JP2001020946A - Dynamic pressure bearing device - Google Patents
Dynamic pressure bearing deviceInfo
- Publication number
- JP2001020946A JP2001020946A JP11191314A JP19131499A JP2001020946A JP 2001020946 A JP2001020946 A JP 2001020946A JP 11191314 A JP11191314 A JP 11191314A JP 19131499 A JP19131499 A JP 19131499A JP 2001020946 A JP2001020946 A JP 2001020946A
- Authority
- JP
- Japan
- Prior art keywords
- thrust
- bearing
- bearing sleeve
- dynamic pressure
- bearing device
- 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
Landscapes
- Sliding-Contact Bearings (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、例えばハードディ
スクドライブやポリゴンミラー等の回転部の軸受に用い
られる動圧軸受装置に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a dynamic pressure bearing device used for a bearing of a rotating part such as a hard disk drive or a polygon mirror.
【０００２】[0002]
【従来の技術】ハードディスクドライブやポリゴンミラ
ー等に用いられるスピンドルモーターの分野に於いて、
高速、高容量化の要求から、高速で高精度のスピンドル
モーターが必要とされ、これに伴い動圧軸受構造を採用
したスピンドルモーターが種々提案されている。その中
でも、軸体に１枚のスラスト板を設け、軸体と軸体に対
向する軸受スリーブの一方を固定し、一方を回転自在に
したタイプは比較的構造が簡単で小型化が容易であるた
め、種々の改良型が提案されている。このようなタイプ
では以下に述べるように、軸受スリーブが軸体とラジア
ル方向の軸受部を形成すると共に、スラスト板との対向
面を設けてスラスト方向の軸受部も構成し、更にスラス
ト板の隙間を管理する構造のタイプが多い。2. Description of the Related Art In the field of spindle motors used for hard disk drives and polygon mirrors,
A demand for high-speed and high-capacity demands a high-speed and high-accuracy spindle motor, and accordingly, various spindle motors employing a dynamic pressure bearing structure have been proposed. Among them, the type in which one thrust plate is provided on the shaft body, and one of the shaft body and the bearing sleeve facing the shaft body is fixed, and one of the bearing sleeves is rotatable, has a relatively simple structure and is easily miniaturized. Therefore, various improved types have been proposed. In such a type, as described below, the bearing sleeve forms a radial bearing portion with the shaft body, and also forms a thrust bearing portion by providing a surface facing the thrust plate. There are many types of structures to manage.
【０００３】特開平９−１８２３６７号公報では、軸受
スリーブが、軸体とラジアル方向の軸受部を形成すると
同時に、スラスト板に対向する面を有してスラスト軸受
部を形成し、更にスラスト軸受部の隙間を管理する段差
を有する構造となっている。また、軸受スリーブを基台
に固定し、軸体を回転自在な構造としている。その他
に、特開平９−２９８８６０号公報では、軸受スリーブ
がラジアル軸受、スラスト軸受部、スラスト軸受部の隙
間を管理する段差を有する構造であり、軸体を固定し軸
受スリーブを回転自在の構造としている。In Japanese Patent Application Laid-Open No. 9-182667, a bearing sleeve forms a radial bearing portion with a shaft body, and at the same time, has a surface facing a thrust plate to form a thrust bearing portion. The structure has a step for managing the gap. In addition, the bearing sleeve is fixed to the base, and the shaft body has a rotatable structure. In addition, JP-A-9-298860 discloses a structure in which a bearing sleeve has a radial bearing, a thrust bearing portion, and a step for managing a gap between the thrust bearing portions. I have.
【０００４】図４は、従来の動圧軸受装置１４０を組み
込んだモーター１５０を示す断面図であり、図５はその
部分拡大図である。モーターハウジング１２０に軸受ス
リーブ１０３が固定され、軸受スリーブ１０３の下端は
スラスト受板１０５が固定され、軸体１０１の保持体を
構成している。軸体１０１の下端にスラスト板１０２が
固定されており、軸受スリーブ１０３及びスラスト受板
１０５に対して回転自在に支持される。ここでは、軸体
１０１の外周面１０７と軸受スリーブ１０３の内周面１
０６がラジアル軸受部を構成し、軸体１０１の外周面１
０７と軸受スリーブ１０３の内周面１０６の少なくとも
一方に動圧発生溝が形成されている。FIG. 4 is a sectional view showing a motor 150 in which a conventional hydrodynamic bearing device 140 is incorporated, and FIG. 5 is a partially enlarged view thereof. The bearing sleeve 103 is fixed to the motor housing 120, and the lower end of the bearing sleeve 103 is fixed to the thrust receiving plate 105, thereby forming a holder for the shaft 101. A thrust plate 102 is fixed to a lower end of the shaft body 101, and is rotatably supported by a bearing sleeve 103 and a thrust receiving plate 105. Here, the outer peripheral surface 107 of the shaft body 101 and the inner peripheral surface 1 of the bearing sleeve 103
06 constitutes a radial bearing portion, and the outer peripheral surface 1 of the shaft body 101
07 and at least one of the inner peripheral surface 106 of the bearing sleeve 103 is formed with a dynamic pressure generating groove.
