of blunt projections shape generated on the surface, it is possible to prevent the occurrence of contact flaws. Also, the dynamic pressure sliding surface serves to less than the contact surface when the metal in contact with the grinding goods, wear is less likely to occur, it is possible to satisfactorily maintain the rotational accuracy. Furthermore, the dynamic pressure sliding surface,
It works to improve the oil adhesion in the operating state, so that stable dynamic pressure characteristics can be obtained. Further, according to the method for manufacturing a bearing device of the present invention, by barrel finishing,
It can be easily obtained surface roughness of the metal dynamic pressure Zaisurido surface.
【図１】本発明の第１実施例を示す軸受装置の横断面図
である。FIG. 1 is a cross-sectional view of a bearing device according to a first embodiment of the present invention.
【図２】図１に示される軸受の横断面図である。FIG. 2 is a cross-sectional view of the bearing shown in FIG.
【図３】本発明の第２実施例を示す軸受装置の縦断面図
である。FIG. 3 is a longitudinal sectional view of a bearing device according to a second embodiment of the present invention.
【図４】本発明の第３実施例を示す軸受装置の縦断面図
である。FIG. 4 is a longitudinal sectional view of a bearing device according to a third embodiment of the present invention.
【図５】バレル仕上げにより得られる表面粗さを表した
図である。FIG. 5 is a diagram showing the surface roughness obtained by barrel finishing.
１，１１，３０ 軸受 ４，１１ａ 軸受の内周面 ５，１２，２１ 回転軸 ３１ａ 油膜 1,11,30 Bearing 4,11a Inner peripheral surface of bearing 5,12,21 Rotating shaft 31a Oil film
Claims (2)
受の内周側動圧摺動面と前記回転軸の外周側動圧摺動面
との間に、当該動圧摺動面に設けられた動圧発生溝の加
圧力により油膜を形成して前記回転軸を回転自在に支承
するようにした軸受装置において、 前記軸受または回転軸の何れか一方を、焼結含油合金よ
り形成すると共に、 他方を、表面粗さ０．３Ｓ〜０．５Ｓのランダムな凹凸
をその動圧摺動面に有する金属材としたことを特徴とす
る軸受装置。1. A rotary shaft is disposed inside the bearing, between the outer peripheral Gawado圧摺dynamic surface of the rotary shaft and the inner circumferential Gawado圧摺dynamic surface of the bearing, to the dynamic圧摺dynamic surface Addition of the provided dynamic pressure generating groove
In a bearing device in which an oil film is formed by pressure to rotatably support the rotating shaft, one of the bearing and the rotating shaft is formed of a sintered oil-impregnated alloy, and the other is formed of a surface roughness of 0. bearing device is characterized in that a metal material having a random unevenness of .3S~0.5S its dynamic pressure sliding surface.
さを、バレル仕上げにより得ることを特徴とする請求項
１記載の軸受装置の製造方法。2. The method of manufacturing a bearing device according to claim 1, wherein the surface roughness of the metal material on the sliding surface for dynamic pressure is obtained by barrel finishing.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP25780093A JP2857304B2 (en) | 1993-09-21 | 1993-09-21 | Bearing device and method of manufacturing the same |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP25780093A JP2857304B2 (en) | 1993-09-21 | 1993-09-21 | Bearing device and method of manufacturing the same |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH0791448A JPH0791448A (en) | 1995-04-04 |
| JP2857304B2 true JP2857304B2 (en) | 1999-02-17 |
Family
ID=17311288
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP25780093A Expired - Lifetime JP2857304B2 (en) | 1993-09-21 | 1993-09-21 | Bearing device and method of manufacturing the same |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2857304B2 (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US7021829B2 (en) | 2003-07-22 | 2006-04-04 | Nidec Corporation | Fluid-dynamic-pressure bearing, spindle motor furnished with the fluid-dynamic-pressure bearing, method of manufacturing rotor assembly applied in the spindle motor, and recording-disk drive furnished with the spindle motor |
| US7866047B2 (en) | 2005-03-18 | 2011-01-11 | Nidec Corporation | Sleeve-unit manufacturing method |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5941646A (en) * | 1996-12-25 | 1999-08-24 | Ntn Corporation | Hydrodynamic type porous oil-impregnated bearing and bearing device |
| GB2322915B (en) | 1997-03-06 | 2001-06-06 | Ntn Toyo Bearing Co Ltd | Hydrodynamic type porous oil-impregnated bearing |
| US6712514B2 (en) * | 2000-08-23 | 2004-03-30 | Ntn Corporation | Hydrodynamic bearing unit |
| JP2002339952A (en) | 2001-05-16 | 2002-11-27 | Sankyo Seiki Mfg Co Ltd | Oil dynamic pressure bearing device, and manufacturing method therefor |
-
1993
- 1993-09-21 JP JP25780093A patent/JP2857304B2/en not_active Expired - Lifetime
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US7021829B2 (en) | 2003-07-22 | 2006-04-04 | Nidec Corporation | Fluid-dynamic-pressure bearing, spindle motor furnished with the fluid-dynamic-pressure bearing, method of manufacturing rotor assembly applied in the spindle motor, and recording-disk drive furnished with the spindle motor |
| US7866047B2 (en) | 2005-03-18 | 2011-01-11 | Nidec Corporation | Sleeve-unit manufacturing method |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH0791448A (en) | 1995-04-04 |
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