JP2001248635A - Dynamic pressure fluid bearing device - Google Patents
Dynamic pressure fluid bearing deviceInfo
- Publication number
- JP2001248635A JP2001248635A JP2000058058A JP2000058058A JP2001248635A JP 2001248635 A JP2001248635 A JP 2001248635A JP 2000058058 A JP2000058058 A JP 2000058058A JP 2000058058 A JP2000058058 A JP 2000058058A JP 2001248635 A JP2001248635 A JP 2001248635A
- Authority
- JP
- Japan
- Prior art keywords
- dynamic pressure
- bearing
- pressure generating
- thrust
- groove
- 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.)
- Granted
Links
Landscapes
- Sliding-Contact Bearings (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は動圧流体軸受装置に
関するものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a hydrodynamic bearing device.
【０００２】[0002]
【従来の技術】ハードディスク等の高速スピンドルモー
タには、一方が他方に対して回転自在に支持された軸体
と軸受体との間に流体を充填した動圧流体軸受装置が使
用されている。2. Description of the Related Art A high-speed spindle motor such as a hard disk uses a hydrodynamic fluid bearing device in which a fluid is filled between a shaft body and a bearing body, one of which is rotatably supported with respect to the other.
【０００３】図１５は、従来の動圧流体軸受装置１ｅを
示す。シャフト２にスラストフランジ３が固定されて軸
体４が形成され、固定軸としてのシャフト２に回転自在
に支持されたスリーブ５の一端側にはスラストプレート
６が取り付けられ軸受体７が形成されている。FIG. 15 shows a conventional hydrodynamic bearing device 1e. A thrust flange 3 is fixed to the shaft 2 to form a shaft 4, and a thrust plate 6 is attached to one end of a sleeve 5 rotatably supported by the shaft 2 as a fixed shaft, and a bearing 7 is formed. I have.
【０００４】シャフト２とスリーブ５の内周面との間
隙、スリーブ５とスラストフランジ３およびスラストプ
レート６との間隙には潤滑油８が充填されている。シャ
フト２の外周面には上側とスラストフランジ３の側にへ
リングボーン形状の動圧発生溝９ａが形成され、ラジア
ル軸受部が構成される。また、スラストフランジ３の両
面にはへリングボーン形状の動圧発生溝９ｂが形成さ
れ、スラスト軸受部が構成される。A gap between the shaft 2 and the inner peripheral surface of the sleeve 5 and a gap between the sleeve 5 and the thrust flange 3 and the thrust plate 6 are filled with a lubricating oil 8. On the outer peripheral surface of the shaft 2, a herringbone-shaped dynamic pressure generating groove 9a is formed on the upper side and on the side of the thrust flange 3, and a radial bearing portion is configured. A herringbone-shaped dynamic pressure generating groove 9b is formed on both surfaces of the thrust flange 3 to constitute a thrust bearing portion.
【０００５】この動圧流体軸受装置１ｅでは、軸受体７
が回転すると動圧発生溝９ａ，９ｂが潤滑油８をポンピ
ングするため圧力が高まり、軸体４と軸受体７とが非接
触で支持されラジアル軸受とスラスト軸受の機能が付与
される。In the hydrodynamic bearing device 1e, the bearing body 7
When the rotor rotates, the dynamic pressure generating grooves 9a and 9b pump the lubricating oil 8 to increase the pressure, and the shaft body 4 and the bearing body 7 are supported in a non-contact manner, thereby providing the function of a radial bearing and a thrust bearing.
【０００６】[0006]
【発明が解決しようとする課題】しかしながら上記のよ
うな動圧流体軸受装置１ｅでは、ラジアル軸受部とスラ
スト軸受部の連結部１０において、潤滑油８がラジアル
軸受部のへリングボーン溝９ａとスラスト軸受部のへリ
ングボーン溝９ｂのポンピング作用により引っ張られる
ため負圧が発生する。その結果、ラジアル軸受部とスラ
スト軸受部に発生する動圧力が低くなり、圧力損失が発
生する。However, in the above-described hydrodynamic bearing device 1e, in the connecting portion 10 between the radial bearing portion and the thrust bearing portion, the lubricating oil 8 is supplied to the herringbone groove 9a of the radial bearing portion and the thrust. Negative pressure is generated because the bearing portion is pulled by the pumping action of the herringbone groove 9b. As a result, the dynamic pressure generated in the radial bearing portion and the thrust bearing portion decreases, and a pressure loss occurs.
【０００７】また、軸体４や軸受体７の偏心や傾き等に
よるラジアル軸受部とスラスト軸受部の圧力変動が互い
に影響し合い、スラストフランジ３が不安定になるとい
う問題がある。Further, there is a problem that pressure fluctuations in the radial bearing portion and the thrust bearing portion due to eccentricity and inclination of the shaft body 4 and the bearing body 7 affect each other, and the thrust flange 3 becomes unstable.
【０００８】さらに、スラストフランジ３に形成された
動圧発生溝９ｂの外周側あるいは内周側ではポンピング
作用により負圧が発生して軸受剛性が低下し、軸受の損
失となるという問題がある。Further, there is a problem that a negative pressure is generated due to the pumping action on the outer peripheral side or the inner peripheral side of the dynamic pressure generating groove 9b formed in the thrust flange 3 and the rigidity of the bearing is reduced, resulting in loss of the bearing.
【０００９】本発明は前記問題点を解決し、負圧の発生
を抑え、軸受剛性の低下を低減できる動圧流体軸受装置
を提供することを目的とする。SUMMARY OF THE INVENTION It is an object of the present invention to solve the above-mentioned problems and to provide a hydrodynamic bearing device capable of suppressing generation of a negative pressure and reducing a decrease in bearing rigidity.
【００１０】[0010]
【課題を解決するための手段】本発明の動圧流体軸受装
置は、負圧の発生を低減する環状の切り欠き空間を設け
たことを特徴とする。The hydrodynamic bearing device according to the present invention is characterized in that an annular cut-out space for reducing generation of negative pressure is provided.
【００１１】この本発明によると、負圧の発生による動
圧軸受の損失を緩和できる。According to the present invention, the loss of the dynamic pressure bearing due to the generation of the negative pressure can be reduced.
【００１２】[0012]
【発明の実施の形態】本発明の請求項１記載の動圧流体
軸受装置は、一方が他方に対して回転自在に支持された
軸体と軸受体との間に流体を充填した動圧流体軸受装置
であって、軸体とこの軸体と対向する前記軸受体の側の
少なくとも何れかの面に動圧発生溝を形成してラジアル
軸受部を設け、軸体の側に設けられたスラストフランジ
とこのスラストフランジと対向する前記軸受体の側の面
の少なくともいずれかに動圧発生溝を形成してスラスト
軸受部を設けるとともに、前記ラジアル軸受部と前記ス
ラスト軸受部との連結部分の軸体側に環状の切り欠き空
間を形成したことを特徴とする。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A hydrodynamic bearing device according to a first aspect of the present invention is a hydrodynamic fluid in which a fluid is filled between a shaft body and a bearing body, one of which is rotatably supported with respect to the other. A bearing device, wherein a radial bearing portion is provided by forming a dynamic pressure generating groove on at least one surface of a shaft body and the bearing body facing the shaft body, and a thrust provided on a shaft body side. A thrust bearing portion is provided by forming a dynamic pressure generating groove in at least one of a flange and a surface of the bearing body facing the thrust flange, and a shaft of a connection portion between the radial bearing portion and the thrust bearing portion is provided. An annular cutout space is formed on the body side.
