JP2002061637A - Dynamic pressure type bearing device - Google Patents
Dynamic pressure type bearing deviceInfo
- Publication number
- JP2002061637A JP2002061637A JP2000252943A JP2000252943A JP2002061637A JP 2002061637 A JP2002061637 A JP 2002061637A JP 2000252943 A JP2000252943 A JP 2000252943A JP 2000252943 A JP2000252943 A JP 2000252943A JP 2002061637 A JP2002061637 A JP 2002061637A
- Authority
- JP
- Japan
- Prior art keywords
- bearing
- housing
- dynamic pressure
- thrust
- peripheral surface
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
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
- F16C33/02—Parts of sliding-contact bearings
- F16C33/04—Brasses; Bushes; Linings
- F16C33/06—Sliding surface mainly made of metal
- F16C33/10—Construction relative to lubrication
- F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
- F16C33/106—Details of distribution or circulation inside the bearings, e.g. details of the bearing surfaces to affect flow or pressure of the liquid
- F16C33/107—Grooves for generating pressure
-
- 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
- F16C17/00—Sliding-contact bearings for exclusively rotary movement
- F16C17/10—Sliding-contact bearings for exclusively rotary movement for both radial and axial load
- F16C17/102—Sliding-contact bearings for exclusively rotary movement for both radial and axial load with grooves in the bearing surface to generate hydrodynamic pressure
- F16C17/107—Sliding-contact bearings for exclusively rotary movement for both radial and axial load with grooves in the bearing surface to generate hydrodynamic pressure with at least one surface for radial load and at least one surface for axial load
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Oil, Petroleum & Natural Gas (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mounting Of Bearings Or Others (AREA)
- Sliding-Contact Bearings (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、動圧型軸受装置に
関する。この軸受装置は、特に情報機器、例えばＨＤ
Ｄ、ＦＤＤ等の磁気ディスク装置、ＣＤ−ＲＯＭ、ＤＶ
Ｄ−ＲＯＭ等の光ディスク装置、ＭＤ、ＭＯ等の光磁気
ディスク装置などのスピンドルモータ、あるいはレーザ
ビームプリンタ（ＬＢＰ）のポリゴンスキャナモータな
どのスピンドル支持用として好適である。The present invention relates to a dynamic pressure bearing device. This bearing device is particularly suitable for information equipment such as HD
D, FDD, etc., magnetic disk drive, CD-ROM, DV
It is suitable for supporting a spindle motor such as an optical disk device such as a D-ROM, a magneto-optical disk device such as an MD or MO, or a polygon scanner motor of a laser beam printer (LBP).
【０００２】[0002]
【従来の技術】上記各種情報機器のスピンドルモータに
は、高回転精度の他、高速化、低コスト化、低騒音化な
どが求められている。これらの要求性能を決定づける構
成要素の一つに当該モータのスピンドルを支持する軸受
があり、近年では、この種の軸受として、上記要求性能
に優れた特性を有する動圧型軸受の使用が検討され、あ
るいは実際に使用されている。2. Description of the Related Art Spindle motors for various information devices are required to have high rotational accuracy, high speed, low cost, low noise, and the like. One of the components that determine these required performances is a bearing that supports the spindle of the motor.In recent years, as this type of bearing, the use of a dynamic pressure bearing having characteristics excellent in the required performance has been studied. Or they are actually used.
【０００３】図８は、ＨＤＤ等のディスク装置のスピン
ドルモータに組込まれる動圧型軸受装置の一構成例を示
している。この動圧軸受装置には、軸部材としての回転
軸２０をラジアル方向に回転自在に非接触支持するラジ
アル軸受部２１と、回転軸２０をスラスト方向に回転自
在に非接触支持するスラスト軸受部２２とが設けられ、
これらの軸受部２１、２２は何れも軸受面に動圧発生用
の溝（動圧溝）を有する動圧型軸受である。ラジアル軸
受部２１の動圧溝は、ハウジング２３の内周面（ラジア
ル軸受面）２３ａ又は回転軸２０の外周面に形成され、
スラスト軸受部２２の動圧溝は、回転軸２０の下端に設
けられたスラスト板２０ｂの両端面２０ｂ１、２０ｂ
２、あるいは、これに対向する面（スラスト軸受面）に
それぞれ形成される。ハウジング２３の側部２３ｂの下
方部分には、スラスト板２０ｂの幅寸法にスラスト軸受
隙間の大きさ（両側で１０〜２０μｍ程度）を加算した
幅寸法の段差部２３ｃが設けられ、この段差部２３ｃに
続くインロー部２３ｄに底部（バックメタル）２３ｅを
組み込むことによって、スラスト板２０ｂの軸方向両側
に所定値のスラスト軸受隙間Ｓ１、Ｓ２が形成される。FIG. 8 shows a configuration example of a dynamic pressure type bearing device incorporated in a spindle motor of a disk device such as an HDD. This dynamic pressure bearing device includes a radial bearing portion 21 that rotatably supports a rotating shaft 20 as a shaft member in a radial direction in a non-contact manner, and a thrust bearing portion 22 that supports a rotating shaft 20 in a non-contact manner so as to be rotatable in a thrust direction. Is provided,
Each of these bearing portions 21 and 22 is a dynamic pressure bearing having a groove (dynamic pressure groove) for generating dynamic pressure on the bearing surface. The dynamic pressure groove of the radial bearing portion 21 is formed on the inner peripheral surface (radial bearing surface) 23 a of the housing 23 or the outer peripheral surface of the rotating shaft 20.
The dynamic pressure grooves of the thrust bearing portion 22 are provided at both end surfaces 20b1, 20b of a thrust plate 20b provided at the lower end of the rotating shaft 20.
2, or a surface (a thrust bearing surface) opposed thereto. A step portion 23c having a width obtained by adding the size of the thrust bearing gap (about 10 to 20 μm on both sides) to the width of the thrust plate 20b is provided below the side portion 23b of the housing 23. By incorporating the bottom portion (back metal) 23e in the spigot portion 23d following the above, thrust bearing gaps S1 and S2 of a predetermined value are formed on both axial sides of the thrust plate 20b.
【０００４】[0004]
【発明が解決しようとする課題】上記軸受装置におい
て、スラスト軸受隙間Ｓ１、Ｓ２を所定値に設定するた
めには、ハウジング２３の段差部２３ｃの幅寸法（軸方
向寸法）とスラスト板２０ｂの幅寸法を精度良く管理す
る必要があり、段差部２３ｃの幅寸法を精度良く管理す
ることは、ハウジング２３の製造工数や製造コストを増
加させる一因となる。In the above bearing device, in order to set the thrust bearing gaps S1 and S2 to predetermined values, the width dimension (axial dimension) of the step portion 23c of the housing 23 and the width of the thrust plate 20b are set. It is necessary to control the dimensions with high accuracy, and managing the width of the step portion 23c with high accuracy contributes to an increase in man-hours and manufacturing costs of the housing 23.
