JPH051715A - Bearing structure - Google Patents
Bearing structureInfo
- Publication number
- JPH051715A JPH051715A JP15447591A JP15447591A JPH051715A JP H051715 A JPH051715 A JP H051715A JP 15447591 A JP15447591 A JP 15447591A JP 15447591 A JP15447591 A JP 15447591A JP H051715 A JPH051715 A JP H051715A
- Authority
- JP
- Japan
- Prior art keywords
- shaft
- bearing
- gap
- bearing structure
- frictional force
- 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]
【産業上の利用分野】本発明は軸と軸受との間隙に潤滑
油を充填し、該潤滑油の潤滑作用で軸受に対して、軸を
円滑に回転させるようになっている軸受構造において、
軸と軸受との間の摩擦力の低下と、軸と軸受との間のガ
タつきの防止とを共に（同時）に図ることができるよう
にしたものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a bearing structure in which a gap between a shaft and a bearing is filled with lubricating oil, and the shaft is smoothly rotated with respect to the bearing by the lubricating action of the lubricating oil.
The reduction of the frictional force between the shaft and the bearing and the prevention of rattling between the shaft and the bearing can both be (simultaneously) achieved.
【０００２】[0002]
【従来の技術】軸受構造として、図４に示したように、
軸１０１と軸受１０２との間の全周に亘って一定の間隙
ｃを設け、該間隙ｃ内に潤滑油１０３を充填し、該潤滑
油１０３の潤滑作用で軸１０１を円滑に回転させるよう
にしたものが知られている。2. Description of the Related Art As a bearing structure, as shown in FIG.
A constant gap c is provided over the entire circumference between the shaft 101 and the bearing 102, the lubricating oil 103 is filled in the gap c, and the lubricating action of the lubricating oil 103 causes the shaft 101 to rotate smoothly. What you have done is known.
【０００３】[0003]
【発明が解決しようとする課題】ところで上記従来の軸
受構造においては、軸１０１と軸受１０２の間のガタつ
きと摩擦力との関係は二律背反の関係にあり、軸１０１
と軸受１０２の間のガタつきを少なくするために両者の
間の間隙ｃを小さくすると両者間の摩擦力が増大し、負
荷が増大するという問題点があった。In the conventional bearing structure described above, the relationship between the backlash and the frictional force between the shaft 101 and the bearing 102 is a trade-off relationship.
If the gap c between the bearing and the bearing 102 is reduced in order to reduce rattling, the frictional force between the two increases and the load increases.
【０００４】即ち、上記摩擦力Ｆは一般に以下に示す式
で表わされ、間隙ｃが小さくなればなる程、摩擦力は増
大するからである。That is, the frictional force F is generally expressed by the following formula, and the smaller the gap c, the greater the frictional force.
【０００５】[0005]
【数１】 [Equation 1]
【０００６】本発明は上記従来の問題点を解決し、軸と
軸受の間の間隙を小さくし、両者間のガタつきを少なく
すると共に、両者間の摩擦力をも低減することのできる
軸受構造を提供することを目的として為されたものであ
る。The present invention solves the above-mentioned problems of the prior art, reduces the gap between the shaft and the bearing, reduces rattling between them, and also reduces the frictional force between them. The purpose is to provide.
【０００７】[0007]
【課題を解決するための手段】軸と軸受との間隙に潤滑
油を充填し、該潤滑油の潤滑作用で軸を円滑に回転させ
る軸受構造において、前記間隙を、小間隙部と、大間隙
部を軸の回転方向に交互に連続させることにより形成し
た。In a bearing structure in which a gap between a shaft and a bearing is filled with lubricating oil and the shaft is smoothly rotated by the lubricating action of the lubricating oil, the gap is divided into a small gap portion and a large gap. It was formed by alternately connecting the parts in the direction of rotation of the shaft.
【０００８】[0008]
【作用】軸と軸受との間の間隙のうち、小間隙部が軸と
軸受の間のガタつきを防止する。The small gap portion of the gap between the shaft and the bearing prevents rattling between the shaft and the bearing.
【０００９】また、小間隙部による摩擦力の増大を大間
隙部で減少させる。Further, the increase in frictional force due to the small gap portion is reduced in the large gap portion.
【００１０】従って、軸と軸受との間隙を少なくして、
両者間のガタつきを少なくした軸受構造と、軸と軸受と
の間隙を大きくして、摩擦力を低減させた軸受構造の、
それぞれの長所を有する軸受構造を得ることができる。Therefore, by reducing the gap between the shaft and the bearing,
The bearing structure that reduces rattling between the two and the bearing structure that reduces the frictional force by increasing the gap between the shaft and the bearing,
A bearing structure having the respective advantages can be obtained.