【００１３】この構成によると、ラジアル軸受部とスラ
スト軸受部の連結部において、ラジアル軸受部のへリン
グボーン溝と、スラスト軸受部のへリングボーン溝のポ
ンピング作用により発生する負圧を緩和して動圧軸受の
損失を低減できるとともに、圧力変動によるラジアル軸
受部とスラスト軸受部の互いの影響を抑制できる。According to this structure, at the connecting portion between the radial bearing and the thrust bearing, the negative pressure generated by the pumping action of the herringbone groove of the radial bearing and the herringbone groove of the thrust bearing is reduced. The loss of the dynamic pressure bearing can be reduced, and the mutual influence of the radial bearing and the thrust bearing due to pressure fluctuation can be suppressed.
【００１４】本発明の請求項２記載の動圧流体軸受装置
は、請求項１において、前記環状の切り欠き空間を軸体
と軸受体の両方の側に形成したことを特徴とする。本発
明の請求項３記載の動圧流体軸受装置は、請求項１また
は請求項２において、前記環状の切り欠き空間を軸と前
記スラストフランジの少なくとも一方に形成したことを
特徴とする。According to a second aspect of the present invention, in the hydrodynamic bearing device according to the first aspect, the annular cutout space is formed on both sides of the shaft body and the bearing body. According to a third aspect of the present invention, in the hydrodynamic bearing device according to the first or second aspect, the annular cutout space is formed in at least one of a shaft and the thrust flange.
【００１５】本発明の請求項４記載の動圧流体軸受装置
は、請求項１〜請求項３の何れかにおいて、ラジアル軸
受部の動圧発生溝がヘリングボーン溝またはラジアル方
向に隣接する溝角度が逆方向になるよう配置されたスパ
イラル溝であることを特徴とする。According to a fourth aspect of the present invention, in the hydrodynamic bearing device according to any one of the first to third aspects, the dynamic pressure generating groove of the radial bearing portion is a herringbone groove or a groove angle adjacent in the radial direction. Are spiral grooves arranged in the opposite direction.
【００１６】本発明の請求項５記載の動圧流体軸受装置
は、請求項１〜請求項３の何れかにおいて、スラスト軸
受部の動圧発生溝がヘリングボーン溝またはポンプイン
タイプのスパイラル溝であることを特徴とする。According to a fifth aspect of the present invention, in the hydrodynamic bearing device according to any one of the first to third aspects, the dynamic pressure generating groove of the thrust bearing portion is a herringbone groove or a pump-in type spiral groove. There is a feature.
【００１７】本発明の請求項６記載の動圧流体軸受装置
は、請求項１〜請求項５のいずれかにおいて、ラジアル
方向に沿った断面における前記環状の切り欠き空間の占
める合計面積ａと軸体の軸半径ｒとがａ≧０．０１×ｒ
2であることを特徴とする。According to a sixth aspect of the present invention, there is provided a hydrodynamic bearing device according to any one of the first to fifth aspects, wherein a total area a occupied by the annular cutout space and a shaft in a cross section along a radial direction are provided. The body's axial radius r is a ≧ 0.01 × r
It is characterized by being 2 .
【００１８】この構成によると、ラジアル軸受部とスラ
スト軸受部の連結部に発生する負圧を１０％以上解消し
て動圧軸受の損失を低減でき、ラジアル軸受部とスラス
ト軸受部の圧力変動が互いに影響し合うのを防止でき
る。According to this configuration, the negative pressure generated at the connecting portion between the radial bearing portion and the thrust bearing portion can be eliminated by 10% or more to reduce the loss of the dynamic pressure bearing, and the pressure fluctuation between the radial bearing portion and the thrust bearing portion can be reduced. They can be prevented from affecting each other.
【００１９】本発明の請求項７記載の動圧流体軸受装置
は、請求項１〜請求項５のいずれかにおいて、前記環状
の切り欠き空間と動圧発生溝が軸体または軸受体の側に
あり、前記環状の切り欠き空間の最大深さが前記動圧発
生溝の溝深さより深く、前記動圧発生溝の端部に前記環
状の切り欠き空間が当接して前記動圧発生溝と前記環状
の切り欠き空間とが連結し、ラジアル方向に沿った断面
における前記環状の切り欠き空間の占める合計面積ａと
軸体の軸半径ｒとがａ≧０．００５×ｒ2であることを
特徴とする。According to a seventh aspect of the present invention, in the hydrodynamic bearing device according to any one of the first to fifth aspects, the annular cutout space and the dynamic pressure generating groove are provided on a shaft body or a bearing body side. The maximum depth of the annular notch space is deeper than the groove depth of the dynamic pressure generating groove, and the annular notch space abuts on an end of the dynamic pressure generating groove, and the dynamic pressure generating groove and An annular notch space is connected, and a total area a occupied by the annular notch space in a cross section along the radial direction and a shaft radius r of the shaft body are a ≧ 0.005 × r 2. And
【００２０】この構成によると、ラジアル軸受部とスラ
スト軸受部の連結部に発生する負圧を５０％以上低減し
て動圧軸受の損失を少なくでき、ラジアル軸受部とスラ
スト軸受部の圧力変動が互いに影響し合うのを低減でき
る。According to this structure, the negative pressure generated at the connecting portion between the radial bearing portion and the thrust bearing portion can be reduced by 50% or more to reduce the loss of the dynamic pressure bearing, and the pressure fluctuation between the radial bearing portion and the thrust bearing portion can be reduced. The influence of each other can be reduced.
【００２１】本発明の請求項８記載の動圧流体軸受装置
は、一方が他方に対して回転自在に支持されたスラスト
フランジと軸受体との間に潤滑流体を充填した動圧流体
軸受装置であって、スラストフランジと軸受体の少なく
とも何れかに形成された動圧発生溝の外周半径が前記ス
ラストスラストフランジの外周半径よりも小さい場合
に、前記動圧発生溝の外周端部に当接した環状の切り欠
き空間を形成し、前記環状の切り欠き空間の最大深さを
前記動圧発生溝よりも深くするとともに、ラジアル方向
に沿った断面における前記環状の切り欠き空間の占める
合計面積ａと前記動圧発生溝の外周半径ｒとがａ≧０．
００２５×ｒ2であることを特徴とする。A hydrodynamic bearing device according to claim 8 of the present invention is a hydrodynamic bearing device in which lubricating fluid is filled between a bearing and a thrust flange rotatably supported on one side with respect to the other. When the outer peripheral radius of the dynamic pressure generating groove formed on at least one of the thrust flange and the bearing body is smaller than the outer peripheral radius of the thrust thrust flange, the dynamic pressure generating groove abuts on the outer peripheral end of the dynamic pressure generating groove. An annular notch space is formed, the maximum depth of the annular notch space is made deeper than the dynamic pressure generating groove, and the total area a occupied by the annular notch space in a cross section along the radial direction is When the outer peripheral radius r of the dynamic pressure generating groove is a ≧ 0.
0025 × r 2 .