【０００５】そこで、本発明は、スラスト軸受部のスラ
スト軸受隙間を簡易かつ精度良く設定することができる
構成を提供し、それによって、この種の動圧型軸受装置
の優れた軸受性能を確保しつつ、製造コストをさらに低
減させることを目的とする。Therefore, the present invention provides a structure capable of easily and accurately setting a thrust bearing gap of a thrust bearing portion, thereby ensuring excellent bearing performance of this type of dynamic pressure bearing device. Another object of the present invention is to further reduce manufacturing costs.
【０００６】[0006]
【課題を解決するための手段】上記目的を達成するた
め、本発明は、円筒状の内周面を有する有底筒状のハウ
ジングと、ハウジングの内周面に固定された軸受部材
と、軸部材と、軸部材と軸受部材との相対回転時に生じ
る動圧作用で軸部材を回転自在に非接触支持するラジア
ル軸受部およびスラスト軸受部とを備え、スラスト軸受
部のスラスト軸受面を構成する軸受部材の下端面が、ハ
ウジングの内底面から定寸位置に形成されている構成を
提供する。この構成によれば、スラスト軸受面を構成す
る軸受部材の下端面がハウジングの内底面から定寸位置
に形成されているので、スラスト軸受隙間を所定値に精
度良く設定することができる。In order to achieve the above object, the present invention provides a bottomed cylindrical housing having a cylindrical inner peripheral surface, a bearing member fixed to the inner peripheral surface of the housing, and a shaft. A bearing comprising a member, a radial bearing portion and a thrust bearing portion rotatably supporting the shaft member in a non-contact manner by a dynamic pressure effect generated at the time of relative rotation between the shaft member and the bearing member, and forming a thrust bearing surface of the thrust bearing portion. Provided is a configuration in which the lower end surface of the member is formed at a fixed position from the inner bottom surface of the housing. According to this configuration, since the lower end surface of the bearing member constituting the thrust bearing surface is formed at a fixed position from the inner bottom surface of the housing, the thrust bearing gap can be accurately set to a predetermined value.
【０００７】上記構成において、軸受部材の下端面を定
寸位置に形成するための位置決め手段をハウジングの内
周面に設けた構成とすることができる。この構成によれ
ば、軸受部材をハウジングの内周面に沿って位置決め手
段に当接するまで押し込むと、軸受部材の下端面の位置
が精度良く決まり、それによって、スラスト軸受隙間が
所定値に精度良く設定される。位置決め手段は、ハウジ
ングの内周面に装着された位置決め部材で構成し、ある
いは、ハウジングの内周面に設けられた段部で構成する
ことができる。In the above configuration, a positioning means for forming the lower end surface of the bearing member at a fixed size position may be provided on the inner peripheral surface of the housing. According to this configuration, when the bearing member is pushed along the inner peripheral surface of the housing until it comes into contact with the positioning means, the position of the lower end surface of the bearing member is accurately determined, whereby the thrust bearing gap is accurately adjusted to a predetermined value. Is set. The positioning means may be constituted by a positioning member mounted on the inner peripheral surface of the housing, or may be constituted by a step provided on the inner peripheral surface of the housing.
【０００８】また、本発明は、上記目的を達成するた
め、円筒状の内周面を有する有底筒状のハウジングと、
ハウジングの内周面に固定された軸受部材と、軸受部材
の内周面に挿入される軸部と、軸部に設けられたスラス
ト板とを有する軸部材と、軸受部材の内周面と、軸部材
の軸部の外周面との間に設けられ、軸部材と軸受部材と
の相対回転時に生じる動圧作用で軸部をラジアル方向に
回転自在に非接触支持するラジアル軸受部と、軸部材の
スラスト板の両端面と、軸受部材の下端面およびハウジ
ングの内底面との間にそれぞれ設けられ、軸部材と軸受
部材との相対回転時に生じる動圧作用で前記スラスト板
をスラスト方向に回転自在に非接触支持するスラスト軸
受部とを備えた動圧型軸受装置であって、この動圧型軸
受装置の組立て時に、ハウジングの内底面とスラスト板
の下端面との間、および軸受部材の下端面とスラスト板
の上端面との間のうち、少なくとも一の部位に所定厚さ
の樹脂層を介在させることによって、軸受部材のハウジ
ングに対する固定位置を調整し、その後、樹脂層を溶剤
によって溶解して除去することによって、スラスト軸受
隙間を所定値に設定した構成を提供する。In order to achieve the above object, the present invention provides a bottomed cylindrical housing having a cylindrical inner peripheral surface,
A bearing member fixed to the inner peripheral surface of the housing, a shaft inserted into the inner peripheral surface of the bearing member, a shaft member having a thrust plate provided on the shaft, and an inner peripheral surface of the bearing member, A radial bearing portion provided between the outer peripheral surface of the shaft portion of the shaft member and supporting the shaft portion rotatably in the radial direction in a non-contact manner by a dynamic pressure effect generated when the shaft member and the bearing member rotate relative to each other; Are provided between both end surfaces of the thrust plate, the lower end surface of the bearing member, and the inner bottom surface of the housing, and the thrust plate is rotatable in the thrust direction by a dynamic pressure action generated when the shaft member and the bearing member rotate relative to each other. A thrust bearing portion for non-contact support to the dynamic pressure bearing device, during assembly of the dynamic pressure bearing device, between the inner bottom surface of the housing and the lower end surface of the thrust plate, and the lower end surface of the bearing member. Between the top surface of the thrust plate That is, the fixing position of the bearing member to the housing is adjusted by interposing a resin layer of a predetermined thickness in at least one portion, and thereafter, the resin layer is dissolved and removed by a solvent to remove the thrust bearing gap by a predetermined amount. Provide the configuration set to the value.
【０００９】上記の部位に樹脂層を介在させることによ
って、軸受部材はハウジング内で樹脂層の厚さを加えた
位置に固定される。従って、樹脂層を除去すると、スラ
スト板の両端面と、ハウジングの内底面および軸受部材
の下端面との間に樹脂層の厚さに等しい隙間ができ、こ
の隙間がスラスト軸受隙間になる。この構成によって
も、スラスト軸受隙間を所定値に簡易かつ精度良く設定
することができる。By interposing the resin layer in the above-mentioned portion, the bearing member is fixed at a position in the housing in which the thickness of the resin layer is added. Therefore, when the resin layer is removed, a gap equal to the thickness of the resin layer is formed between both end faces of the thrust plate and the inner bottom face of the housing and the lower end face of the bearing member, and this gap becomes a thrust bearing gap. Also with this configuration, the thrust bearing gap can be set to a predetermined value simply and accurately.