【０００５】更に、スラスト板１０２の上面１０８に対
向する軸受スリーブ１０３の面１１０及びスラスト板１
０２の下面１０９に対向するスラスト受板１０５の軸受
面１１４とがスラスト軸受部を構成し、スラスト板１０
２の上面１０８と下面１０９には動圧発生溝が形成され
ている。また、固定部と回転部の隙間には潤滑流体が隙
間の開放口１１５付近まで充填されている。以上の構造
の動圧軸受装置を回転させる為に、軸体１０１にはハブ
１２５を設け、ハブ１２５にはローターマグネット１２
６を設け、モーターハウジング１２０にはステーター１
２１を設けている。前記構成において、軸体１０１とス
ラスト板１０２及びハブ１２５の固定、モーターハウジ
ング１２０と軸受スリーブ１０３、スラスト受板１０
５、ステータ１２１との固定は、隙間嵌め、接着、スポ
ット溶接等から適宜選択または組み合わせて行われてい
る。Further, the surface 110 of the bearing sleeve 103 facing the upper surface 108 of the thrust plate 102 and the thrust plate 1
02 and the bearing surface 114 of the thrust receiving plate 105 opposed to the lower surface 109 constitute a thrust bearing portion.
A dynamic pressure generating groove is formed on the upper surface 108 and the lower surface 109 of the second. Further, the gap between the fixed part and the rotating part is filled with the lubricating fluid up to the vicinity of the opening 115 of the gap. In order to rotate the hydrodynamic bearing device having the above-described structure, a hub 125 is provided on the shaft body 101, and the rotor 125 is provided on the hub 125.
6 and the motor housing 120 includes the stator 1
21 are provided. In the above configuration, the shaft body 101, the thrust plate 102 and the hub 125 are fixed, the motor housing 120, the bearing sleeve 103, and the thrust receiving plate 10
5. The fixation to the stator 121 is performed by appropriately selecting or combining from gap fitting, adhesion, spot welding and the like.
【０００６】[0006]
【発明が解決しようとする課題】図４及び図５に示す従
来の動圧軸受装置に於いて、動圧を発生する為には、ラ
ジアル軸受部及びスラスト軸受部の隙間は一般に５μｍ
付近に管理する必要がある。さらに、量産的に製品のバ
ラツキを管理するためには各製品の軸受部の隙間が１μ
ｍ〜２μｍ程度のバラツキ精度で管理される必要があ
る。ラジアル軸受部の隙間は、軸体１０１の外径と軸受
スリーブ１０３の内周面１０６の内径との差だけでな
く、実際には、軸体１０１の外周面１０７の表面粗さ、
真円度及び円筒度と、軸受スリーブ１０３の内周面１０
６の表面粗さ、真円度及び円筒度等の精度を含めて管理
される。軸体１０１の外周面１０７及び軸受スリーブ１
０３の内周面１０６は旋盤等の切削加工の他、研削加工
や研磨加工による仕上げ加工をすることも可能である
為、量産的にも精度を管理し易い部分である。In the conventional hydrodynamic bearing device shown in FIGS. 4 and 5, in order to generate dynamic pressure, the gap between the radial bearing portion and the thrust bearing portion is generally 5 μm.
It needs to be managed nearby. Furthermore, in order to manage product variations in mass production, the clearance between the bearings of each product must be 1μ.
It needs to be controlled with a variation accuracy of about m to 2 μm. The gap between the radial bearings is not only the difference between the outer diameter of the shaft body 101 and the inner diameter of the inner circumferential surface 106 of the bearing sleeve 103, but also the actual surface roughness of the outer circumferential surface 107 of the shaft body 101,
Roundness and cylindricity, and inner peripheral surface 10 of bearing sleeve 103
6, including the accuracy of surface roughness, roundness and cylindricity. Outer peripheral surface 107 of shaft body 101 and bearing sleeve 1
Since the inner peripheral surface 106 of 03 can be finished by grinding or polishing in addition to cutting with a lathe or the like, the accuracy is easily controlled even in mass production.
【０００７】もう一方のスラスト軸受部の隙間について
も、軸受スリーブ１０３の段差１１２とスラスト板１０
５の厚み１１３の差だけでなく、実際には、スラスト板
１０２の上面１０８及び下面１０９の平面度と、スラス
ト受板１０５の軸受面１１４の平面度、及び軸受スリー
ブ１０３の面１１０、面１１１の平面度等の精度を含め
て管理される。その中で、スラスト板１０２の厚み１１
３、その上面１０８、その下面１０９、及びスラスト受
板１０５の軸受面１１４は切削加工の他、必要に応じて
研削加工や研磨加工での面仕上げ加工により、部品の精
度を得ることは可能である。[0007] Regarding the gap between the other thrust bearing portion, the step 112 of the bearing sleeve 103 and the thrust plate 10
5, the flatness of the upper surface 108 and the lower surface 109 of the thrust plate 102, the flatness of the bearing surface 114 of the thrust receiving plate 105, and the surfaces 110 and 111 of the bearing sleeve 103 Is managed, including the accuracy of the flatness and the like. Among them, the thickness 11 of the thrust plate 102
3. The upper surface 108, the lower surface 109, and the bearing surface 114 of the thrust receiving plate 105 can obtain the precision of the component by surface finishing by grinding or polishing as required in addition to cutting. is there.
