JPH0416014Y2 - - Google Patents
Info
- Publication number
- JPH0416014Y2 JPH0416014Y2 JP1987164639U JP16463987U JPH0416014Y2 JP H0416014 Y2 JPH0416014 Y2 JP H0416014Y2 JP 1987164639 U JP1987164639 U JP 1987164639U JP 16463987 U JP16463987 U JP 16463987U JP H0416014 Y2 JPH0416014 Y2 JP H0416014Y2
- Authority
- JP
- Japan
- Prior art keywords
- fixed shaft
- bearing surface
- rotating member
- base
- radial bearing
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired
Links
- 239000010935 stainless steel Substances 0.000 claims description 7
- 229910001220 stainless steel Inorganic materials 0.000 claims description 7
- 230000002093 peripheral effect Effects 0.000 description 8
- 230000005291 magnetic effect Effects 0.000 description 4
- 230000004323 axial length Effects 0.000 description 3
- 238000004891 communication Methods 0.000 description 3
- 230000000694 effects Effects 0.000 description 3
- 239000012530 fluid Substances 0.000 description 3
- 239000000463 material Substances 0.000 description 2
- 238000005086 pumping Methods 0.000 description 2
- 229910000838 Al alloy Inorganic materials 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 239000003302 ferromagnetic material Substances 0.000 description 1
- 239000011521 glass Substances 0.000 description 1
- 238000007639 printing Methods 0.000 description 1
- 230000001846 repelling effect Effects 0.000 description 1
Description
【考案の詳細な説明】
〔産業上の利用分野〕
この考案は産業用機器、事務用機器等に使用さ
れる動圧形流体軸受装置に関する。[Detailed Description of the Invention] [Industrial Application Field] This invention relates to a hydrodynamic bearing device used in industrial equipment, office equipment, etc.
従来は、縦弾性係数が約7200Kgｆ／mm2のアルミ
ニウム合金からなる基台に縦弾性係数が約20400
Kgｆ／mm2のステンレス鋼からなる固定軸の一方の
端部を取付けている。前記基台の軸方向長さは固
定軸の直径より短かく、この固定軸に回転部材の
円筒状孔を嵌合している。前記固定軸の外周面に
設けた円筒状のラジアル軸受面が回転部材に設け
たラジアル受面に対向し、このラジアル受面にス
パイラル状のみぞが設けられている。前記固定軸
の端面に設けたスラスト受面が回転部材に設けた
スラスト軸受面に対向し、このスラスト軸受面と
スラスト受面とから構成されるスラスト流体軸受
は回転部材を軸方向に支持する手段となつてい
る。前記スラスト軸受面の半径方向中心部には回
転部材の外部に開口する流通穴が設けられ、また
ラジアル受面とラジアル軸受面との間のラジアル
軸受すきま及びスラスト受面とスラスト軸受面と
の間のスラスト軸受すきまには気体がそれぞれ存
在している。
Conventionally, a base made of aluminum alloy with a longitudinal elastic modulus of about 7200 Kgf/mm 2 has a longitudinal elastic modulus of about 20400.
One end of a fixed shaft made of Kgf/mm 2 stainless steel is attached. The axial length of the base is shorter than the diameter of the fixed shaft, and the cylindrical hole of the rotating member is fitted into the fixed shaft. A cylindrical radial bearing surface provided on the outer peripheral surface of the fixed shaft faces a radial bearing surface provided on the rotating member, and a spiral groove is provided in this radial bearing surface. A thrust bearing surface provided on the end face of the fixed shaft faces a thrust bearing surface provided on the rotating member, and a thrust fluid bearing composed of the thrust bearing surface and the thrust bearing surface is a means for supporting the rotating member in the axial direction. It is becoming. A communication hole that opens to the outside of the rotating member is provided in the radial center of the thrust bearing surface, and a radial bearing clearance between the radial bearing surfaces and between the thrust bearing surfaces. Gas exists in each thrust bearing clearance.
レーザビームプリンタでは印字速度の高速化が
要望され、このような装置に使用される動圧形流
体軸受装置の高速回転限界数の向上が要望されて
いる。
In laser beam printers, there is a demand for higher printing speeds, and there is a demand for an increase in the high-speed rotation limit number of hydrodynamic bearing devices used in such devices.