【００１０】上記構成において、樹脂層はスラスト板の
下端面に形成することができ、その場合、樹脂層は、ス
ラスト板の下端面に滴下した樹脂液を軸部材の回転に伴
う遠心力で流動させて所定厚さの層状にした後、これを
乾燥固化させて形成することができる。これにより、所
定厚さの樹脂層を簡易かつ精度良く形成することができ
る。また、ハウジングの底部に、樹脂層の溶解液を排出
するための排出部を設けることにより、溶解液の排出作
業が容易になる。In the above configuration, the resin layer can be formed on the lower end surface of the thrust plate. In this case, the resin layer flows the resin liquid dropped on the lower end surface of the thrust plate by centrifugal force accompanying rotation of the shaft member. After being formed into a layer having a predetermined thickness, the layer can be formed by drying and solidifying the layer. Thus, a resin layer having a predetermined thickness can be easily and accurately formed. Further, by providing a discharge portion for discharging the solution of the resin layer at the bottom of the housing, the operation of discharging the solution is facilitated.
【００１１】以上の構成において、軸受部材は好ましく
は多孔質体で形成され、より好ましくは燒結金属で形成
される。これにより、軸受部材に動圧溝を形成する場合
の加工が容易になり、また、軸受部材の気孔内に潤滑油
又は潤滑グリースを含浸させて動圧型含油軸受とした
り、動圧型気体軸受として、軸受性能の向上を図ること
ができる。In the above configuration, the bearing member is preferably formed of a porous body, and more preferably formed of a sintered metal. This facilitates processing when forming a dynamic pressure groove in the bearing member, and also impregnates the lubricating oil or lubricating grease into the pores of the bearing member to form a hydrodynamic oil-impregnated bearing, or as a hydrodynamic gas bearing. Bearing performance can be improved.
【００１２】[0012]
【発明の実施の形態】以下、本発明の実施形態について
説明する。Embodiments of the present invention will be described below.
【００１３】図１は、本発明の第１の実施形態に係る動
圧型軸受装置１を組み込んだ情報機器用スピンドルモー
タの一構成例を示している。このスピンドルモータは、
ＨＤＤ等のディスク駆動装置に用いられるもので、軸部
材としての回転軸２を回転自在に非接触支持する動圧型
軸受装置１と、回転軸２に装着されたディスクハブ３
と、半径方向のギャップを介して対向させたモータステ
ータ４およびモータロータ５とを備えている。ステータ
４はケーシング６の外周に取付けられ、ロータ５はディ
スクハブ３の内周に取付けられる。動圧型軸受装置１の
ハウジング７は、ケーシング６の内周に装着される。デ
ィスクハブ３には、磁気ディスク等のディスクＤが一又
は複数枚保持される。ステータ４に通電すると、ステー
タ４とロータ５との間の励磁力でロータ５が回転し、そ
れによって、ディスクハブ３および回転軸２が一体とな
って回転する。FIG. 1 shows an example of the configuration of a spindle motor for information equipment incorporating a dynamic pressure bearing device 1 according to a first embodiment of the present invention. This spindle motor
A dynamic pressure bearing device 1 that is used in a disk drive device such as an HDD and rotatably supports a rotating shaft 2 as a shaft member in a non-contact manner, and a disk hub 3 mounted on the rotating shaft 2.
And a motor stator 4 and a motor rotor 5 opposed to each other via a radial gap. The stator 4 is mounted on the outer circumference of the casing 6, and the rotor 5 is mounted on the inner circumference of the disk hub 3. The housing 7 of the dynamic pressure bearing device 1 is mounted on the inner periphery of the casing 6. The disk hub 3 holds one or more disks D such as magnetic disks. When the stator 4 is energized, the rotor 5 rotates by the exciting force between the stator 4 and the rotor 5, whereby the disk hub 3 and the rotating shaft 2 rotate integrally.
【００１４】図２は、動圧型軸受装置１を示している。
動圧型軸受装置１は、円筒状の内周面７ａを有する有底
筒状のハウジング７と、ハウジング７の内周面７ａに固
定された円筒状の軸受部材８と、軸部材としての回転軸
２と、ハウジング７の内周面７ａに装着された位置決め
手段としての位置決め部材９と、軸受部材８の上端面側
（ハウジング７の開口側）を密封するシール部材１０と
を主要な構成要素とする。FIG. 2 shows the dynamic pressure type bearing device 1.
The dynamic pressure bearing device 1 includes a bottomed cylindrical housing 7 having a cylindrical inner peripheral surface 7a, a cylindrical bearing member 8 fixed to the inner peripheral surface 7a of the housing 7, and a rotating shaft as a shaft member. 2, a positioning member 9 as positioning means mounted on the inner peripheral surface 7a of the housing 7, and a seal member 10 for sealing the upper end surface side (opening side of the housing 7) of the bearing member 8 as main components. I do.
【００１５】ハウジング７は、円筒状の側部７ｂと、底
部７ｃとで構成され、側部７ｂの内周面７ａは上端から
下端にかけて同一内径に形成される。尚、この実施形態
では、ハウジング７の側部７ｂと底部７ｃとを一体構造
にしているが、両者を別体構造としても良い。The housing 7 includes a cylindrical side 7b and a bottom 7c, and the inner peripheral surface 7a of the side 7b has the same inner diameter from the upper end to the lower end. In addition, in this embodiment, the side part 7b and the bottom part 7c of the housing 7 are made into an integral structure, but they may be made into separate structures.
【００１６】回転軸２は、軸部２ａと、軸部２ａに一体
又は別体に設けられたスラスト板２ｂとを備えている。
スラスト板２ｂの幅寸法はＷ１である。軸部２ａは、軸
受部材８の内周面８ａに所定のラジアル軸受隙間Ｓ５を
もって挿入され、スラスト板２ｂは、軸受部材８の下端
面８ｂとハウジング７の内底面７ｃ１との間の空間部に
収容される。スラスト板２ｂの上端面２ｂ１と軸受部材
８の下端面８ｂとの間、および、スラスト板２ｂの下端
面２ｂ２とハウジング７の内底面７ｃ１との間には、そ
れぞれ、所定の大きさをもったスラスト軸受隙間Ｓ３、
Ｓ４が設けられる。The rotating shaft 2 has a shaft portion 2a and a thrust plate 2b provided integrally with or separately from the shaft portion 2a.