【００２２】この構成によると、へリングボーン溝の外
周端部に発生する負圧を７０％以上解消して動圧軸受の
損失を低減できる。本発明の請求項９記載の動圧流体軸
受装置は、一方が他方に対して回転自在に支持されたス
ラストフランジと軸受体との間に潤滑流体を充填した動
圧流体軸受装置であって、スラストフランジと軸受体の
少なくとも何れかに形成された動圧発生溝の内周周端部
に当接した環状の切り欠き空間を形成し、前記環状の切
り欠き空間の最大深さを前記動圧発生溝の深さよりも深
くするとともに、ラジアル方向に沿った断面における前
記環状の切り欠き空間の占める合計面積ａと前記動圧発
生溝の内周半径ｒとがａ≧０．００２５×ｒ2であるこ
とを特徴とする。According to this configuration, the negative pressure generated at the outer peripheral end of the herringbone groove is eliminated by 70% or more, and the loss of the dynamic pressure bearing can be reduced. The hydrodynamic bearing device according to claim 9 of the present invention is a hydrodynamic bearing device in which lubricating fluid is filled between a bearing body and a thrust flange rotatably supported on one side, An annular notch space is formed in contact with the inner peripheral end of a dynamic pressure generating groove formed in at least one of the thrust flange and the bearing body, and the maximum depth of the annular notch space is determined by the dynamic pressure. While the depth is greater than the depth of the generation groove, the total area a occupied by the annular cutout space in the cross section along the radial direction and the inner peripheral radius r of the dynamic pressure generation groove are a ≧ 0.0025 × r 2 . There is a feature.
【００２３】この構成によると、スパイラル溝の内周端
部に発生する負圧を７０％以上解消できる。本発明の請
求項１０記載の動圧流体軸受装置は、請求項８または請
求項９において、動圧発生溝がヘリングボーン溝または
ポンプインタイプのスパイラル溝であることを特徴とす
る。According to this configuration, the negative pressure generated at the inner peripheral end of the spiral groove can be eliminated by 70% or more. According to a tenth aspect of the present invention, in the hydrodynamic bearing device according to the eighth or ninth aspect, the dynamic pressure generating groove is a herringbone groove or a pump-in type spiral groove.
【００２４】以下、本発明の実施例について、図１〜図
１４を用いて説明する。 （実施の形態１）図１〜図８は、本発明の（実施の形態
１）を示す。An embodiment of the present invention will be described below with reference to FIGS. (Embodiment 1) FIGS. 1 to 8 show (Embodiment 1) of the present invention.
【００２５】この（実施の形態１）では、図１に示す動
圧流体軸受装置１ａに、ラジアル軸受部とスラスト軸受
部の連結部１０の負圧の発生を低減する環状の切り欠き
空間１１ａ〜１１ｃを設けた点で従来例とは異なる。In this (Embodiment 1), in the hydrodynamic bearing device 1a shown in FIG. 1, annular cut-out spaces 11a to 11g for reducing generation of negative pressure in the connecting portion 10 between the radial bearing portion and the thrust bearing portion. 11c is different from the conventional example in that it is provided.
【００２６】詳細には、動圧流体軸受装置１ａは、シャ
フト２にスラストフランジ３が固定された軸体４によっ
てスリーブ５とスラストプレート６とからなる軸受体７
が回転自在に支持されている。スラストフランジ３は圧
入等によって固定軸としてのシャフト２の外周部に固定
され、スラストプレート６は接着等によりスリーブ５の
下端部に固定されている。More specifically, the hydrodynamic bearing device 1a comprises a bearing member 7 composed of a sleeve 5 and a thrust plate 6 by a shaft 4 having a thrust flange 3 fixed to a shaft 2.
Are rotatably supported. The thrust flange 3 is fixed to the outer peripheral portion of the shaft 2 as a fixed shaft by press fitting or the like, and the thrust plate 6 is fixed to the lower end of the sleeve 5 by bonding or the like.
【００２７】シャフト２とスリーブ５の内周面との間
隙、スリーブ５とスラストフランジ３およびスラストプ
レート６との間隙には、流体として潤滑油８が充填され
ている。The gap between the shaft 2 and the inner peripheral surface of the sleeve 5 and the gap between the sleeve 5 and the thrust flange 3 and the thrust plate 6 are filled with lubricating oil 8 as a fluid.
【００２８】スリーブ５の内周面にはヘリングボーン形
状の動圧発生溝９ａが形成されてラジアル軸受部が構成
される。一方、円板状のスラストフランジ３には、スリ
ーブ５およびスラストプレート６に対向する面に、図２
に示すようにヘリングボーン形状の動圧発生溝９ｂが形
成され、スラスト軸受部が構成される。動圧発生溝９ｂ
の内周部にある環状の溝は、スラストフランジ３に形成
された環状の切り欠き空間１１ｃである。On the inner peripheral surface of the sleeve 5, a herringbone-shaped dynamic pressure generating groove 9a is formed to constitute a radial bearing portion. On the other hand, the disk-shaped thrust flange 3 has a surface facing the sleeve 5 and the thrust plate 6 as shown in FIG.
The herringbone-shaped dynamic pressure generating groove 9b is formed as shown in FIG. Dynamic pressure generating groove 9b
An annular groove formed in the inner peripheral portion of the groove is an annular cutout space 11c formed in the thrust flange 3.
【００２９】ラジアル軸受部とスラスト軸受部との連結
部１０には、軸体４側であるシャフト２とスラストフラ
ンジ３、また軸受体７側のスリーブ５の内周面の全周に
わたって環状の切り欠き空間１１ａ〜１１ｃが形成され
ている。In the connecting portion 10 between the radial bearing portion and the thrust bearing portion, an annular cut is formed over the entire circumference of the shaft 2 and the thrust flange 3 on the shaft body 4 side and the inner peripheral surface of the sleeve 5 on the bearing body 7 side. Notched spaces 11a to 11c are formed.
【００３０】このように構成された動圧流体軸受装置１
ａでは、軸体４に対して軸受体７が回転するとヘリング
ボーン形状の動圧発生溝９ａ，９ｂによって動圧が発生
し、軸体４と軸受体７とが非接触で支持される。このと
きラジアル軸受部とスラスト軸受部との連結部１０に
は、上述のように環状の切り欠き空間１１ａ〜１１ｃが
形成されているため、連結部１０に発生する負圧を緩和
して動圧の損失を抑制できる。The hydrodynamic bearing device 1 thus configured
In a, when the bearing 7 rotates with respect to the shaft 4, dynamic pressure is generated by the herringbone-shaped dynamic pressure generating grooves 9a and 9b, and the shaft 4 and the bearing 7 are supported in a non-contact manner. At this time, the annular cutout spaces 11a to 11c are formed in the connecting portion 10 between the radial bearing portion and the thrust bearing portion as described above, so that the negative pressure generated in the connecting portion 10 is relieved and the dynamic pressure is reduced. Loss can be suppressed.
【００３１】以下、具体例に基づき環状の切り欠き空間
１１ａ〜１１ｃとラジアル軸受部とスラスト軸受部との
連結部１０に発生する負圧との関係を説明する。上記の
ように構成された動圧流体発生装置１ａにおいて、シャ
フト２の半径を０．５ｍｍから３ｍｍ、スラストフラン
ジ３の半径をシャフト２の半径の２倍から３倍、ラジア
ル軸受部におけるシャフト２とスリーブ５内周面との間
隙を３μｍから１０μｍ、スラスト軸受部のスリーブ５
とスラストフランジ３との間隙を３μｍから１０μｍに
変化させるとともに、動圧発生溝９ａ，９ｂの溝角度、
偏心率を変化させ、それぞれの場合における環状の切り
欠き空間１１ａ〜１１ｃの断面積と断面形状を変化させ
た。なお、断面形状は四角形と三角形に変化させた。Hereinafter, the relationship between the annular cut-out spaces 11a to 11c and the negative pressure generated in the connecting portion 10 between the radial bearing portion and the thrust bearing portion will be described based on a specific example. In the hydrodynamic fluid generator 1a configured as described above, the radius of the shaft 2 is 0.5 mm to 3 mm, the radius of the thrust flange 3 is 2 to 3 times the radius of the shaft 2, and the shaft 2 in the radial bearing portion. The gap between the inner peripheral surface of the sleeve 5 and the sleeve 5 of the thrust bearing portion is 3 μm to 10 μm.