この考案は高速回転限界数が向上する動圧形流
体軸受装置を提供することを目的とする。 The object of this invention is to provide a hydrodynamic bearing device with improved high-speed rotation limit speed.
基台に固定軸の一方の端部を取付け、この固定
軸に回転部材の円筒状孔を嵌合している。前記固
定軸の外周面に設けた円筒状のラジアル受面が回
転部材に設けたラジアル軸受面に対向し、このラ
ジアル軸受面とラジアル受面との少なくとも一方
に動圧発生用みぞを設けている。前記回転部材を
軸方向に支持する手段を備え、また基台と固定軸
とはいずれも縦弾性係数が18000Kgｆ／mm2以上で
ある。
One end of a fixed shaft is attached to the base, and the cylindrical hole of the rotating member is fitted into the fixed shaft. A cylindrical radial bearing surface provided on the outer peripheral surface of the fixed shaft faces a radial bearing surface provided on the rotating member, and a groove for generating dynamic pressure is provided in at least one of the radial bearing surface and the radial bearing surface. . Means for supporting the rotating member in the axial direction is provided, and both the base and the fixed shaft have a longitudinal elastic modulus of 18000 Kgf/mm 2 or more.
回転部材が回転すると動圧発生用みぞのポンピ
ング作用によつてラジアル軸受面はラジアル受面
と非接触で回転する。基台と固定軸とはいずれも
剛性が高いので回転部材の固定軸に対する回転時
に動圧形流体軸受装置の共振周波数が高く、動圧
形流体軸受装置の高速回転限界数が向上する。
When the rotating member rotates, the radial bearing surface rotates without contacting the radial bearing surface due to the pumping action of the dynamic pressure generating groove. Since both the base and the fixed shaft have high rigidity, the resonance frequency of the hydrodynamic bearing device is high when the rotating member rotates with respect to the fixed shaft, and the high speed rotation limit number of the hydrodynamic bearing device is improved.
この考案の実施例を図面に基いて説明する。第
１図はこの考案の動圧形流体軸受装置を使用した
レーザビームプリンタのポリゴンミラースキヤナ
であるが、基台１はSUS304，SUS303等のステ
ンレス鋼からなつている。前記基台１のステンレ
ス鋼は縦弾性係数が約19700Kgｆ／mm2であり、、あ
た基台１には固定軸３の一方の端部が焼ばめによ
つて取付けられている。前記固定軸３は
SUS420J2，SUS440C等のステンレス鋼からな
り、この固定軸３のステンレス鋼の縦弾性係数は
約20400Kgｆ／mm2である。前記基台１の固定軸３
への取付部分４の軸方向長さは固定軸３の直径以
上である。
An embodiment of this invention will be described based on the drawings. FIG. 1 shows a polygon mirror scanner for a laser beam printer using the hydrodynamic bearing device of this invention, and the base 1 is made of stainless steel such as SUS304 or SUS303. The stainless steel of the base 1 has a modulus of longitudinal elasticity of approximately 19,700 Kgf/mm 2 , and one end of the fixed shaft 3 is attached to the base 1 by shrink fitting. The fixed shaft 3 is
It is made of stainless steel such as SUS420J2 and SUS440C, and the longitudinal elastic modulus of the stainless steel of this fixed shaft 3 is approximately 20400 Kgf/mm 2 . Fixed shaft 3 of the base 1
The axial length of the attachment portion 4 to the fixed shaft 3 is greater than or equal to the diameter of the fixed shaft 3.