The width dimension of the thrust plate 2b is W1. The shaft portion 2a is inserted into the inner peripheral surface 8a of the bearing member 8 with a predetermined radial bearing gap S5, and the thrust plate 2b is inserted into the space between the lower end surface 8b of the bearing member 8 and the inner bottom surface 7c1 of the housing 7. Will be accommodated. A predetermined size was provided between the upper end surface 2b1 of the thrust plate 2b and the lower end surface 8b of the bearing member 8, and between the lower end surface 2b2 of the thrust plate 2b and the inner bottom surface 7c1 of the housing 7, respectively. Thrust bearing gap S3,
S4 is provided.
【００１７】軸受部材８は、例えば多孔質材、特に燒結
金属で形成され、その内部の気孔に潤滑油又は潤滑グリ
ースが含浸されて含油軸受とされる。軸受部材８の内周
面８ａの、ラジアル軸受面となる領域には動圧溝が形成
される。この動圧溝は圧縮成形、例えば、コアロッドの
外周面にラジアル軸受面の動圧溝形状（図３（ａ）参
照）に対応した凹凸パターンを有する溝型を形成し、コ
アロッドの外周に焼結金属を供給して焼結金属を圧迫
し、焼結金属の内周部に溝型形状に対応した動圧溝を転
写することによって、低コストにかつ高精度に成形する
ことができる。回転軸２が回転すると、ラジアル軸受隙
間Ｓ５に動圧作用が発生し、回転軸２の軸部２ａがラジ
アル軸受隙間Ｓ５内に形成される潤滑油の油膜によって
ラジアル方向に回転自在に非接触支持される。これによ
り、回転軸２をラジアル方向に回転自在に非接触支持す
るラジアル軸受部１１が構成される。尚、軸受部材８
は、燒結金属の他、軟質金属あるいは合金（例えば銅、
真鍮等）で形成しても良い。また、ラジアル軸受面の動
圧溝は、回転軸２の軸部２ａの外周面に形成しても良
い。The bearing member 8 is formed of, for example, a porous material, particularly a sintered metal, and its pores are impregnated with lubricating oil or lubricating grease to form an oil-impregnated bearing. A dynamic pressure groove is formed in a region of the inner peripheral surface 8a of the bearing member 8 to be a radial bearing surface. This dynamic pressure groove is formed by compression molding, for example, by forming a groove mold having an uneven pattern corresponding to the shape of the dynamic pressure groove on the radial bearing surface (see FIG. 3A) on the outer peripheral surface of the core rod, and sintering the outer periphery of the core rod. By supplying the metal and pressing the sintered metal and transferring the dynamic pressure groove corresponding to the groove shape to the inner peripheral portion of the sintered metal, the molding can be performed at low cost and with high precision. When the rotating shaft 2 rotates, a dynamic pressure action is generated in the radial bearing gap S5, and the shaft portion 2a of the rotating shaft 2 is rotatably and non-contactly supported in the radial direction by a lubricating oil film formed in the radial bearing gap S5. Is done. As a result, a radial bearing portion 11 that rotatably supports the rotating shaft 2 in the radial direction in a non-contact manner is configured. The bearing member 8
Means soft metals or alloys (such as copper,
Brass or the like). Further, the dynamic pressure groove on the radial bearing surface may be formed on the outer peripheral surface of the shaft portion 2 a of the rotating shaft 2.
【００１８】スラスト板２ｂの上端面２ｂ１又は軸受部
材８の下端面８ｂ、および、スラスト板２ｂの下端面２
ｂ２又はハウジング７の内底面７ｃ１の、スラスト軸受
面となる領域には、それぞれ動圧溝が形成される。回転
軸２が回転すると、スラスト軸受隙間Ｓ３およびＳ４に
動圧作用が発生し、回転軸２のスラスト板２ｂがスラス
ト軸受隙間Ｓ３、Ｓ４内に形成される潤滑油の油膜によ
ってスラスト方向に回転自在に非接触支持される。これ
により、回転軸２をスラスト方向に回転自在に非接触支
持するスラスト軸受部１２が構成される。The upper end surface 2b1 of the thrust plate 2b or the lower end surface 8b of the bearing member 8, and the lower end surface 2b of the thrust plate 2b
A dynamic pressure groove is formed in each of the regions b2 and the inner bottom surface 7c1 of the housing 7 to be the thrust bearing surface. When the rotating shaft 2 rotates, a dynamic pressure action is generated in the thrust bearing gaps S3 and S4, and the thrust plate 2b of the rotating shaft 2 is freely rotatable in the thrust direction by a lubricating oil film formed in the thrust bearing gaps S3 and S4. Non-contact support. As a result, a thrust bearing portion 12 that rotatably supports the rotating shaft 2 in the thrust direction in a non-contact manner is configured.
【００１９】ラジアル軸受面およびスラスト軸受面の動
圧溝形状は任意に選択することができ、公知のへリング
ボーン型、スパイラル型、ステップ型、多円弧型等の何
れかを選択し、あるいはこれらを適宜組合わせて使用す
ることができる。図３（ａ）（ｂ）は、一例としてへリ
ングボーン型を示すもので、図３（ａ）は軸受部材８の
内周面８ａにおけるラジアル軸受面８ａ１に動圧溝１４
を設けた例、図３（ｂ）は、スラスト板２ｂの下端面２
ｂ２におけるスラスト軸受面２ｂ２１に動圧溝１６を設
けた例を示している。例えば、軸受部材８の内周面８ａ
には、２つのラジアル軸受面８ａ１が軸方向に離間して
設けられている。スラスト軸受面２ｂ１の動圧溝１６
は、半径方向のほぼ中心部に屈曲部分を有するほぼＶ字
状をなしている。The shape of the dynamic pressure grooves on the radial bearing surface and the thrust bearing surface can be arbitrarily selected, and any of the well-known herringbone type, spiral type, step type, multi-arc type, or the like is selected. Can be used in appropriate combination. 3 (a) and 3 (b) show a herringbone type as an example. FIG. 3 (a) shows a hydrodynamic groove 14 on a radial bearing surface 8a1 of the inner peripheral surface 8a of the bearing member 8. FIG.
FIG. 3B shows the lower end surface 2 of the thrust plate 2b.
The example in which the dynamic pressure groove 16 is provided on the thrust bearing surface 2b21 in b2 is shown. For example, the inner peripheral surface 8a of the bearing member 8
, Two radial bearing surfaces 8a1 are provided apart from each other in the axial direction. Dynamic pressure groove 16 in thrust bearing surface 2b1
Has a substantially V-shape having a bent portion substantially at the center in the radial direction.