Of the gap between the dynamic pressure generating grooves 9a and 9b,
The eccentricity was changed, and the cross-sectional areas and cross-sectional shapes of the annular cutout spaces 11a to 11c in each case were changed. The cross-sectional shape was changed into a square and a triangle.
【００３２】そして、ラジアル方向に沿った断面におけ
る環状の切り欠き空間１１ａ〜１１ｃの占める断面積の
合計面積をａ、シャフト２の半径をｒとしたときのａ／
ｒ2と、負圧の減少比との関係を求めた。The total area of the cross-sectional areas occupied by the annular cutout spaces 11a to 11c in the cross section along the radial direction is represented by a, and when the radius of the shaft 2 is represented by r, a /
The relationship between r 2 and the negative pressure reduction ratio was determined.
【００３３】なお、負圧の減少比とは、環状の切り欠き
空間１１ａ〜１１ｃが形成されていない場合、すなわち
ａ／ｒ2＝０のときのラジアル軸受部とスラスト軸受部
の連結部１０の負圧を１として、環状の切り欠き空間１
１ａ〜１１ｃが形成された場合の負圧の減少を求めたも
のである。The reduction ratio of the negative pressure means that the annular cut-out spaces 11a to 11c are not formed, that is, the connecting portion 10 of the radial bearing and the thrust bearing when a / r 2 = 0. Assuming that the negative pressure is 1, the annular cutout space 1
This is to determine a decrease in negative pressure when 1a to 11c are formed.
【００３４】得られた解析結果を図３に示す。ａ／ｒ2
の値の変化に応じて、負圧はほぼ斜線部Ａの範囲で変化
した。ところで、上記のようにラジアル軸受部とスラス
ト軸受部の連結部１０に環状の切り欠き空間１１ａ〜１
１ｃが形成されていない場合には、例えばスリーブ５が
偏心するとラジアル軸受部に圧力変動が生じる。ラジア
ル軸受部の圧力変動が生じると、スラスト軸受部にも影
響を与えスラスト軸受部にも圧力変動が生じる。FIG. 3 shows the obtained analysis results. a / r 2
The negative pressure changed substantially in the range of the hatched area A in accordance with the change in the value of. By the way, as described above, the annular cut-out spaces 11a to 11a are formed in the connection portion 10 between the radial bearing portion and the thrust bearing portion.
When 1c is not formed, for example, when the sleeve 5 is eccentric, pressure fluctuation occurs in the radial bearing portion. When the pressure fluctuation of the radial bearing part occurs, it also affects the thrust bearing part, and the pressure fluctuation also occurs in the thrust bearing part.
【００３５】そこで、ラジアル軸受部、例えばスリーブ
５に偏心が生じた際の圧力変動がスラスト軸受部へ与え
る影響を調べるために、環状の切り欠き空間１１ａ〜１
１ｃの形状、および軸受形状を上記と同様に変化させて
解析を行った。Therefore, in order to examine the effect of pressure fluctuations on the radial bearing portion, for example, the sleeve 5 when eccentricity occurs, on the thrust bearing portion, the annular cut-out spaces 11a to 11a-1 are formed.
The analysis was performed by changing the shape of 1c and the bearing shape in the same manner as described above.
【００３６】ここでは、環状の切り欠き空間１１ａ〜１
１ｃが形成されていない場合すなわちａ／ｒ2＝０のと
きにラジアル軸受部が偏心した場合に、スラスト軸受部
の最大圧力と最小圧力の差を１とし、偏心していない場
合の最大圧力と最小圧力の差を０として、環状の切り欠
き空間１１ａ〜１１ｃが形成された場合の圧力差を求め
た。Here, the annular cutout spaces 11a to 11a
When 1c is not formed, that is, when the radial bearing is eccentric when a / r 2 = 0, the difference between the maximum pressure and the minimum pressure of the thrust bearing is set to 1, and the maximum pressure and the minimum when the eccentric is not eccentric. Assuming that the pressure difference is 0, the pressure difference when the annular cutout spaces 11a to 11c were formed was obtained.
【００３７】得られた解析結果を図４に示す。このとき
の圧力の影響は、ほぼ斜線部Ｃの範囲で変化した。以
上、図３，図４より、ラジアル方向に沿った断面におけ
る環状の切り欠き空間の占める合計面積ａと軸体の軸半
径ｒとをａ≧０．０１×ｒ2と設定することで、負圧を
１０％以上解消でき、さらに、ラジアル軸受部とスラス
ト軸受部の圧力変動が互いに影響する度合いを１５％以
下にできる。FIG. 4 shows the obtained analysis results. The influence of the pressure at this time changed substantially in the range of the hatched portion C. As described above, according to FIGS. 3 and 4, by setting the total area a occupied by the annular cutout space and the axial radius r of the shaft body in the cross section along the radial direction as a ≧ 0.01 × r 2 , the negative value is obtained. The pressure can be reduced by 10% or more, and the degree to which the pressure fluctuations of the radial bearing and the thrust bearing affect each other can be reduced to 15% or less.
【００３８】また、図５に示すように、上記と同様に構
成された動圧流体軸受装置１ｂにおいて、環状の切り欠
き空間１１ａと動圧発生溝９ｃの下端とを当接させ、動
圧発生溝９ｃと環状の切り欠き空間１１ａ〜１１ｃを連
結させた形状とするとともに、環状の切り欠き空間１１
ａ〜１１ｃの最大深さを動圧発生溝９ｃよりも深くする
よう構成すると、さらにラジアル軸受部とスラスト軸受
部の連結部１０における負圧の発生を低減できる。As shown in FIG. 5, in the hydrodynamic bearing device 1b having the same structure as described above, the annular cutout space 11a and the lower end of the hydrodynamic groove 9c are brought into contact with each other to generate the hydrodynamic pressure. The groove 9c is connected to the annular cutout spaces 11a to 11c, and the annular cutout space 11a is formed.
When the maximum depth of a to 11c is set to be greater than the dynamic pressure generating groove 9c, the generation of negative pressure in the connecting portion 10 between the radial bearing portion and the thrust bearing portion can be further reduced.
【００３９】ここでは、動圧発生溝９ｃの深さを１０μ
ｍ、環状の切り欠き空間１１ａの最大の深さを１０μｍ
〜１００μｍまで変化させて、上記と同様にａ／ｒ2の
値と負圧の減少比とを測定した。Here, the depth of the dynamic pressure generating groove 9c is set to 10 μm.
m, the maximum depth of the annular cutout space 11a is 10 μm
The value of a / r 2 and the decrease ratio of the negative pressure were measured in the same manner as described above, while changing the thickness to 100 μm.
【００４０】この動圧流体発生装置１ｂによるａ／ｒ2
の値の変化に応じて負圧は、ほぼ斜線部Ｂの範囲で変化
した。また、ａ／ｒ2の値の変化と最大圧力と最小圧力
の差は、上記図４とほぼ同様になった。A / r 2 by the dynamic pressure fluid generator 1b
The negative pressure changed substantially in the range of the hatched portion B in accordance with the change in the value of. The change in the value of a / r 2 and the difference between the maximum pressure and the minimum pressure were almost the same as in FIG.