【０００８】しかしながら、軸受スリーブ１０３の面１
１０は面仕上げ加工が難しい構造となっている為、旋盤
等の切削加工の精度に依存し、研削加工面や研磨加工面
の平面度には到底及ばない。よって、段差１１２の加工
精度も旋盤等の切削加工の精度に依存し、その量産的な
部品加工精度は５μｍ程度が限界である。このような精
度の軸受スリーブを用いて動圧軸受装置を組み立てた場
合、スラスト軸受部の隙間の製品ばらつきは、段差１１
２の精度に面１１０の平面度も影響して、５μｍ以上に
なってしまった。よって、量産的にスラスト軸受部の隙
間を、製品ばらつきで１μｍ〜２μｍに管理ことは非常
に困難である。However, the surface 1 of the bearing sleeve 103
Since the surface finish 10 has a structure that makes it difficult to finish the surface, it depends on the precision of the cutting process of a lathe or the like, and is far from the flatness of the ground surface or the polished surface. Therefore, the processing accuracy of the step 112 also depends on the accuracy of the cutting process of a lathe or the like, and the processing accuracy of mass-produced parts is limited to about 5 μm. When a hydrodynamic bearing device is assembled using a bearing sleeve having such an accuracy, the product variation of the gap in the thrust bearing portion is caused by a step 11.
The flatness of the surface 110 also affected the accuracy of No. 2 and became 5 μm or more. Therefore, it is very difficult to control the gap between the thrust bearing portions to be 1 μm to 2 μm due to product variation in mass production.
【０００９】本発明は前記課題を解決するためのもので
あり、その目的とするところは、量産的にスラスト軸受
部の隙間の精度が得られる構造の動圧軸受装置を提供す
ることにある。An object of the present invention is to solve the above-mentioned problem, and an object of the present invention is to provide a hydrodynamic bearing device having a structure in which the accuracy of a gap between thrust bearing portions can be obtained in mass production.
【００１０】[0010]
【課題を解決するための手段】本発明の動圧軸受装置で
は上記目的を達成するために、従来の軸受スリーブに設
けた段差構造を無くし、スラストスペーサを使用するこ
とにより軸受スリーブのスラスト軸受面の研削加工や研
磨加工等の仕上げ加工を可能にし、量産的にもスラスト
軸受部の隙間精度の管理を可能にする。その構成とし
て、下記記載の構成を採用する。SUMMARY OF THE INVENTION In order to achieve the above object, a dynamic bearing device of the present invention eliminates the step structure provided in a conventional bearing sleeve and uses a thrust spacer to provide a thrust bearing surface of the bearing sleeve. It is possible to perform finishing such as grinding and polishing, and to manage the gap accuracy of the thrust bearing part even in mass production. The following configuration is employed as the configuration.
【００１１】本発明の請求項１記載の動圧軸受装置で
は、ハウジングの内周に円筒状の内周部を有する軸受ス
リーブを固定し、または、ハウジングに円筒状の外周部
を有する軸体を固定し、該軸体の外周には円筒状内周部
を有する軸受スリーブを回転自在に嵌合し、該軸受スリ
ーブの内周には円筒状外周部を有する軸体を回転自在に
嵌合し、該軸体の一部には軸体の外周部の径よりも大な
る外径のスラスト板を設けてなる動圧軸受装置に於い
て、前記スラスト板を前記軸受スリーブとスラスト受板
でスラストスペーサを介して対向に嵌合したことを特徴
とする。In the hydrodynamic bearing device according to the first aspect of the present invention, a bearing sleeve having a cylindrical inner peripheral portion is fixed to the inner periphery of the housing, or a shaft body having a cylindrical outer peripheral portion is fixed to the housing. It is fixed, and a bearing sleeve having a cylindrical inner peripheral portion is rotatably fitted to the outer periphery of the shaft, and a shaft having a cylindrical outer peripheral portion is rotatably fitted to the inner periphery of the bearing sleeve. In a hydrodynamic bearing device in which a thrust plate having an outer diameter larger than the diameter of the outer peripheral portion of the shaft body is provided in a part of the shaft body, the thrust plate is thrusted by the bearing sleeve and a thrust receiving plate. It is characterized in that they are fitted to each other via a spacer.
【００１２】本発明の請求項２記載の動圧軸受装置で
は、請求項１に記載の動圧軸受装置において、前記スラ
ストスペーサにセラミックスを用いたことを特徴とす
る。According to a second aspect of the present invention, there is provided the hydrodynamic bearing device according to the first aspect, wherein ceramic is used for the thrust spacer.
【００１３】[0013]
【発明の実施の形態】本発明の実施の形態を、図１、図
２及び図３を用いて説明する。図１は本発明の第１の実
施の形態の動圧軸受装置７及び、それを組み込んだモー
ター８の断面図であり、図２はその部分拡大図である。
モーターハウジング４５内周４６に、円筒状の内周面１
１を有する軸受スリーブ１０が固定されている。軸受ス
リーブ１０の内周面１１には円筒状外周面２を有する軸
体１が回転自在に嵌合されており、隙間３を形成してい
る。軸受スリーブ１０の内周面１１もしくは軸体１の外
周面２の少なくとも一方に動圧発生溝パターンを設ける
ことにより軸受スリーブ１０の内周面１１と軸体の１の
外周面２の間でラジアル軸受を形成している。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention will be described with reference to FIGS. FIG. 1 is a cross-sectional view of a hydrodynamic bearing device 7 according to a first embodiment of the present invention and a motor 8 incorporating the hydrodynamic bearing device, and FIG. 2 is a partially enlarged view thereof.