【００２０】図２に示すように、この実施形態におい
て、位置決め部材９は金属製又は樹脂製のリングで、ハ
ウジング７の内底面７ｃ１と軸受部材８の下端面８ｂと
の間に介装される。位置決め部材９の外周面はハウジン
グ７の内周面７ａに装着され、位置決め部材９の内周面
はスラスト板２ｂの外周面と僅かな隙間を介して対向す
る。位置決め部材９の下端面がハウジング７の内底面７
ｃ１と当接し、上端面が軸受部材８の下端面８ｂと当接
することによって、軸受部材８のハウジング７に対する
固定位置が決まる。すなわち、軸受部材８をハウジング
７の内周面７ａに沿って位置決め部材９に当接するまで
押し込むと、ハウジング７の内底面７ｃ１に対する軸受
部材８の下端面８ｂの位置が、位置決め部材９の幅寸法
Ｗによって定寸位置Ｗに決まる。この状態で、軸受部材
８をハウジング７の内周面７ａに固定する。固定方法と
しては、圧入、接着等がある。従って、位置決め部材９
の幅寸法Ｗを、スラスト板２ｂの幅寸法Ｗ１に両側のス
ラスト軸受隙間Ｓ３、Ｓ４の値を加えた値に管理してお
けば｛Ｗ＝Ｗ１＋（Ｓ３＋Ｓ４）｝、位置決め部材９に
よってスラスト軸受隙間Ｓ３、Ｓ４を簡易かつ精度良く
設定することができる。位置決め部材９の幅寸法Ｗの管
理は比較的容易であり、かつ、高精度な管理が可能であ
る。また、使用条件等によって、スラスト軸受隙間Ｓ
３、Ｓ４の設定値を変更する必要が生じた場合でも、変
更後のスラスト軸受隙間Ｓ３、Ｓ４に対応する幅寸法Ｗ
をもった位置決め部材９を用いることによって容易に対
応することができる。As shown in FIG. 2, in this embodiment, the positioning member 9 is a metal or resin ring and is interposed between the inner bottom surface 7c1 of the housing 7 and the lower end surface 8b of the bearing member 8. . The outer peripheral surface of the positioning member 9 is mounted on the inner peripheral surface 7a of the housing 7, and the inner peripheral surface of the positioning member 9 faces the outer peripheral surface of the thrust plate 2b with a small gap. The lower end surface of the positioning member 9 is the inner bottom surface 7 of the housing 7.
The fixed position of the bearing member 8 with respect to the housing 7 is determined by contacting the upper end surface of the bearing member 8 with the lower end surface 8b of the bearing member 8. That is, when the bearing member 8 is pushed along the inner peripheral surface 7 a of the housing 7 until it comes into contact with the positioning member 9, the position of the lower end surface 8 b of the bearing member 8 with respect to the inner bottom surface 7 c 1 of the housing 7 becomes the width dimension of the positioning member 9. W determines the fixed size position W. In this state, the bearing member 8 is fixed to the inner peripheral surface 7a of the housing 7. As a fixing method, there are press-fitting, bonding and the like. Therefore, the positioning member 9
If the width W of the thrust plate is controlled to a value obtained by adding the values of the thrust bearing gaps S3 and S4 on both sides to the width W1 of the thrust plate 2b, {W = W1 + (S3 + S4)} S3 and S4 can be set easily and accurately. Management of the width dimension W of the positioning member 9 is relatively easy, and high-precision management is possible. In addition, the thrust bearing clearance S
Even when it is necessary to change the set values of S3 and S4, the width dimension W corresponding to the changed thrust bearing gaps S3 and S4
By using the positioning member 9 having the above, it is possible to easily cope with the problem.
【００２１】上記のようにして、回転軸２、軸受部材
８、位置決め部材９、シール部材１０をアッセンブリし
た後、ハウジング７内を潤滑油で満たすと、図１に示す
動圧型軸受装置１が得られる。After the rotary shaft 2, the bearing member 8, the positioning member 9, and the seal member 10 are assembled as described above, and the housing 7 is filled with lubricating oil, the dynamic pressure bearing device 1 shown in FIG. 1 is obtained. Can be
【００２２】図９は、本発明の第２の実施形態に係る動
圧型軸受装置１’を示している。この実施形態の動圧型
軸受装置１’が、上述した実施形態の動圧型軸受装置１
と異なる点は、位置決め手段として、位置決め部材９に
代えて、ハウジング７の内周面７ａに段部７ａ１を設け
ている点にある。軸受部材８をハウジング７の内周面７
ａに沿って段部７ａ１に当接するまで押し込むと、ハウ
ジング７の内底面７ｃ１に対する軸受部材８の下端面８
ｂの位置が、段部７ａ１の内底面７ｃ１からの寸法Ｗに
よって定寸位置Ｗに決まる。この状態で、軸受部材８を
ハウジング７の内周面７ａに固定する。従って、段部７
ａ１の内底面７ｃ１からの寸法Ｗを、スラスト板２ｂの
幅寸法Ｗ１に両側のスラスト軸受隙間Ｓ３、Ｓ４の値を
加えた値に管理しておけば｛Ｗ＝Ｗ１＋（Ｓ３＋Ｓ
４）｝、段部７ａ１によってスラスト軸受隙間Ｓ３、Ｓ
４を簡易かつ精度良く設定することができる。また、上
述した第１の実施形態に比べ、部品点数の削減にもな
る。FIG. 9 shows a dynamic pressure bearing device 1 'according to a second embodiment of the present invention. The hydrodynamic bearing device 1 'of this embodiment is different from the hydrodynamic bearing device 1 of the above-described embodiment.
The difference from the first embodiment is that a step 7a1 is provided on the inner peripheral surface 7a of the housing 7 instead of the positioning member 9 as the positioning means. The bearing member 8 is connected to the inner peripheral surface 7 of the housing 7.
a until it comes into contact with the stepped portion 7a1 until the lower end surface 8 of the bearing member 8 with respect to the inner bottom surface 7c1 of the housing 7.
The position b is determined as the fixed size position W by the dimension W from the inner bottom surface 7c1 of the step portion 7a1. In this state, the bearing member 8 is fixed to the inner peripheral surface 7a of the housing 7. Therefore, the step 7
If the dimension W from the inner bottom surface 7c1 of a1 is controlled to a value obtained by adding the width dimension W1 of the thrust plate 2b to the values of the thrust bearing gaps S3 and S4 on both sides, then ΔW = W1 + (S3 + S
4) Thrust bearing gaps S3, S by step 7a1
4 can be set simply and accurately. Further, the number of parts can be reduced as compared with the first embodiment.