【００４１】図３の斜線部Ｂ、図４の解析結果より、ａ
≧０．００５×ｒ2に設定すると、負圧が５０％以上解
消できる。このように、ラジアル軸受部とスラスト軸受
部の連結部１０に環状の切り欠き空間１１ａ〜１１ｃを
設けることで、ラジアル軸受部とスラスト軸受部の連結
部に発生する負圧を低減でき、また、軸の偏心や傾きな
どによるラジアル軸受部とスラスト軸受部の互いの圧力
変動の影響を低減して、軸受剛性の低下を低減できる。From the hatched portion B in FIG. 3 and the analysis result in FIG.
By setting ≧ 0.005 × r 2 , the negative pressure can be eliminated by 50% or more. As described above, by providing the annular cutout spaces 11a to 11c in the connecting portion 10 between the radial bearing portion and the thrust bearing portion, the negative pressure generated in the connecting portion between the radial bearing portion and the thrust bearing portion can be reduced. The effect of mutual pressure fluctuations of the radial bearing portion and the thrust bearing portion due to the eccentricity or inclination of the shaft can be reduced, and a decrease in bearing rigidity can be reduced.
【００４２】なお、上記説明では、環状の切り欠き空間
１１ａ〜１１ｃを、ラジアル軸受部とスラスト軸受部の
連結部１０の軸体４と軸受体７の両方の側に形成した
が、いずれか一方のみに形成してもよい。また、シャフ
ト２とスラストフランジ３の両方の側に環状の切り欠き
空間を形成したが、いずれか一方であってもよい。ま
た、環状の切り欠き空間のラジアル軸方向への断面形状
も特に限定されるものではなく、任意の形状でよい。In the above description, the annular cutout spaces 11a to 11c are formed on both the shaft 4 and the bearing 7 of the connecting portion 10 between the radial bearing and the thrust bearing. It may be formed only. In addition, although the annular cutout space is formed on both sides of the shaft 2 and the thrust flange 3, either one may be provided. Further, the cross-sectional shape of the annular cutout space in the radial axis direction is not particularly limited, and may be any shape.
【００４３】また、上記説明では、ラジアル軸受部の動
圧発生溝９ａ，９ｃをヘリングボーン形状としたが、図
６に示すようにラジアル方向に隣接する溝角度が逆方向
になるよう配置された一対のスパイラル溝１２ａ，１２
ｂを対向させたものであっても同様の効果が得られる。In the above description, the dynamic pressure generating grooves 9a and 9c of the radial bearing portion have a herringbone shape. However, as shown in FIG. 6, the grooves are arranged so that adjacent groove angles in the radial direction are opposite to each other. A pair of spiral grooves 12a, 12
The same effect can be obtained even when b faces each other.
【００４４】また、上記説明では、スラスト軸受部の動
圧発生溝９ｂの形状をヘリングボーン形状としたが、図
７に示すように、ポンプインタイプのスパイラル溝１３
としても同様の効果が得られる。なお、この図７では、
スラストフランジ３のスパイラル溝１３の外周部に環状
の切り欠き空間１１ｄが形成された例を示している。こ
のように、スラストフランジ３に形成される環状の切り
欠き空間は動圧発生溝の内周部、外周部のいずれに形成
されてもよく、両方の側に形成されてもよい。Further, in the above description, the shape of the dynamic pressure generating groove 9b of the thrust bearing portion is a herringbone shape. However, as shown in FIG.
The same effect can be obtained. In FIG. 7,
An example in which an annular cutout space 11d is formed in the outer peripheral portion of the spiral groove 13 of the thrust flange 3 is shown. As described above, the annular cutout space formed in the thrust flange 3 may be formed on either the inner peripheral portion or the outer peripheral portion of the dynamic pressure generating groove, or may be formed on both sides.
【００４５】また、シャフト２の下側にスラストフラン
ジ３が形成された動圧発生装置１ａ，１ｂだけでなく、
図８に示すように、シャフト２ａの上端に動圧発生溝９
ｅが形成されたスラストフランジ３ａが固定された動圧
流体発生装置１ｃであっても同様の効果が得られる。こ
こで、５ａはスリーブ、６ａはスラストプレート、９ｄ
はヘリングボーン形状の動圧発生溝である。In addition to the dynamic pressure generators 1a and 1b in which the thrust flange 3 is formed below the shaft 2,
As shown in FIG. 8, a dynamic pressure generating groove 9 is formed at the upper end of the shaft 2a.
The same effect can be obtained even with the hydrodynamic fluid generator 1c in which the thrust flange 3a on which e is formed is fixed. Here, 5a is a sleeve, 6a is a thrust plate, 9d
Is a herringbone-shaped dynamic pressure generating groove.
【００４６】（実施の形態２）図９〜図１４は、本発明
の（実施の形態２）を示す。この（実施の形態２）で
は、スラスト軸受部の構成について説明する。(Embodiment 2) FIGS. 9 to 14 show (Embodiment 2) of the present invention. In this (Embodiment 2), the configuration of the thrust bearing will be described.
【００４７】図９に示すように、一方が他方に対して回
転自在に支持されたスラスト軸受部を有する動圧流体軸
受装置１ｄにおいて、スラストプレート６ｂにスリーブ
５ｂが接着等により固定されて構成された軸受体と、ス
ラストフランジ３ｂとが対向して配置されている。As shown in FIG. 9, in a hydrodynamic bearing device 1d having a thrust bearing portion rotatably supported on one side with respect to the other, a sleeve 5b is fixed to a thrust plate 6b by bonding or the like. The bearing body and the thrust flange 3b are arranged to face each other.
【００４８】スラストフランジ３ｂとスリーブ５ｂおよ
びスラストプレート６ｂとの間には、潤滑油８が充填さ
れている。スラストフランジ３ｂのスラストプレート６
ｂとの対向面には、図１０に示すように、ヘリングボー
ン形状の動圧発生溝９ｅが形成されており、動圧発生溝
９ｅの外周端部に接するように環状の切り欠き空間１１
ｅが形成され、動圧発生溝９ｅと環状の切り欠き空間１
１ｅとが連結されている。The space between the thrust flange 3b, the sleeve 5b and the thrust plate 6b is filled with lubricating oil 8. Thrust plate 6 of thrust flange 3b
As shown in FIG. 10, a herringbone-shaped dynamic pressure generating groove 9 e is formed on the surface opposing the groove b, and an annular cutout space 11 is formed so as to contact the outer peripheral end of the dynamic pressure generating groove 9 e.
e is formed, and the dynamic pressure generating groove 9e and the annular cutout space 1 are formed.
1e.
【００４９】ここで、環状の切り欠き空間１１ｅの最大
深さは動圧発生溝９ｅの深さよりも深くすることが好ま
しい。また、この環状の切り欠き空間７７ｅの断面形状
は特に限定されるものではなく任意の形状でよい。Here, it is preferable that the maximum depth of the annular cutout space 11e is larger than the depth of the dynamic pressure generating groove 9e. The sectional shape of the annular cutout space 77e is not particularly limited, and may be any shape.
【００５０】このように構成された動圧流体軸受装置１
ｄでは、スラストフランジ３ｂに対して軸受体が回転す
るとヘリングボーン形状の動圧発生溝９ｅによって動圧
が発生し、スラストフランジ３ｂと軸受体とが非接触で
支持される。このとき、スラストフランジ３ｂには環状
の切り欠き空間１１ｅが形成されているため、スラスト
軸受部における負圧を緩和して動圧の損失を緩和でき
る。The hydrodynamic bearing device 1 thus configured
In d, when the bearing rotates with respect to the thrust flange 3b, a dynamic pressure is generated by the herringbone-shaped dynamic pressure generating groove 9e, and the thrust flange 3b and the bearing are supported in a non-contact manner. At this time, since the annular cutout space 11e is formed in the thrust flange 3b, the negative pressure in the thrust bearing portion can be reduced, and the loss of dynamic pressure can be reduced.