A cylindrical inner peripheral surface 1 is formed on the inner periphery 46 of the motor housing 45.
1, a bearing sleeve 10 is fixed. A shaft body 1 having a cylindrical outer peripheral surface 2 is rotatably fitted to an inner peripheral surface 11 of the bearing sleeve 10 to form a gap 3. By providing a dynamic pressure generating groove pattern on at least one of the inner peripheral surface 11 of the bearing sleeve 10 and the outer peripheral surface 2 of the shaft body 1, a radial is formed between the inner peripheral surface 11 of the bearing sleeve 10 and the outer peripheral surface 2 of the shaft body 1. Forming a bearing.
【００１４】また、軸体１の下部４には軸体１の外周面
２の径よりも大なる外径のスラスト板２０を設けてい
る。スラスト板２０を軸体１にスラストスペーサ３０を
介して軸受スリーブ１０とスラスト受板２５に対向する
ように嵌合し、スラスト板２０を回転自在にする為のス
ラスト軸受部の隙間を形成している。また、スラスト板
２０の上面２１と軸受スリーブ１０の下面１２の少なく
とも一方と、スラスト板２０の下面２２とスラスト受板
２５の上面２６の少なくとも一方に動圧発生溝パターン
を設けることにより、スラスト板２０と軸受スリーブ１
０、スラスト受板２５との間にスラスト軸受部を形成し
ている。Further, a thrust plate 20 having an outer diameter larger than the diameter of the outer peripheral surface 2 of the shaft body 1 is provided in the lower portion 4 of the shaft body 1. The thrust plate 20 is fitted to the shaft body 1 via the thrust spacer 30 so as to face the bearing sleeve 10 and the thrust receiving plate 25, thereby forming a gap in the thrust bearing portion for allowing the thrust plate 20 to freely rotate. I have. Further, by providing a dynamic pressure generating groove pattern on at least one of the upper surface 21 of the thrust plate 20 and the lower surface 12 of the bearing sleeve 10, and at least one of the lower surface 22 of the thrust plate 20 and the upper surface 26 of the thrust receiving plate 25, the thrust plate 20 and bearing sleeve 1
0, a thrust bearing portion is formed between the thrust bearing plate 25 and the thrust bearing plate 25.
【００１５】さらに、ラジアル軸受部及びスラスト軸受
部には潤滑流体が封入されている。軸受スリーブ１０の
上面１３には、潤滑流体の飛散を防止するためのカバー
３５を設け、そのカバー３５の軸体１の近傍の部分３６
には、ラビリンスシール構造や磁性流体シール構造を形
成することも可能である。また、モーターの回転機構に
ついては、先に図４を用いて説明した従来技術の一般的
な構成であるので、ここでは説明を省略する。Further, a lubricating fluid is sealed in the radial bearing portion and the thrust bearing portion. A cover 35 for preventing the lubricating fluid from scattering is provided on the upper surface 13 of the bearing sleeve 10, and a portion 36 of the cover 35 near the shaft 1 is provided.
It is also possible to form a labyrinth seal structure or a magnetic fluid seal structure. In addition, the rotation mechanism of the motor has the general configuration of the related art described above with reference to FIG.
【００１６】次に、軸受部の隙間管理について説明す
る。ラジアル軸受部の隙間管理は従来と同様であるので
省略し、ここでは、本発明の特徴であるスラスト軸受部
の隙間管理について説明する。スラスト軸受部の隙間
は、スラスト板２０の厚み２３とスラストスペーサ３０
の厚み３３との差だけでなく、実際には、スラスト板２
０の上面２１と下面２２との平行度及びそれぞれの平面
度、スラスト受板２５の上面２６の平面度、及び軸受ス
リーブ１０の下面１２の平面度、スラストスペーサ３０
の上面３１と下面３２との平行度及びそれぞれの平面度
等の精度を含めて管理される。Next, management of the clearance of the bearing portion will be described. The management of the clearance of the radial bearing portion is the same as that of the related art, and therefore is omitted. Here, the management of the clearance of the thrust bearing portion, which is a feature of the present invention, will be described. The gap between the thrust bearings is determined by the thickness 23 of the thrust plate 20 and the thrust spacer 30.
Not only the difference from the thickness 33 of the thrust plate 2
And the flatness of the upper surface 26 of the thrust receiving plate 25, the flatness of the lower surface 12 of the bearing sleeve 10, and the thrust spacer 30
And the accuracy such as the parallelism between the upper surface 31 and the lower surface 32 and the flatness of each.
【００１７】従来と同様に、スラスト板２０の厚み２
３、その上面２１、その下面２２、及びスラスト受板２
５の上面２６は切削加工の他、必要に応じて研削加工や
研磨加工での面仕上げ加工により、部品の精度を得るこ
とが可能であるが、さらに、本発明では、従来の軸受ス
リーブに設けた段差構造を無くし、隙間管理の為にスラ
ストスペーサ３０を設けたことにより、軸受スリーブ１
０の下面１２、スラストスペーサ３０の上面３１と下面
３２に対しても研削加工や研磨加工での面仕上げ加工が
可能である。よって、スラスト軸受部の隙間の管理に関
わるすべての部材表面に面仕上げ加工が可能な構造とな
っている。The thickness of the thrust plate 20 is 2
3, its upper surface 21, its lower surface 22, and the thrust receiving plate 2
The upper surface 26 of the fifth member 5 can be subjected to surface finishing by grinding or polishing, if necessary, in addition to cutting, so that the precision of the component can be obtained. Elimination of the step structure and the provision of the thrust spacer 30 for gap management, the bearing sleeve 1
Surface finishing by grinding or polishing can be performed on the lower surface 12 of the “0” and the upper surface 31 and the lower surface 32 of the thrust spacer 30. Therefore, the structure is such that surface finishing can be performed on all member surfaces involved in managing the clearance of the thrust bearing portion.