【００２３】図４は、本発明の第３の実施形態に係る動
圧型軸受装置１”を示している。この実施形態におい
て、スラスト軸受隙間Ｓ３、Ｓ４は、例えば以下の手順
での設定されている。FIG. 4 shows a hydrodynamic bearing device 1 ″ according to a third embodiment of the present invention. In this embodiment, the thrust bearing gaps S3 and S4 are set, for example, in the following procedure. I have.
【００２４】まず、図５に示す態様で、回転軸２のスラ
スト板２ｂの下端面２ｂ２に所定厚さδの樹脂層１９を
形成する。樹脂層１９の形成材料となる合成樹脂材料を
溶剤で溶かして樹脂液Ｌを作り、その樹脂液Ｌをスラス
ト板２ｂの下端面２ｂ２に所定量滴下する。その後、回
転軸２を所定速度で回転させる。そうすると、滴下され
た樹脂液Ｌが遠心力で外径側に流動して、スラスト板２
ｂの下端面２ｂ２に均一厚さで広がる。その後、樹脂液
Ｌを乾燥固化させると、スラスト板２ｂの下端面２ｂ２
に所定厚さδの樹脂層１９が形成される。この方法によ
れば、均一厚さの樹脂層１９を精度良く形成することが
できる。樹脂層１９の厚さδは、スラスト軸受隙間Ｓ３
とＳ４の設定値を合計した値（δ＝Ｓ３＋Ｓ４）となる
ように管理する（１０〜２０μｍ程度）。First, in the mode shown in FIG. 5, a resin layer 19 having a predetermined thickness δ is formed on the lower end surface 2b2 of the thrust plate 2b of the rotating shaft 2. A resin liquid L is prepared by dissolving a synthetic resin material as a material for forming the resin layer 19 with a solvent, and the resin liquid L is dropped on the lower end surface 2b2 of the thrust plate 2b in a predetermined amount. Thereafter, the rotating shaft 2 is rotated at a predetermined speed. Then, the dropped resin liquid L flows to the outer diameter side by centrifugal force, and the thrust plate 2
b spreads on the lower end surface 2b2 with a uniform thickness. Thereafter, when the resin liquid L is dried and solidified, the lower end surface 2b2 of the thrust plate 2b is formed.
Then, a resin layer 19 having a predetermined thickness δ is formed. According to this method, the resin layer 19 having a uniform thickness can be accurately formed. The thickness δ of the resin layer 19 is determined by the thrust bearing gap S3.
And S4 are managed so as to be a total value (δ = S3 + S4) (about 10 to 20 μm).
【００２５】つぎに、図６に示すように、回転軸２をハ
ウジング７に挿入し、スラスト板２ｂの下端面２ｂ２を
樹脂層１９を介してハウジング７の内底面７ｃ１に当接
させる。その後、軸受部材８をハウジング７の内周面７
ａに沿ってスラスト板２ｂの上端面２ｂ１に当接するま
で押し込むと、軸受部材８のハウジング７に対する固定
位置が決まる。すなわち、軸受部材８の下端面８ｂとハ
ウジング７の内底面７ｃ１との間の間隔（軸方向寸法）
が、スラスト板２ｂの幅寸法Ｗ１と樹脂層１９の厚さδ
によって寸法（Ｗ１＋δ）に決まる。この状態で、軸受
部材８をハウジング７の内周面７ａに固定する。固定方
法としては、圧入、接着等がある。尚、回転軸２と軸受
部材８とを予めアッセンブリしておき、両者を一緒にハ
ウジング７に挿入しても良い。Next, as shown in FIG. 6, the rotating shaft 2 is inserted into the housing 7, and the lower end surface 2b2 of the thrust plate 2b is brought into contact with the inner bottom surface 7c1 of the housing 7 via the resin layer 19. Then, the bearing member 8 is connected to the inner peripheral surface 7 of the housing 7.
When the bearing member 8 is pushed along the upper end surface 2b1 of the thrust plate 2b along a, the fixing position of the bearing member 8 to the housing 7 is determined. That is, the distance between the lower end surface 8b of the bearing member 8 and the inner bottom surface 7c1 of the housing 7 (axial dimension).
Is the width dimension W1 of the thrust plate 2b and the thickness δ of the resin layer 19.
Determines the size (W1 + δ). In this state, the bearing member 8 is fixed to the inner peripheral surface 7a of the housing 7. As a fixing method, there are press-fitting, bonding and the like. Note that the rotating shaft 2 and the bearing member 8 may be assembled in advance, and both may be inserted into the housing 7 together.
【００２６】上記のようにして軸受部材８の固定位置を
決めた後、ハウジング７の内部に溶剤を供給して樹脂層
１９を溶解する。この溶解液は、ハウジング７の底部７
ｃに設けられた排出部７ｄから排出される。溶解液を排
出した後、排出部７ｄは適当な栓、例えば図４に示すよ
うなボール栓７ｄ１によって封止される。After the fixing position of the bearing member 8 is determined as described above, a solvent is supplied into the housing 7 to dissolve the resin layer 19. This solution is supplied to the bottom 7 of the housing 7.
c is discharged from a discharge section 7d provided in the printer. After draining the lysis solution, the outlet 7d is sealed with a suitable stopper, for example a ball stopper 7d1 as shown in FIG.
【００２７】上記の態様で樹脂層１９を除去すると、図
４に示すように、スラスト板２ｂの両端面２ｂ１、２ｂ
２と、軸受部材８の下端面８ｂおよびハウジング７の内
底面７ｃ１との間に、樹脂層１９の厚さδに等しい大き
さをもったスラスト軸受隙間Ｓ３、Ｓ４（δ＝Ｓ３＋Ｓ
４）が形成される。その後、軸受部材８の上面側をシー
ル部材１０でシールし、ハウジング７内を潤滑油で満た
すと、図４に示す動圧型軸受装置１”が得られる。When the resin layer 19 is removed in the above manner, as shown in FIG. 4, both end surfaces 2b1, 2b of the thrust plate 2b are removed.
2 and the lower end surface 8b of the bearing member 8 and the inner bottom surface 7c1 of the housing 7, the thrust bearing gaps S3, S4 having a size equal to the thickness δ of the resin layer 19 (δ = S3 + S
4) is formed. Thereafter, the upper surface side of the bearing member 8 is sealed with a seal member 10 and the inside of the housing 7 is filled with lubricating oil, whereby the dynamic pressure bearing device 1 ″ shown in FIG. 4 is obtained.