【００５１】以下、具体例に基づき環状の切り欠き空間
１１ｅと負圧との関係を説明する。上記のように構成さ
れた動圧流体発生装置１ｄにおいて、ラジアル方向に沿
った環状の切り欠き空間１１ｅの占める断面積の合計面
積をａ、へリングボーン形状の動圧発生溝１１ｅの外側
半径をｒとしたときのａ／ｒ2と負圧の減少比との関係
を、さまざまな軸受形状、環状の切り欠き空間の形状を
変化させて解析を行った。Hereinafter, the relationship between the annular notch space 11e and the negative pressure will be described based on a specific example. In the hydrodynamic fluid generator 1d configured as described above, the total area of the cross-sectional area occupied by the annular cutout space 11e along the radial direction is a, and the outer radius of the herringbone-shaped hydrodynamic groove 11e is The relationship between a / r 2 and the reduction ratio of the negative pressure when r was analyzed by changing various bearing shapes and the shape of the annular cutout space.
【００５２】ここでの負圧の減少比とは、環状の切り欠
き空間１１ｅが形成されていない場合すなわちａ／ｒ2
＝０のときの負圧を１として、環状の切り欠き空間１１
ｅが形成された場合の負圧の減少を求めたものである。Here, the negative pressure reduction ratio means that the annular notch space 11e is not formed, that is, a / r 2
Assuming that the negative pressure when = 0 is 1, the annular cutout space 11
This is to determine a decrease in negative pressure when e is formed.
【００５３】得られた解析結果を図１２に示す。ａ／ｒ
2の値の変化に応じた負圧は、ほぼ斜線部Ｄの範囲で変
化した。また、ａ≧０．００２５×ｒ2に設定すること
で負圧を７０％以上解消し、動圧軸受の損失を少なくで
きる。FIG. 12 shows the obtained analysis results. a / r
The negative pressure corresponding to the change in the value of 2 changed almost in the range of the hatched portion D. Further, by setting a ≧ 0.0025 × r 2 , the negative pressure can be eliminated by 70% or more, and the loss of the dynamic pressure bearing can be reduced.
【００５４】なお、上記説明では動圧発生溝９ｅをヘリ
ングボーン形状としたが、図１１に示すように、ポンプ
インタイプのスパイラル溝１３ａとしてもよい。また、
図１３，１４に示すように、動圧発生溝９ｅの内周端部
に接するように環状の切り欠き空間１１ｆを形成しても
よい。Although the dynamic pressure generating groove 9e has a herringbone shape in the above description, it may be a pump-in type spiral groove 13a as shown in FIG. Also,
As shown in FIGS. 13 and 14, an annular cutout space 11f may be formed so as to be in contact with the inner peripheral end of the dynamic pressure generating groove 9e.
【００５５】この場合についても上記と同様に環状の切
り欠き空間４５の断面積をａとし、へリングボーン溝５
４の内側半径をｒとしたて負圧の変化を測定したとこ
ろ、図１２の斜線部Ｄとほぼ同様に変化した。Also in this case, the sectional area of the annular cutout space 45 is set to a, and the herringbone groove 5 is formed.
When the change in negative pressure was measured with the inside radius of r being r, the change was almost the same as the shaded area D in FIG.
【００５６】従って、動圧発生溝９ｅの内周端部に接す
るように環状の切り欠き空間１１ｆを形成した場合にお
いても、ａ≧０．００２５×ｒ2と設定することで負圧
を７０％以上解消でき、動圧軸受の損失を少なくでき
る。Therefore, even when the annular cutout space 11f is formed so as to be in contact with the inner peripheral end of the dynamic pressure generating groove 9e, by setting a ≧ 0.0025 × r 2 , the negative pressure is reduced by 70%. Thus, the loss of the dynamic pressure bearing can be reduced.
【００５７】また、上記各実施の形態では、流体として
潤滑油を用いたが、本発明はこれに限定されるものでは
なく、流体として気体、具体的には空気を用いてもよ
い。このような構成とすると、潤滑油を使用する必要が
なくなり、コストダウンが図れる。In each of the above embodiments, lubricating oil is used as the fluid. However, the present invention is not limited to this, and a gas, specifically, air may be used as the fluid. With such a configuration, it is not necessary to use a lubricating oil, and cost can be reduced.
【００５８】[0058]
【発明の効果】以上のように、本発明の動圧流体軸受装
置によれば、ラジアル軸受部とスラスト軸受部の連結部
に環状の切り欠き空間を設けることで、連結部に発生す
る負圧を緩和し、動圧流体軸受の損失を少なくするとと
もに、ラジアル軸受部とスラスト軸受部の圧力変動が互
いに影響し合うのを防止できる。As described above, according to the hydrodynamic bearing device of the present invention, by providing an annular cutout space at the connecting portion between the radial bearing portion and the thrust bearing portion, the negative pressure generated at the connecting portion is reduced. And the loss of the hydrodynamic bearing can be reduced, and the pressure fluctuations of the radial bearing and the thrust bearing can be prevented from affecting each other.
【００５９】また、環状の切り欠き空間を設けること
で、軸体の偏心や傾き等によるラジアル軸受部とスラス
ト軸受部の圧力変動が互いに影響し合うことを低減でき
る。Further, by providing the annular cutout space, it is possible to reduce the influence of the pressure fluctuations of the radial bearing and the thrust bearing caused by the eccentricity or inclination of the shaft body.
【図１】本発明の（実施の形態１）における動圧流体軸
受装置の断面図FIG. 1 is a sectional view of a hydrodynamic bearing device according to a first embodiment of the present invention.
【図２】図１のスラスト軸受部の平面図FIG. 2 is a plan view of the thrust bearing portion of FIG. 1;
【図３】本発明の（実施の形態１）における環状の切り
欠き空間と負圧の減少比との関係を示すグラフFIG. 3 is a graph showing a relationship between an annular cutout space and a negative pressure reduction ratio according to the first embodiment of the present invention.
【図４】本発明の（実施の形態１）における環状の切り
欠き空間と最大圧力と最小圧力の差との関係を示すグラ
フFIG. 4 is a graph showing a relationship between an annular cutout space and a difference between a maximum pressure and a minimum pressure according to the first embodiment of the present invention.
【図５】本発明の（実施の形態１）における図１とは別
の動圧流体軸受装置の断面図FIG. 5 is a sectional view of a hydrodynamic bearing device different from FIG. 1 according to (Embodiment 1) of the present invention;
【図６】本発明の（実施の形態１）における図２とは別
のスラスト軸受部の平面図FIG. 6 is a plan view of a thrust bearing different from FIG. 2 according to the first embodiment of the present invention.
【図７】本発明の（実施の形態１）における図１，図５
とは別の動圧流体軸受装置の断面図FIGS. 1 and 5 in (Embodiment 1) of the present invention.
Sectional view of another hydrodynamic bearing device
【図８】本発明の（実施の形態１）における図１，図５
とは別の動圧流体軸受装置の断面図8 and FIG. 5 in (Embodiment 1) of the present invention.
Sectional view of another hydrodynamic bearing device
【図９】本発明の（実施の形態２）におけるスラスト軸
受部の断面図FIG. 9 is a cross-sectional view of a thrust bearing according to the second embodiment of the present invention.