【００１１】[0011]
【実施例】次に本発明を図１〜図３に基づいて説明す
る。DESCRIPTION OF THE PREFERRED EMBODIMENTS Next, the present invention will be described with reference to FIGS.
【００１２】図１において１は本発明の軸受構造２を使
用したフロッピーディスクドライブ用のスピンドルモー
タである。In FIG. 1, reference numeral 1 is a spindle motor for a floppy disk drive using a bearing structure 2 of the present invention.
【００１３】上記軸受構造２は軸３と軸受４との間隙に
潤滑油（図示省略）を充填し、該潤滑油の潤滑作用で軸
４を円滑に回転させるようになっている。The bearing structure 2 is configured such that a gap between the shaft 3 and the bearing 4 is filled with lubricating oil (not shown), and the shaft 4 is smoothly rotated by the lubricating action of the lubricating oil.
【００１４】そして、上記軸３の上端側にはロータアッ
シー５が組付けられ、軸受４の下端側にはステータアッ
シー６が組付けられている。A rotor assembly 5 is attached to the upper end of the shaft 3 and a stator assembly 6 is attached to the lower end of the bearing 4.
【００１５】上記ロータアッシー５はターンテーブル７
と、該ターンテーブル７の上面側に取付けられたディス
クチャック用マグネット８と、上記ターンテーブル７の
下面側に取付けられたバックヨーク９と、該バックヨー
クの下面に取付けられた駆動用のマグネット１０とから
なっている。The rotor assembly 5 is a turntable 7
A disk chuck magnet 8 mounted on the upper surface side of the turntable 7, a back yoke 9 mounted on the lower surface side of the turntable 7, and a driving magnet 10 mounted on the lower surface of the back yoke. It consists of
【００１６】また、上記ステータアッシー６は、珪素鋼
板で作られたステータ１１と、該ステータ１１の上面側
に、上記駆動用のマグネット１０と対向させた状態で取
付けられたコイル１２とからなっていて、該コイル１２
に通電することにより、上記軸４を中心にしてロータア
ッシー５を回転させるようになっている。The stator assembly 6 is composed of a stator 11 made of a silicon steel plate, and a coil 12 mounted on the upper surface of the stator 11 so as to face the driving magnet 10. The coil 12
By energizing the rotor 4, the rotor assembly 5 is rotated about the shaft 4.
【００１７】前記軸３と軸受４との間隙は、図２に示し
たように、小間隙部ｃと大間隙部ｃnを軸３の回転方向
に交互に連続させることにより、軸３と軸受４の対向面
（摺動面）の全域に亘って形成されている。As shown in FIG. 2, the gap between the shaft 3 and the bearing 4 is such that the small gap portion c and the large gap portion c n are alternately continuous in the rotation direction of the shaft 3 so that the shaft 3 and the bearing are 4 is formed over the entire area of the facing surface (sliding surface).
【００１８】上記小間隙部ｃと大間隙ｃnの長さの比率
はλ＝１−λに設定されている。The ratio of the lengths of the small gap portion c and the large gap c n is set to λ = 1−λ.
【００１９】上記（１）の式から小間隙部ｃの摩擦力Ｆ
と大間隙部ｃnの摩擦力Ｆnは、それぞれ次の式で表わさ
れる。From the above equation (1), the frictional force F of the small gap portion c
And the frictional force F n of the large gap part c n is expressed by the following equations.
【００２０】[0020]
【数２】 [Equation 2]
【００２１】そして、単位長さ（Ｌ）での平均摩擦力Ｆ
Mは、次の式で求められる。Then, the average frictional force F in the unit length (L)
M is calculated by the following formula.
【００２２】[0022]
【数３】 [Equation 3]
【００２３】従って、図４に示した全周が均一の間隙ｃ
の軸受構造の摩擦力と、本発明の大小の間隙ｃ、間隙ｃ
nを有する混合間隙の軸受構造の摩擦力を比較すると次
の式のようになる。Therefore, the gap c shown in FIG.
Frictional force of the bearing structure and the large and small gaps c and c of the present invention
Comparing the friction forces of bearing structures with mixed gaps having n , the following equation is obtained.
【００２４】[0024]
【数４】 [Equation 4]
【００２５】上記（５）式をグラフにすると図３に示す
ようになり、０＜ｃ／ｃn＜１の領域内において、ＦM／
Ｆ値が小さいほど有利であり、ＦM／Ｆがλに近付くほ
ど大きな効果を発揮する。FIG. 3 is a graph of the above equation (5). In the region of 0 <c / c n <1, F M /
The smaller the F value is, the more advantageous it is, and the closer the F M / F is to λ, the greater the effect.