前記固定軸３に回転部材の円筒状孔５を嵌合
し、この固定軸３の外周面には円筒状のラジアル
受面１１が設けられている。前記ラジアル受面１
１には動圧発生用みぞ１２が設けられ、また固定
軸３の上方の端面には凸球面状のスラスト受面１
３が設けられている。前記回転部材１９はスリー
ブ２１とスリーブ２１の内周面の一方の端部に嵌
合して取付けた嵌合部材２３とから構成されてい
る。前記回転部材１９の内周面にはラジアル受面
１１に対向する円筒状のラジアル軸受面２７が設
けられ、また回転部材１９にはスラスト受面１３
に対向する平面状のスラスト軸受面２９が設けら
れている。前記スラスト受面１３とスラスト軸受
面２９とを備えたスラスト流体軸受は回転部材１
９を軸方向に支持する手段であり、またスラスト
軸受面２９の半径方向の中央部には回転部材１９
の外面へ開口する流通穴３１が設けられている。
前記回転部材１９の上部に設けたフランジには多
面鏡３５が取付けられ、また回転部材１９の下部
の外周面にはロータ４３が取付けられている。前
記回転部材１９を覆うケース５３が基台１に取付
けられ、このケース５３は下方のステータ取付部
５５と上方のカバー部材５７とから構成されてい
る。前記カバー部材５７には多面鏡３５と水平方
向に対向する位置にガラス窓５９が設けられ、ま
たステータ取付部材５５の内周面にはロータ４３
に半径方向に対向するステータ６１が取付けられ
ている。 A cylindrical hole 5 of a rotating member is fitted into the fixed shaft 3, and a cylindrical radial receiving surface 11 is provided on the outer peripheral surface of the fixed shaft 3. Said radial receiving surface 1
1 is provided with a groove 12 for generating dynamic pressure, and a convex spherical thrust bearing surface 1 is provided on the upper end surface of the fixed shaft 3.
3 is provided. The rotating member 19 is composed of a sleeve 21 and a fitting member 23 fitted and attached to one end of the inner peripheral surface of the sleeve 21. A cylindrical radial bearing surface 27 facing the radial bearing surface 11 is provided on the inner peripheral surface of the rotating member 19, and a thrust bearing surface 13 is provided on the rotating member 19.
A planar thrust bearing surface 29 facing the is provided. The thrust fluid bearing including the thrust bearing surface 13 and the thrust bearing surface 29 is attached to the rotating member 1.
9 in the axial direction, and a rotating member 19 is provided at the center of the thrust bearing surface 29 in the radial direction.
A communication hole 31 is provided that opens to the outer surface.
A polygon mirror 35 is attached to a flange provided on the upper part of the rotating member 19, and a rotor 43 is attached to the outer peripheral surface of the lower part of the rotating member 19. A case 53 that covers the rotating member 19 is attached to the base 1, and the case 53 is composed of a lower stator mounting portion 55 and an upper cover member 57. The cover member 57 is provided with a glass window 59 at a position horizontally facing the polygon mirror 35, and the rotor 43 is provided on the inner peripheral surface of the stator mounting member 55.
Radially opposed stators 61 are attached to the radially opposite stators 61 .
以上のような構成で回転部材１９が回転する
と、動圧発生用みぞ１２のポンピング作用によつ
てケース５３内の下方の気体がラジアル軸受面２
７とラジアル受面１１との間のラジアル軸受すき
ま、スラスト軸受面２９とスラスト受面１３との
間のスラスト軸受すきま及び流通穴３１を通つて
循環する。従つて、回転部材１９は固定軸３に非
接触状態で支持されて回転する。 When the rotating member 19 rotates with the above configuration, the gas in the lower part of the case 53 is pumped to the radial bearing surface 2 by the pumping action of the hydrodynamic groove 12.
7 and the radial bearing surface 11 , the thrust bearing clearance between the thrust bearing surface 29 and the thrust bearing surface 13 , and the circulation hole 31 . Therefore, the rotating member 19 is supported by the fixed shaft 3 in a non-contact state and rotates.