【００１８】動圧軸受装置７を構成する各部品には、金
属及び合金、セラミックス、ガラス、プラスチック等か
ら適宜選択して用いることが可能であるが、研削加工や
研磨加工によって寸法精度を得る部分には、加工時の弾
性変形が少なく、且つ加工中に発生する熱に対して寸法
変化の小さい材質が好ましく、その材料としてはセラミ
ックスやガラス等の脆性材料が挙げられる。その中で
も、強度が高いセラミックスを用いることはさらに好ま
しい。セラミックスの材質としては、アルミナ、ジルコ
ニア、窒化ケイ素、炭化ケイ素等を用いることが可能で
ある。しかしながら、全ての部材にセラミックスを用い
ることはコストアップにつながる為、その中でも軸受ス
リーブ１０及びスラストスペーサ３０にセラミックスを
用いて面仕上げ加工を施せば、従来の軸受スリーブ１０
３と比較して格段に寸法精度が向上する。Each component constituting the dynamic pressure bearing device 7 can be appropriately selected from metals and alloys, ceramics, glass, plastics and the like, and can be used for obtaining the dimensional accuracy by grinding or polishing. Preferably, the material is a material that undergoes little elastic deformation during processing and has a small dimensional change with respect to heat generated during processing. Examples of the material include brittle materials such as ceramics and glass. Among them, it is more preferable to use ceramics having high strength. As the material of the ceramic, alumina, zirconia, silicon nitride, silicon carbide, or the like can be used. However, since the use of ceramics for all members leads to an increase in cost, if the bearing sleeve 10 and the thrust spacer 30 are subjected to surface finishing using ceramics, the conventional bearing sleeve 10
The dimensional accuracy is remarkably improved as compared with 3.
【００１９】さらに、その中でも特に、スラストスペー
サ３０にセラミックスを用いることは最も効果が大き
く、その厚み３３の加工精度は、従来の軸受スリーブ１
０３の段差１１２の切削加工精度と比較される部分であ
ることから明らかである。具体的には、段差１１２の切
削加工精度は量産的に５μｍが限界であるが、セラミッ
クス製のスラストスペーサ３０の上面３１及び下面３２
に研磨加工を行った場合は、その厚み３３の寸法精度は
量産的にも１μｍ以下に管理可能である。Further, among them, the use of ceramics for the thrust spacer 30 is most effective, and the processing accuracy of the thickness 33 is the same as that of the conventional bearing sleeve 1.
This is apparent from the comparison with the cutting accuracy of the step 112 of No. 03. Specifically, the cutting accuracy of the step 112 is limited to 5 μm in mass production, but the upper surface 31 and the lower surface 32 of the ceramic thrust spacer 30 are limited.
When the polishing is performed, the dimensional accuracy of the thickness 33 can be controlled to 1 μm or less in mass production.
【００２０】本発明の動圧軸受装置７を組み立て、スラ
スト軸受部の隙間の製品ばらつきを測定した。尚、スラ
スト軸受部の隙間とは、単にスラストスペーサ３０の厚
み３３とスラスト板２０の厚み２３の差ではなく、前述
の様に、スラスト軸受部の隙間を構成する部材の表面の
影響を受けるので、スラスト板が実際に上下に可動な範
囲をスラスト軸受部の隙間とした。その測定は、軸体１
に嵌合したスラスト板２０をスラスト受板２５の上面２
６に押しつけた場合と、軸受スリーブ１０の下面１２に
押しつけた場合との、軸体１の面６の高さの差を測定し
て求めた。スラスト軸受部の隙間の設計値は１０．０μ
ｍとした。The dynamic pressure bearing device 7 of the present invention was assembled, and the product variation in the gap of the thrust bearing was measured. Note that the gap of the thrust bearing portion is not simply the difference between the thickness 33 of the thrust spacer 30 and the thickness 23 of the thrust plate 20, but is affected by the surface of the member constituting the gap of the thrust bearing portion as described above. The range in which the thrust plate can actually move up and down is defined as the gap between the thrust bearings. The measurement is performed on the shaft 1
The thrust plate 20 fitted to the upper surface 2 of the thrust receiving plate 25
6, and the difference between the height of the surface 6 of the shaft body 1 and the case of pressing against the lower surface 12 of the bearing sleeve 10 was determined. The design value of the clearance of the thrust bearing is 10.0μ
m.