【００２８】この実施形態によれば、スラスト軸受隙間
Ｓ３、Ｓ４の合計値が樹脂層１９の厚さδと等しくなる
ので（δ＝Ｓ３＋Ｓ４）、樹脂層１９の厚さδを正確に
管理すれば、スラスト板２ｂの幅寸法Ｗ１に多少の寸法
誤差がある場合でも、スラスト軸受隙間Ｓ３、Ｓ４を高
精度に設定することができる。According to this embodiment, since the total value of the thrust bearing gaps S3 and S4 becomes equal to the thickness δ of the resin layer 19 (δ = S3 + S4), if the thickness δ of the resin layer 19 is accurately managed. Also, even when there is some dimensional error in the width dimension W1 of the thrust plate 2b, the thrust bearing gaps S3 and S4 can be set with high accuracy.
【００２９】尚、供給した溶剤がスムーズに樹脂層１９
まで達するよう、軸受部材８の外周面に溶剤供給用の軸
方向溝８ｃを形成しておくのが望ましい。Incidentally, the supplied solvent is smoothly applied to the resin layer 19.
It is desirable to form an axial groove 8c for supplying a solvent on the outer peripheral surface of the bearing member 8 so as to reach the height.
【００３０】また、この実施形態では、スラスト軸受隙
間Ｓ３、Ｓ４の設定工程において、樹脂層１９をスラス
ト板２ｂの下端面２ｂ２とハウジング７の内底面７ｃ１
との間に介在させる構成にしているが、樹脂層１９をス
ラスト板２ｂの上端面２ｂ１と軸受部材８の下端面８ｂ
との間に介在させても良く、あるいは、これらの２つの
部位に同時に介在させても良い。Further, in this embodiment, in the step of setting the thrust bearing gaps S3, S4, the resin layer 19 is provided with the lower end face 2b2 of the thrust plate 2b and the inner bottom face 7c1 of the housing 7.
Between the upper surface 2b1 of the thrust plate 2b and the lower surface 8b of the bearing member 8.
And may be interposed between these two parts at the same time.
【００３１】樹脂層１９を形成する合成樹脂材料と溶剤
との組合わせは、樹脂層１９を確実に溶解させ得る限り
任意に選択することができるが、含塩素樹脂、塩素系溶
剤、腐食性溶剤は除外するのが好ましい。樹脂材料と溶
剤の具体的な組合わせとしては、例えば図７の○印で示
すものが考えられる。The combination of the synthetic resin material and the solvent for forming the resin layer 19 can be arbitrarily selected as long as the resin layer 19 can be surely dissolved. Examples of the combination include a chlorine-containing resin, a chlorine-based solvent, and a corrosive solvent. Is preferably excluded. As a specific combination of the resin material and the solvent, for example, a combination indicated by a circle in FIG. 7 is considered.
【００３２】[0032]
【発明の効果】本発明によれば、スラスト軸受部のスラ
スト軸受隙間を簡易かつ精度良く設定することができ、
それによって、この種の動圧型軸受装置の優れた軸受性
能を確保しつつ、製造コストをさらに低減させることが
できる。According to the present invention, the thrust bearing clearance of the thrust bearing can be set easily and accurately.
As a result, it is possible to further reduce the manufacturing cost while securing excellent bearing performance of this type of dynamic pressure bearing device.
【図１】本発明の第１の実施形態に係る動圧型軸受装置
を有するスピンドルモータの断面図である。FIG. 1 is a sectional view of a spindle motor having a dynamic pressure bearing device according to a first embodiment of the present invention.
【図２】本発明の第１の実施形態に係る動圧型軸受装置
を示す断面図である。FIG. 2 is a cross-sectional view showing the dynamic pressure bearing device according to the first embodiment of the present invention.
【図３】軸受部材の断面図｛図３（ａ）｝、スラスト板
の上端面を示す平面図｛図３（ｂ）｝である。FIG. 3 is a sectional view of the bearing member {FIG. 3A} and a plan view {FIG. 3B} showing the upper end surface of the thrust plate.
【図４】本発明の第３の実施形態に係る動圧型軸受装置
の断面図である。FIG. 4 is a sectional view of a dynamic pressure bearing device according to a third embodiment of the present invention.
【図５】樹脂層の形成工程を示す概念図である。FIG. 5 is a conceptual diagram showing a step of forming a resin layer.
【図６】スラスト軸受隙間の設定工程を説明する図であ
る。FIG. 6 is a diagram illustrating a process of setting a thrust bearing gap.
【図７】実施形態で適用され得る樹脂材料と溶剤の組合
わせを示す図である。FIG. 7 is a diagram showing a combination of a resin material and a solvent that can be applied in the embodiment.
【図８】従来の動圧型軸受装置を示す断面図である。FIG. 8 is a sectional view showing a conventional hydrodynamic bearing device.
【図９】本発明の第２の実施形態に係る動圧型軸受装置
の断面図である。FIG. 9 is a sectional view of a hydrodynamic bearing device according to a second embodiment of the present invention.
１ 動圧型軸受装置 １’ 動圧型軸受装置 1１” 動圧型軸受装置 ２ 回転軸 2ａ 軸部 2ｂ スラスト板 ２ｂ１ 上端面 ２ｂ２ 下端面 ７ ハウジング ７ａ 内周面 ７ａ１ 段部 ７ｃ 底部 ７ｃ１ 内底面 ７ｄ 排出部 ８ 軸受部材 ８ｂ 下端面 ９ 位置決め部材 １１ ラジアル軸受部 １２ スラスト軸受部 １９ 樹脂層 Ｓ３ スラスト軸受隙間 Ｓ４ スラスト軸受隙間 Ｓ５ ラジアル軸受隙間 REFERENCE SIGNS LIST 1 dynamic pressure bearing device 1 ′ dynamic pressure bearing device 11 ″ dynamic pressure bearing device 2 rotating shaft 2a shaft portion 2b thrust plate 2b1 upper end surface 2b2 lower end surface 7 housing 7a inner peripheral surface 7a1 stepped portion 7c bottom 7c1 inner bottom surface 7d discharge portion 8 Bearing member 8b Lower end surface 9 Positioning member 11 Radial bearing portion 12 Thrust bearing portion 19 Resin layer S3 Thrust bearing gap S4 Thrust bearing gap S5 Radial bearing gap
───────────────────────────────────────────────────── フロントページの続き (72)発明者 黒田 正幸 大阪府大阪市西区京町堀１丁目３番17号 エヌティエヌ株式会社内 Ｆターム(参考） 3J011 AA02 BA04 BA06 CA02 DA02 JA02 KA02 KA03 LA01 MA21 SB19 3J017 AA02 AA03 BA01 CA03 CA06 DA01 DB07 DB10 HA01 ────────────────────────────────────────────────── ─── Continuing on the front page (72) Inventor Masayuki Kuroda 1-3-17 Kyomachibori, Nishi-ku, Osaka-shi, Osaka F-term in NTN Corporation (reference) 3J011 AA02 BA04 BA06 CA02 DA02 JA02 KA02 KA03 LA01 MA21 SB19 3J017 AA02 AA03 BA01 CA03 CA06 DA01 DB07 DB10 HA01
Claims (10)
ングと、ハウジングの内周面に固定された軸受部材と、
軸部材と、前記軸部材と軸受部材との相対回転時に生じ
る動圧作用で前記軸部材を回転自在に非接触支持するラ
ジアル軸受部およびスラスト軸受部とを備え、前記スラ
スト軸受部のスラスト軸受面を構成する前記軸受部材の
下端面が、前記ハウジングの内底面から定寸位置に形成
されている動圧型軸受装置。A bottomed cylindrical housing having a cylindrical inner peripheral surface; a bearing member fixed to the inner peripheral surface of the housing;
A thrust bearing surface of the thrust bearing portion, comprising: a shaft member; and a radial bearing portion and a thrust bearing portion rotatably supporting the shaft member in a non-contact manner by a dynamic pressure effect generated when the shaft member and the bearing member rotate relative to each other. A dynamic pressure bearing device wherein a lower end surface of the bearing member is formed at a fixed position from an inner bottom surface of the housing.