【図１０】図９のスラストフランジの平面図FIG. 10 is a plan view of the thrust flange of FIG. 9;
【図１１】図９とは別の形状の動圧発生溝を示す平面図FIG. 11 is a plan view showing a dynamic pressure generating groove having a shape different from that of FIG. 9;
【図１２】本発明の（実施の形態２）における環状の切
り欠き空間と最大圧力と最小圧力の差との関係を示すグ
ラフFIG. 12 is a graph showing a relationship between an annular cut-out space and a difference between a maximum pressure and a minimum pressure according to the second embodiment of the present invention.
【図１３】図９とは別の例を示すスラスト軸受部の断面
図FIG. 13 is a sectional view of a thrust bearing portion showing another example different from FIG. 9;
【図１４】図９のスラストフランジの平面図FIG. 14 is a plan view of the thrust flange of FIG. 9;
【図１５】従来の動圧流体軸受装置の断面図FIG. 15 is a sectional view of a conventional hydrodynamic bearing device.
１ａ〜１ｄ 動圧流体発生装置 ２ スリーブ ３ スラストフランジ ４ 軸体 ５ スリーブ ６ スラストプレート ７ 軸受体 ８ 潤滑油 ９ａ〜９ｄ 動圧発生溝 １０ 連結部 １１ａ〜１１ｆ 環状の切り欠き空間 1a to 1d Dynamic pressure fluid generating device 2 Sleeve 3 Thrust flange 4 Shaft 5 Sleeve 6 Thrust plate 7 Bearing 8 Lubricating oil 9a to 9d Dynamic pressure generating groove 10 Connecting portion 11a to 11f Annular notched space
Claims (10)
軸体と軸受体との間に流体を充填した動圧流体軸受装置
であって、 軸体とこの軸体と対向する前記軸受体の側の少なくとも
何れかの面に動圧発生溝を形成してラジアル軸受部を設
け、 軸体の側に設けられたスラストフランジとこのスラスト
フランジと対向する前記軸受体の側の面の少なくともい
ずれかに動圧発生溝を形成してスラスト軸受部を設ける
とともに、 前記ラジアル軸受部と前記スラスト軸受部との連結部分
の軸体側に環状の切り欠き空間を形成した動圧流体軸受
装置。1. A hydrodynamic bearing device in which a fluid is filled between a shaft body rotatably supported on one side and a bearing body, wherein the shaft body and the bearing opposed to the shaft body. A dynamic pressure generating groove is formed on at least one surface on the body side to provide a radial bearing portion, and at least a thrust flange provided on the shaft body side and a surface on the bearing body side facing the thrust flange. A hydrodynamic fluid bearing device in which a thrust bearing portion is provided by forming a dynamic pressure generating groove in one of the grooves and an annular cutout space is formed on a shaft body side of a connection portion between the radial bearing portion and the thrust bearing portion.
両方の側に形成した請求項１記載の動圧流体軸受装置。2. The hydrodynamic bearing device according to claim 1, wherein said annular cut-out space is formed on both sides of the shaft body and the bearing body.
トフランジの少なくとも一方に形成した請求項１または
請求項２記載の動圧流体軸受装置。3. The hydrodynamic bearing device according to claim 1, wherein the annular cutout space is formed in at least one of a shaft and the thrust flange.
ーン溝またはラジアル方向に隣接する溝角度が逆方向に
なるよう配置されたスパイラル溝である請求項１〜請求
項３の何れかに記載の動圧流体軸受装置。4. The dynamic pressure generating groove of the radial bearing portion is a herringbone groove or a spiral groove arranged such that adjacent groove angles in the radial direction are opposite to each other. Hydrodynamic bearing device.
ーン溝またはポンプインタイプのスパイラル溝である請
求項１〜請求項３の何れかに記載の動圧流体軸受装置。5. The hydrodynamic bearing device according to claim 1, wherein the dynamic pressure generating groove of the thrust bearing portion is a herringbone groove or a pump-in type spiral groove.
状の切り欠き空間の占める合計面積ａと軸体の軸半径ｒ
とがａ≧０．０１×ｒ2である請求項１〜請求項５のい
ずれかに記載の動圧流体軸受装置。6. A total area a occupied by said annular cutout space in a cross section along a radial direction and a shaft radius r of a shaft body.
The hydrodynamic bearing device according to claim 1, wherein a ≧ 0.01 × r 2 .
体または軸受体の側にあり、 前記環状の切り欠き空間の最大深さが前記動圧発生溝の
溝深さより深く、前記動圧発生溝の端部に前記環状の切
り欠き空間が当接して前記動圧発生溝と前記環状の切り
欠き空間とが連結し、 ラジアル方向に沿った断面における前記環状の切り欠き
空間の占める合計面積ａと軸体の軸半径ｒとがａ≧０．
００５×ｒ2である請求項１〜請求項５のいずれかに記
載の動圧流体軸受装置。7. The annular cut-out space and the dynamic pressure generating groove are on the side of a shaft or a bearing body, and a maximum depth of the annular cut-out space is deeper than a groove depth of the dynamic pressure generating groove. The annular notch space abuts on the end of the dynamic pressure generating groove, connects the dynamic pressure generating groove and the annular notch space, and occupies the annular notch space in a cross section along the radial direction. When the total area a and the shaft radius r of the shaft body are a ≧ 0.
The hydrodynamic bearing device according to claim 1, wherein 005 × r 2 .
スラストフランジと軸受体との間に潤滑流体を充填した
動圧流体軸受装置であって、 スラストフランジと軸受体の少なくとも何れかに形成さ
れた動圧発生溝の外周半径が前記スラストスラストフラ
ンジの外周半径よりも小さい場合に、前記動圧発生溝の
外周端部に当接した環状の切り欠き空間を形成し、 前記環状の切り欠き空間の最大深さを前記動圧発生溝よ
りも深くするとともに、 ラジアル方向に沿った断面における前記環状の切り欠き
空間の占める合計面積ａと前記動圧発生溝の外周半径ｒ
とがａ≧０．００２５×ｒ2である動圧流体軸受装置。8. A hydrodynamic bearing device in which a lubricating fluid is filled between a thrust flange rotatably supported on one side and a bearing body, wherein at least one of the thrust flange and the bearing body. When the outer peripheral radius of the formed dynamic pressure generating groove is smaller than the outer peripheral radius of the thrust thrust flange, an annular notch space is formed in contact with the outer peripheral end of the dynamic pressure generating groove, and the annular notch is formed. The maximum depth of the notched space is made deeper than the dynamic pressure generating groove, and the total area a occupied by the annular cutout space in the cross section along the radial direction and the outer radius r of the dynamic pressure generating groove
Wherein a ≧ 0.0025 × r 2 .
スラストフランジと軸受体との間に潤滑流体を充填した
動圧流体軸受装置であって、 スラストフランジと軸受体の少なくとも何れかに形成さ
れた動圧発生溝の内周周端部に当接した環状の切り欠き
空間を形成し、 前記環状の切り欠き空間の最大深さを前記動圧発生溝の
深さよりも深くするとともに、 ラジアル方向に沿った断面における前記環状の切り欠き
空間の占める合計面積ａと前記動圧発生溝の内周半径ｒ
とがａ≧０．００２５×ｒ2である動圧流体軸受装置。9. A hydrodynamic bearing device in which a lubricating fluid is filled between a thrust flange rotatably supported on one side and a bearing body, wherein at least one of the thrust flange and the bearing body. Forming an annular notch space in contact with the inner peripheral end of the formed dynamic pressure generating groove, and making the maximum depth of the annular notch space deeper than the depth of the dynamic pressure generating groove, The total area a occupied by the annular cutout space in the cross section along the radial direction and the inner peripheral radius r of the dynamic pressure generating groove
Wherein a ≧ 0.0025 × r 2 .