【００２１】はじめに、軸受スリーブ１０，スラスト受
板２５、スラスト板２０、スラストスペーサ３０にはス
テンレスを用いて、軸受スリーブ１０の下面１２、スラ
スト受板２５の上面２６、スラスト板２０の上面２１と
下面２２、スラストスペーサ３０の上面３１と下面３２
に研磨加工を行い、スラストスペーサ３０の厚み３３を
最大最小範囲で１μｍ以下で使用して、本発明の動圧軸
受装置７を２０台組み立てた。スラスト軸受部の隙間を
測定したところ平均値１０．５μｍ、標準偏差０．８μ
ｍであった。次に、スラストスペーサ３０にセラミック
スを用いて、その厚み３３の最大最小範囲を０．５μｍ
以下に管理して、本発明の動圧軸受装置７を２０台組み
立てた。スラスト軸受部の隙間を測定したところ平均値
１０．１μｍ、標準偏差０．３μｍであった。First, stainless steel is used for the bearing sleeve 10, the thrust receiving plate 25, the thrust plate 20, and the thrust spacer 30, and the lower surface 12, the upper surface 26 of the thrust receiving plate 25, and the upper surface 21 of the thrust plate 20 are made of stainless steel. Lower surface 22, upper surface 31 and lower surface 32 of thrust spacer 30
Then, 20 thrust bearings 7 of the present invention were assembled using the thickness 33 of the thrust spacer 30 within a maximum and minimum range of 1 μm or less. When the gap between the thrust bearings was measured, the average value was 10.5 µm, and the standard deviation was 0.8 µm.
m. Next, using ceramics for the thrust spacer 30, the maximum and minimum range of the thickness 33 is set to 0.5 μm.
Twenty dynamic pressure bearing devices 7 of the present invention were assembled under the following management. When the gap between the thrust bearing portions was measured, the average value was 10.1 μm and the standard deviation was 0.3 μm.
【００２２】以上、本発明の第１の実施の形態より、軸
受スリーブ２０とスラストスペーサ３０とを組み合わせ
て用いる方が、従来構造の軸受スリーブ１０３よりも、
各部品の構造が単純化される為、軸受スリーブ１０の下
面１２、スラストスペーサ３０の上面３１、下面３２へ
の研削加工や研摩加工といった面仕上げの加工が可能に
なり、スラスト軸受部の隙間の各製品のばらつきを格段
に小さくすることが可能となった。また、スラストスペ
ーサにセラミックスを用いて、スラストスペーサの厚み
精度を高めると、組立後のスラスト軸受部の隙間ばらつ
きも、より小さくすることが可能である。As described above, according to the first embodiment of the present invention, the use of the bearing sleeve 20 and the thrust spacer 30 in combination is more effective than that of the bearing sleeve 103 having the conventional structure.
Since the structure of each part is simplified, the lower surface 12 of the bearing sleeve 10 and the upper surface 31 and the lower surface 32 of the thrust spacer 30 can be subjected to surface finishing such as grinding or polishing, and the clearance of the thrust bearing portion can be reduced. It has become possible to significantly reduce variations among products. Further, when the thickness accuracy of the thrust spacer is increased by using ceramics for the thrust spacer, it is possible to further reduce the variation in the gap of the thrust bearing portion after assembly.
【００２３】図３は本発明の第２の実施の形態の動圧軸
受装置５７及び、それを組み込んだモーター５８の断面
図である。第１の実施の形態は軸が回転するタイプであ
り、第２の実施の形態は軸受スリーブが回転するタイプ
である。軸受スリーブの従来の段差構造を無くして、ス
ラストスペーサを用いた特徴は第１の実施の形態と同様
であり、スラスト軸受部の隙間のばらつき範囲は第１の
実施の形態と同様の精度が得られる為、以下は動圧軸受
装置５７の構造のみを説明する。モーターハウジング９
５に、軸体５０が固定されている。軸体５０の外周には
隙間５２を形成して、軸受スリーブ６０が回転自在に嵌
合されており、軸受スリーブ６０の外周にはハブ９０が
固定されている。FIG. 3 is a sectional view of a hydrodynamic bearing device 57 according to a second embodiment of the present invention and a motor 58 incorporating the same. The first embodiment is of a type in which a shaft rotates, and the second embodiment is of a type in which a bearing sleeve rotates. The feature of using the thrust spacer without the conventional step structure of the bearing sleeve is the same as that of the first embodiment, and the variation range of the gap of the thrust bearing portion has the same accuracy as that of the first embodiment. Therefore, only the structure of the dynamic pressure bearing device 57 will be described below. Motor housing 9
5, the shaft body 50 is fixed. A gap 52 is formed on the outer periphery of the shaft body 50, and a bearing sleeve 60 is rotatably fitted therein. A hub 90 is fixed to the outer periphery of the bearing sleeve 60.
【００２４】さらに、軸体５０にはその径よりも大なる
外径のスラスト板７０を設けている。スラスト板７０を
軸体５０にスラストスペーサ８０を介して軸受スリーブ
６０とスラスト受板７５に対向するように嵌合し、スラ
スト板７０を回転自在にする為のスラスト軸受部の隙間
を形成している。軸受スリーブ６０の内周面６１もしく
は軸体５０の外周面５１の少なくとも一方に動圧発生溝
パターンを設けることにより軸受スリーブ６０の内周面
６１と軸体の５０の外周面５１の間でラジアル軸受部を
形成している。Further, the shaft body 50 is provided with a thrust plate 70 having an outer diameter larger than its diameter. The thrust plate 70 is fitted to the shaft body 50 via the thrust spacer 80 so as to face the bearing sleeve 60 and the thrust receiving plate 75, and a gap is formed between the thrust bearing portions so that the thrust plate 70 can freely rotate. I have. By providing a dynamic pressure generating groove pattern on at least one of the inner peripheral surface 61 of the bearing sleeve 60 or the outer peripheral surface 51 of the shaft body 50, a radial is formed between the inner peripheral surface 61 of the bearing sleeve 60 and the outer peripheral surface 51 of the shaft body 50. A bearing portion is formed.