【００２６】次に具体的な計算例を示すと、図２の軸受
構造において、λ＝０．６、ｃ／ｃn＝０．１とする
と、式（５）から ＦM／Ｆ＝０．６＋（１−０．６）×０．１＝０．６４ となり、摩擦力は全周が全て間隙ｃのものの場合の摩擦
力の６４％に減少する。Next, a specific calculation example will be given. In the bearing structure of FIG. 2, assuming that λ = 0.6 and c / c n = 0.1, from the formula (5), F M / F = 0. 6+ (1-0.6) × 0.1 = 0.64, and the frictional force is reduced to 64% of the frictional force in the case where the entire circumference has the gap c.
【００２７】なお、図面に示した実施例では、軸２の外
周面の長さ方向に同一幅の溝２１…２１を穿設し、該溝
２１…２１の部分を大間隙ｃnとし、溝２１…２１を穿
設していない部分を小間隙部ｃとした場合を示したが、
これとは逆に、軸受２の内周面に溝を形成して、大，小
間隙部ｃn，ｃを形成してもよい。[0027] In the embodiment shown in the drawings, bored grooves 21 ... 21 of the same width in the longitudinal direction of the outer peripheral surface of the shaft 2, a portion of the groove 21 ... 21 and the large gap c n, a groove The case where the portion where 21 ... 21 is not formed is the small gap portion c is shown.
On the contrary, a groove may be formed on the inner peripheral surface of the bearing 2 to form the large and small gap parts c n , c.
【００２８】また、大，小間隙ｃn，ｃを形成する手段
は問わない。The means for forming the large and small gaps c n , c is not limited.
【００２９】[0029]
【発明の効果】本発明の軸受構造は以上、説明したよう
な構成であって、軸と軸受との間隙を、軸の回転方向に
連続する小間隙部と大間隙部とで構成したので、上記小
間隙部で軸と軸受との間のガタつきを防止し、大間隙部
で摩擦力の低減を図り、ガタつき防止と摩擦力の低減と
いう従来、同時に得ることは不可能とされていた二律背
反的な効果を得ることを可能にするという効果がある。The bearing structure of the present invention has the structure as described above, and the gap between the shaft and the bearing is constituted by the small gap portion and the large gap portion which are continuous in the rotation direction of the shaft. In the past, it was impossible to prevent rattling between the shaft and the bearing in the small gap portion and to reduce the frictional force in the large gap portion to prevent the rattling and reduce the frictional force at the same time. There is an effect that it is possible to obtain an antinomy effect.
【図１】本発明の軸受構造を施したスピンドルモータの
断面図。FIG. 1 is a sectional view of a spindle motor provided with a bearing structure of the present invention.
【図２】要部の断面図。FIG. 2 is a sectional view of a main part.
【図３】本発明の軸受構造の効果を示すグラフ図。FIG. 3 is a graph showing the effect of the bearing structure of the present invention.
【図４】従来の軸受構造の断面図。FIG. 4 is a sectional view of a conventional bearing structure.
２…軸受構造、３…軸、４…軸受、ｃ…小間隙部、ｃn
…大間隙部。2 ... bearing structure, 3 ... shaft, 4 ... bearing, c ... small gap, c n
… Large gap.
Claims (1)
潤滑油の潤滑作用で軸を円滑に回転させる軸受構造にお
いて、前記間隙は、小間隙部と、大間隙部を軸の回転方
向に交互に連続させることにより形成されていることを
特徴とする軸受構造。Claim: What is claimed is: 1. A bearing structure in which a lubricating oil is filled in a gap between a shaft and a bearing, and the shaft is smoothly rotated by a lubricating action of the lubricating oil. A bearing structure, characterized in that the large gap portion is formed by alternately continuing in the rotation direction of the shaft.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP15447591A JPH051715A (en) | 1991-06-26 | 1991-06-26 | Bearing structure |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP15447591A JPH051715A (en) | 1991-06-26 | 1991-06-26 | Bearing structure |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH051715A true JPH051715A (en) | 1993-01-08 |
Family
ID=15585068
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP15447591A Pending JPH051715A (en) | 1991-06-26 | 1991-06-26 | Bearing structure |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH051715A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO1998038433A1 (en) * | 1997-02-28 | 1998-09-03 | Sumitomo Electric Industries, Ltd. | Dynamic pressure pneumatic bearing structure and method of its manufacture |
-
1991
- 1991-06-26 JP JP15447591A patent/JPH051715A/en active Pending
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO1998038433A1 (en) * | 1997-02-28 | 1998-09-03 | Sumitomo Electric Industries, Ltd. | Dynamic pressure pneumatic bearing structure and method of its manufacture |
| WO1998038434A1 (en) * | 1997-02-28 | 1998-09-03 | Sumitomo Electric Industries, Ltd. | Dynamic pressure pneumatic bearing structure and optical deflection scanner employing the structure |
| US6082900A (en) * | 1997-02-28 | 2000-07-04 | Sumitomo Electric Industries, Ltd. | Dynamic pressure pneumatic bearing structure and method of manufacturing the same |
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