ンプインタイプのスパイラル溝である請求項８または請
求項９記載の動圧流体軸受装置。10. The hydrodynamic bearing device according to claim 8, wherein the dynamic pressure generating groove is a herringbone groove or a pump-in type spiral groove.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2000058058A JP4338281B2 (en) | 2000-03-03 | 2000-03-03 | Hydrodynamic bearing device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2000058058A JP4338281B2 (en) | 2000-03-03 | 2000-03-03 | Hydrodynamic bearing device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JP2001248635A true JP2001248635A (en) | 2001-09-14 |
| JP4338281B2 JP4338281B2 (en) | 2009-10-07 |
Family
ID=18578709
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2000058058A Expired - Lifetime JP4338281B2 (en) | 2000-03-03 | 2000-03-03 | Hydrodynamic bearing device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP4338281B2 (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2004081399A1 (en) * | 2003-03-14 | 2004-09-23 | Seiko Instruments Inc. | Hydrodynamic bearing, motor, and recording medium drive device |
| JP2005048951A (en) * | 2004-07-28 | 2005-02-24 | Ntn Corp | Dynamic pressure type bearing unit |
| JP2008038989A (en) * | 2006-08-03 | 2008-02-21 | Tokai Univ | Grooved hydrodynamic thrust gas bearing and its manufacturing method |
| KR101291296B1 (en) | 2006-07-10 | 2013-07-30 | 볼보 컨스트럭션 이큅먼트 에이비 | Bearing pre-load structure for swing gear box of heavy construction equipment |
-
2000
- 2000-03-03 JP JP2000058058A patent/JP4338281B2/en not_active Expired - Lifetime
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2004081399A1 (en) * | 2003-03-14 | 2004-09-23 | Seiko Instruments Inc. | Hydrodynamic bearing, motor, and recording medium drive device |
| JP2005048951A (en) * | 2004-07-28 | 2005-02-24 | Ntn Corp | Dynamic pressure type bearing unit |
| KR101291296B1 (en) | 2006-07-10 | 2013-07-30 | 볼보 컨스트럭션 이큅먼트 에이비 | Bearing pre-load structure for swing gear box of heavy construction equipment |
| JP2008038989A (en) * | 2006-08-03 | 2008-02-21 | Tokai Univ | Grooved hydrodynamic thrust gas bearing and its manufacturing method |
Also Published As
| Publication number | Publication date |
|---|---|
| JP4338281B2 (en) | 2009-10-07 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| USRE39613E1 (en) | Half bearing with grooves preventing leakage of lubricating oil | |
| KR100708924B1 (en) | Foil hydrodynamic journal bearing and method of manufacturing the same | |
| JP4159332B2 (en) | Hydrodynamic bearing device | |
| JP2516967B2 (en) | Bearing device | |
| US5932946A (en) | Porous bearing system having internal grooves and electric motor provided with the same | |
| US5704718A (en) | Sintered oil-impregnated bearing and method for manufacturing same | |
| KR19980014962A (en) | Sintered bearing | |
| JP2002349548A (en) | Hydrodynamic fluid bearing device | |
| JP3774080B2 (en) | Hydrodynamic bearing unit | |
| JP4245897B2 (en) | Method for manufacturing hydrodynamic bearing device | |
| JPH1182487A (en) | Porous bearing | |
| JP2001248635A (en) | Dynamic pressure fluid bearing device | |
| US8506167B2 (en) | Dynamic bearing device having a thrust bearing portion | |
| JP2003232353A (en) | Dynamic pressure type bearing device | |
| JP3983435B2 (en) | Hydrodynamic bearing unit | |
| JPH05215128A (en) | Bering device | |
| JP2003194045A (en) | Dynamic pressure bearing device | |
| JPH02278007A (en) | Thrust bearing | |
| JP3842499B2 (en) | Hydrodynamic bearing unit | |
| JP2003074543A (en) | Hydrodynamic fluid bearing unit and motor with the same | |
| JP3620814B2 (en) | Porous composite bearing | |
| JP3892995B2 (en) | Hydrodynamic bearing unit | |
| JP2006329391A (en) | Dynamic pressure bearing arrangement | |
| JP2005127524A (en) | Dynamic-pressure bearing device | |
| JP2004108549A (en) | Hydrodynamic bearing device |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| A621 | Written request for application examination |
Free format text: JAPANESE INTERMEDIATE CODE: A621 Effective date: 20070122 |
|
| A977 | Report on retrieval |
Free format text: JAPANESE INTERMEDIATE CODE: A971007 Effective date: 20081008 |
|
| A131 | Notification of reasons for refusal |
Free format text: JAPANESE INTERMEDIATE CODE: A131 Effective date: 20081014 |
|
| A521 | Written amendment |
Free format text: JAPANESE INTERMEDIATE CODE: A523 Effective date: 20081215 |
|
| A131 | Notification of reasons for refusal |
Free format text: JAPANESE INTERMEDIATE CODE: A131 Effective date: 20090127 |
|
| A521 | Written amendment |
Free format text: JAPANESE INTERMEDIATE CODE: A523 Effective date: 20090303 |
|
| TRDD | Decision of grant or rejection written | ||
| A01 | Written decision to grant a patent or to grant a registration (utility model) |
Free format text: JAPANESE INTERMEDIATE CODE: A01 Effective date: 20090602 |
|
| A01 | Written decision to grant a patent or to grant a registration (utility model) |
Free format text: JAPANESE INTERMEDIATE CODE: A01 |
|
| A61 | First payment of annual fees (during grant procedure) |
Free format text: JAPANESE INTERMEDIATE CODE: A61 Effective date: 20090630 |
|
| R151 | Written notification of patent or utility model registration |
Ref document number: 4338281 Country of ref document: JP Free format text: JAPANESE INTERMEDIATE CODE: R151 |
|
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20120710 Year of fee payment: 3 |
|
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20120710 Year of fee payment: 3 |
|
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20130710 Year of fee payment: 4 |
|
| S111 | Request for change of ownership or part of ownership |
Free format text: JAPANESE INTERMEDIATE CODE: R313113 |
|
| R350 | Written notification of registration of transfer |
Free format text: JAPANESE INTERMEDIATE CODE: R350 |
|
| S111 | Request for change of ownership or part of ownership |
Free format text: JAPANESE INTERMEDIATE CODE: R313113 |
|
| R350 | Written notification of registration of transfer |
Free format text: JAPANESE INTERMEDIATE CODE: R350 |
|
| S111 | Request for change of ownership or part of ownership |
Free format text: JAPANESE INTERMEDIATE CODE: R313113 |
|
| R350 | Written notification of registration of transfer |
Free format text: JAPANESE INTERMEDIATE CODE: R350 |
|
| R250 | Receipt of annual fees |
Free format text: JAPANESE INTERMEDIATE CODE: R250 |
|
| R250 | Receipt of annual fees |
Free format text: JAPANESE INTERMEDIATE CODE: R250 |
|
| R250 | Receipt of annual fees |
Free format text: JAPANESE INTERMEDIATE CODE: R250 |
|
| S533 | Written request for registration of change of name |
Free format text: JAPANESE INTERMEDIATE CODE: R313533 |
|
| R350 | Written notification of registration of transfer |
Free format text: JAPANESE INTERMEDIATE CODE: R350 |
|
| R250 | Receipt of annual fees |
Free format text: JAPANESE INTERMEDIATE CODE: R250 |
|
| R250 | Receipt of annual fees |
Free format text: JAPANESE INTERMEDIATE CODE: R250 |
|
| EXPY | Cancellation because of completion of term |