【００２５】また、スラスト板７０の下面７１と軸受ス
リーブ６０の上面６２の少なくとも一方と、スラスト板
７０の上面７２とスラスト受板７５の下面７６の少なく
とも一方に動圧発生溝パターンを設けることにより、ス
ラスト板７０と軸受スリーブ６０、スラスト受板７５と
の間にスラスト軸受部を形成している。また、ラジアル
軸受部及びスラスト軸受部には潤滑流体が封入されてい
る。軸受スリーブ６０の下面６３には、潤滑流体の飛散
を防止するためのカバー８５を設けている。モーターの
回転機構については、先に図４の用いて説明した従来技
術と同様にの一般的な構成を応用することが可能であ
る。The dynamic pressure generating groove pattern is provided on at least one of the lower surface 71 of the thrust plate 70 and the upper surface 62 of the bearing sleeve 60, and at least one of the upper surface 72 of the thrust plate 70 and the lower surface 76 of the thrust receiving plate 75. A thrust bearing is formed between the thrust plate 70, the bearing sleeve 60, and the thrust receiving plate 75. Further, a lubricating fluid is sealed in the radial bearing portion and the thrust bearing portion. A cover 85 for preventing the lubricating fluid from scattering is provided on the lower surface 63 of the bearing sleeve 60. Regarding the rotation mechanism of the motor, it is possible to apply a general configuration similar to that of the prior art described above with reference to FIG.
【００２６】[0026]
【発明の効果】以上の実施の形態から明らかなように、
請求項１に記載の本発明の動圧軸受装置の構造によれ
ば、軸受スリーブとスラストスペーサの２部品を組み合
わせて用いる方が、従来構造のように段加工を必要とす
る軸受スリーブ１部品よりも、部品の構造が単純化さ
れ、研削加工や研磨加工といった面仕上げの加工が可能
になる為に部品の加工精度が向上し、スラスト軸受部の
隙間の製品のばらつきを小さく抑えることが可能となっ
た。As is clear from the above embodiment,
According to the structure of the hydrodynamic bearing device according to the first aspect of the present invention, it is preferable to use the bearing sleeve and the thrust spacer in combination of two parts, as compared with the conventional bearing, which requires one step processing as in the conventional structure. In addition, since the structure of the parts is simplified, surface finishing such as grinding and polishing can be performed, the processing accuracy of the parts is improved, and it is possible to reduce the variation in the product of the gap in the thrust bearing part. became.
【００２７】また、請求項２の本発明の動圧軸受装置に
よれば、加工時の弾性変形が少なく、加工中に発生する
熱に対して寸法変化の小さいセラミックスをスラストス
ペーサに用いることにより、スラストスペーサの加工精
度を更に向上させることが可能であると共に、スラスト
軸受部の隙間の製品ばらつきをさらに小さく抑えること
が可能となった。According to the hydrodynamic bearing device of the present invention, the elastic deformation at the time of working is small, and the ceramic having a small dimensional change with respect to the heat generated during the working is used for the thrust spacer. The processing accuracy of the thrust spacer can be further improved, and the product variation in the gap of the thrust bearing can be further reduced.
【図１】本発明の動圧軸受装置を組み込んだモーターを
示す模式断面図。FIG. 1 is a schematic sectional view showing a motor incorporating a dynamic pressure bearing device of the present invention.
【図２】本発明の動圧軸受装置を組み込んだモーターを
示す模式断面図の部分拡大図。FIG. 2 is a partially enlarged view of a schematic sectional view showing a motor incorporating the dynamic pressure bearing device of the present invention.
【図３】本発明の動圧軸受装置を組み込んだモーターを
示す模式断面図。FIG. 3 is a schematic sectional view showing a motor incorporating the dynamic bearing device of the present invention.
【図４】従来の動圧軸受装置を組み込んだモーターを示
す模式断面図。FIG. 4 is a schematic cross-sectional view showing a motor incorporating a conventional hydrodynamic bearing device.
【図５】従来の動圧軸受装置を組み込んだモーターを示
す模式断面図の部分拡大図。FIG. 5 is a partially enlarged view of a schematic sectional view showing a motor incorporating a conventional dynamic pressure bearing device.