るための位置決め手段を前記ハウジングの内周面に設け
た請求項１記載の動圧型軸受装置。2. A dynamic pressure bearing device according to claim 1, wherein a positioning means for forming a lower end surface of said bearing member at a fixed position is provided on an inner peripheral surface of said housing.
周面に装着された位置決め部材である請求項２記載の動
圧型軸受装置。3. The dynamic pressure bearing device according to claim 2, wherein said positioning means is a positioning member mounted on an inner peripheral surface of said housing.
周面に設けられた段部である請求項２記載の動圧型軸受
装置。4. A dynamic pressure bearing device according to claim 2, wherein said positioning means is a step provided on an inner peripheral surface of said housing.
ングと、 ハウジングの内周面に固定された軸受部材と、 前記軸受部材の内周面に挿入される軸部と、前記軸部に
設けられたスラスト板とを有する軸部材と、 前記軸受部材の内周面と、前記軸部材の軸部の外周面と
の間に設けられ、前記軸部材と軸受部材との相対回転時
に生じる動圧作用で前記軸部をラジアル方向に回転自在
に非接触支持するラジアル軸受部と、 前記軸部材のスラスト板の両端面と、前記軸受部材の下
端面および前記ハウジングの内底面との間にそれぞれ設
けられ、前記軸部材と軸受部材との相対回転時に生じる
動圧作用で前記スラスト板をスラスト方向に回転自在に
非接触支持するスラスト軸受部とを備えた動圧型軸受装
置であって、 前記動圧型軸受装置の組立て時に、前記ハウジングの内
底面と前記スラスト板の下端面との間、および前記軸受
部材の下端面と前記スラスト板の上端面との間のうち、
少なくとも一の部位に所定厚さの樹脂層を介在させるこ
とによって、前記軸受部材の前記ハウジングに対する固
定位置を調整し、その後、前記樹脂層を溶剤によって溶
解して除去することによって、前記スラスト軸受隙間を
所定値に設定したことを特徴とする動圧型軸受装置。A bottomed cylindrical housing having a cylindrical inner peripheral surface; a bearing member fixed to the inner peripheral surface of the housing; a shaft portion inserted into the inner peripheral surface of the bearing member; A shaft member having a thrust plate provided on a shaft portion; a shaft member provided between an inner peripheral surface of the bearing member and an outer peripheral surface of the shaft portion of the shaft member; and a relative rotation between the shaft member and the bearing member. A radial bearing portion that rotatably and non-contactably supports the shaft portion in a radial direction by a dynamic pressure effect that occurs at the time; a both end surface of a thrust plate of the shaft member; a lower end surface of the bearing member and an inner bottom surface of the housing; A thrust bearing portion provided between the shaft members and rotatably supporting the thrust plate in a thrust direction in a non-contact manner by a dynamic pressure effect generated when the shaft member and the bearing member rotate relative to each other. Assembling the dynamic pressure bearing device , Out between the lower end surface and the upper end surface of the thrust plate between the lower end surface of the thrust plate and the inner bottom surface of said housing, and said bearing member,
By interposing a resin layer of a predetermined thickness in at least one part, the fixing position of the bearing member with respect to the housing is adjusted, and then the resin layer is dissolved and removed by a solvent to remove the thrust bearing gap. Is set to a predetermined value.
形成した請求項５記載の動圧型軸受装置。6. A dynamic pressure bearing device according to claim 5, wherein said resin layer is formed on a lower end surface of said thrust plate.
滴下した樹脂液を前記軸部材の回転に伴う遠心力で流動
させて所定厚さの層状にした後、これを乾燥固化させて
形成したものである請求項６記載の動圧型軸受装置。7. The resin layer is formed such that the resin liquid dropped on the lower end surface of the thrust plate is flowed by centrifugal force accompanying rotation of the shaft member to form a layer having a predetermined thickness, and then dried and solidified. 7. The dynamic pressure bearing device according to claim 6, wherein the bearing is formed.
解液を排出するための排出部を設けた請求項５記載の動
圧型軸受装置。8. The dynamic pressure bearing device according to claim 5, wherein a discharge portion for discharging a solution of the resin layer is provided at a bottom portion of the housing.
請求項１又は５記載の動圧型軸受装置。9. The dynamic pressure bearing device according to claim 1, wherein said bearing member is formed of a porous body.
記載の動圧型軸受装置。10. The porous body is a sintered metal.
The dynamic pressure bearing device according to the above.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2000252943A JP2002061637A (en) | 2000-08-23 | 2000-08-23 | Dynamic pressure type bearing device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2000252943A JP2002061637A (en) | 2000-08-23 | 2000-08-23 | Dynamic pressure type bearing device |
Related Child Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2006259446A Division JP2006342975A (en) | 2006-09-25 | 2006-09-25 | Dynamic pressure type bearing device |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JP2002061637A true JP2002061637A (en) | 2002-02-28 |
Family
ID=18742113
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2000252943A Pending JP2002061637A (en) | 2000-08-23 | 2000-08-23 | Dynamic pressure type bearing device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2002061637A (en) |
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