１、５０ 軸体 ２、５１ 外周面 ３、５２ 隙間 ４ 下部 ６ 面 ７、５７ 動圧軸受装置 ８、５８ モーター １０、６０ 軸受スリーブ １１、６１ 内周面 １２、２２、３２、６３、７１、７６ 下面 １３、２１、２６、３１、６２、７２ 上面 ２０、７０ スラスト板 ２３、３３ 厚み ２５、７５ スラスト受板 ３０、８０ スラストスペーサ ３５、８５ カバー ３６ 部分 ４５、９５ モーターハウジング ４６ 内周 ９０ ハブ 1, 50 shaft body 2, 51 outer peripheral surface 3, 52 gap 4 lower 6 surface 7, 57 dynamic pressure bearing device 8, 58 motor 10, 60 bearing sleeve 11, 61 inner peripheral surface 12, 22, 32, 63, 71, 76 Lower surface 13, 21, 26, 31, 62, 72 Upper surface 20, 70 Thrust plate 23, 33 Thickness 25, 75 Thrust receiving plate 30, 80 Thrust spacer 35, 85 Cover 36 Part 45, 95 Motor housing 46 Inner circumference 90 Hub
フロントページの続き (72)発明者 柴 和男 東京都田無市本町６丁目１番12号 シチズ ン時計株式会社田無製造所内 (72)発明者 金澤 豊次 東京都田無市本町６丁目１番12号 シチズ ン時計株式会社田無製造所内 Ｆターム(参考） 3J011 BA04 DA01 KA04 QA01 SD01Continued on the front page (72) Inventor Kazuo Shiba 6-11-12 Honcho, Tanashi-shi, Tokyo Citizen Watch Co., Ltd. Inside Tanashi Works (72) Inventor Toyoji Kanazawa 6-1-112, Honcho, Tanashi-shi, Tokyo Citizen Watch Term Co., Ltd. Tanashi Factory F-term (reference) 3J011 BA04 DA01 KA04 QA01 SD01
Claims (2)
する軸受スリーブを固定し、該軸受スリーブの内周には
円筒状外周部を有する軸体を回転自在に嵌合し、また
は、ハウジングに円筒状の外周部を有する軸体を固定
し、該軸体の外周には円筒状内周部を有する軸受スリー
ブを回転自在に嵌合し、該軸体の一部には軸体の外周部
の径よりも大なる外径のスラスト板を設けてなる動圧軸
受装置に於いて、前記スラスト板を前記軸受スリーブと
スラスト受板でスラストスペーサを介して対向に嵌合し
たことを特徴とする動圧軸受装置。1. A bearing sleeve having a cylindrical inner peripheral portion is fixed to an inner periphery of a housing, and a shaft having a cylindrical outer peripheral portion is rotatably fitted to an inner periphery of the bearing sleeve. A shaft having a cylindrical outer peripheral portion is fixed to the housing, a bearing sleeve having a cylindrical inner peripheral portion is rotatably fitted to the outer periphery of the shaft, and a part of the shaft is In a hydrodynamic bearing device provided with a thrust plate having an outer diameter larger than the diameter of the outer peripheral portion, the thrust plate is fitted to the bearing sleeve and a thrust receiving plate so as to face each other via a thrust spacer. Dynamic bearing device.
用いたことを特徴とする請求項１記載の動圧軸受装置。2. The dynamic pressure bearing device according to claim 1, wherein ceramic is used for said thrust spacer.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP11191314A JP2001020946A (en) | 1999-07-06 | 1999-07-06 | Dynamic pressure bearing device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP11191314A JP2001020946A (en) | 1999-07-06 | 1999-07-06 | Dynamic pressure bearing device |
Related Child Applications (4)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2006147513A Division JP2006220311A (en) | 2006-05-29 | 2006-05-29 | Dynamic pressure bearing device |
| JP2006147511A Division JP2006234176A (en) | 2006-05-29 | 2006-05-29 | Dynamic pressure bearing device |
| JP2006147510A Division JP2006220309A (en) | 2006-05-29 | 2006-05-29 | Dynamic pressure bearing device |
| JP2006147512A Division JP2006220310A (en) | 2006-05-29 | 2006-05-29 | Dynamic pressure bearing device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JP2001020946A true JP2001020946A (en) | 2001-01-23 |
| JP2001020946A5 JP2001020946A5 (en) | 2006-07-20 |
Family
ID=16272506
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP11191314A Pending JP2001020946A (en) | 1999-07-06 | 1999-07-06 | Dynamic pressure bearing device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2001020946A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2003036111A1 (en) * | 2001-10-24 | 2003-05-01 | Sony Corporation | Bearing unit, and motor using this bearing unit |
| JP2007211845A (en) * | 2006-02-08 | 2007-08-23 | Crd Kk | Hydrodynamic bearing motor |
| US7455456B2 (en) | 2003-01-10 | 2008-11-25 | Sony Corporation | Bearing unit and rotation drive device using the same |
-
1999
- 1999-07-06 JP JP11191314A patent/JP2001020946A/en active Pending
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2003036111A1 (en) * | 2001-10-24 | 2003-05-01 | Sony Corporation | Bearing unit, and motor using this bearing unit |
| US7029179B2 (en) | 2001-10-24 | 2006-04-18 | Sony Corporation | Bearing unit, and motor using same |
| CN100339603C (en) * | 2001-10-24 | 2007-09-26 | 索尼公司 | Bearing unit and motor provided therewith |
| CN100458195C (en) * | 2001-10-24 | 2009-02-04 | 索尼公司 | Bearing unit and motor provided therewith |
| KR100927247B1 (en) * | 2001-10-24 | 2009-11-16 | 소니 가부시끼 가이샤 | Bearing unit and motor using this bearing unit |
| US7455456B2 (en) | 2003-01-10 | 2008-11-25 | Sony Corporation | Bearing unit and rotation drive device using the same |
| US7510329B2 (en) | 2003-01-10 | 2009-03-31 | Sony Corporation | Bearing unit and rotary drive using the same |
| JP2007211845A (en) * | 2006-02-08 | 2007-08-23 | Crd Kk | Hydrodynamic bearing motor |
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