前記回転部材１９の高速回転限界数は基台１と
固定軸３と回転部材１９とを備えた動圧形流体軸
受装置の共振周波数に左右されることがわかり、
またこの共振周波数の向上には基台１と固定軸３
との取付部の剛性を高めることが有効であること
がわかつてきた。そこで、基台１と固定軸３との
両方の縦弾性係数をいずれも18000Kgｆ／mm2以上
にすると、基台１と固定軸３との取付部の支持剛
性が高くなり、動圧形流体軸受装置の共振周波数
が向上するので回転部材１９の高速回転限界数を
大幅に向上させることができる。なお、基台１と
固定軸３との少なくとも一方の縦弾性係数18000
Kgｆ／mm2より低くすると基台１と固定軸３との取
付部の支持剛性が不充分であり、また基台１と固
定軸３との縦弾性係数が可能な限り高い方が基台
１と固定軸３との取付部の支持剛性の向上が好ま
しい。 It can be seen that the high speed rotation limit number of the rotating member 19 depends on the resonance frequency of the hydrodynamic bearing device including the base 1, the fixed shaft 3, and the rotating member 19,
In addition, to improve this resonant frequency, the base 1 and the fixed shaft 3 are
It has been found that it is effective to increase the rigidity of the attachment part. Therefore, if the longitudinal elastic modulus of both the base 1 and the fixed shaft 3 is set to 18000 Kgf/mm 2 or more, the support rigidity of the attachment part between the base 1 and the fixed shaft 3 will be increased, and the hydrodynamic bearing Since the resonant frequency of the device is improved, the high speed rotation limit number of the rotating member 19 can be significantly increased. In addition, the longitudinal elastic modulus of at least one of the base 1 and the fixed shaft 3 is 18000.
If it is lower than Kgf/mm 2 , the supporting rigidity of the attachment part between the base 1 and the fixed shaft 3 will be insufficient, and if the longitudinal elastic modulus of the base 1 and the fixed shaft 3 is as high as possible, the base 1 It is preferable to improve the support rigidity of the attachment portion between the fixed shaft 3 and the fixed shaft 3.
なお、基台１と固定軸３とはほぼ等しい縦弾性
係数を有する材料をそれぞれ使用することが共振
周波数の向上に好ましい。 Note that it is preferable to use materials having substantially the same longitudinal elastic modulus for the base 1 and the fixed shaft 3 in order to improve the resonance frequency.
また、基台１の固定軸３への取付部分４の軸方
向長さを固定軸３の直径以上にすることが基台１
と固定軸３との取付部の支持剛性の向上に好まし
い。 In addition, the axial length of the attachment portion 4 of the base 1 to the fixed shaft 3 must be greater than or equal to the diameter of the fixed shaft 3.
This is preferable for improving the support rigidity of the attachment portion between the fixed shaft 3 and the fixed shaft 3.
さらに、基台１及び固定軸３の材料としてステ
ンレス鋼以外の他の材料を使用しても良い。 Furthermore, materials other than stainless steel may be used for the base 1 and the fixed shaft 3.
また、固定軸３を基台１へねじ、圧入等を利用
して取付けても良い。 Furthermore, the fixed shaft 3 may be attached to the base 1 using screws, press fitting, or the like.
さらに、ラジアル軸受面２７とラジアル受面１
１との少なくとも一方にスパイラル状、ヘリング
ボーン状等の動圧発生用みぞ１２を設けても良
い。 Furthermore, the radial bearing surface 27 and the radial bearing surface 1
A dynamic pressure generating groove 12 in a spiral shape, a herringbone shape, etc. may be provided on at least one of the grooves 1 and 1.
また、スラスト軸受面２９の半径方向中央部で
はなくスリーブ２１と嵌合部材２３との間に円筒
状孔５から回転部材１９の外部へ通ずる流通孔を
設け、そしてスラスト軸受面２９とスラスト受面
１３との両方を平面状としてスラスト軸受面２９
とスラスト受面１３との少なくとも一方にスパイ
ラル状、ヘリングボーン状等の動圧発生用みぞを
設けても良い。 Further, a communication hole communicating from the cylindrical hole 5 to the outside of the rotating member 19 is provided between the sleeve 21 and the fitting member 23 instead of at the radial center of the thrust bearing surface 29, and the thrust bearing surface 29 and the thrust bearing surface 13 are both planar and the thrust bearing surface 29
At least one of the thrust receiving surface 13 and the thrust receiving surface 13 may be provided with a groove for generating dynamic pressure in a spiral shape, a herringbone shape, or the like.
さらに、回転部材１９を軸方向に支持する手段
としてはスラスト軸受面２９とスラスト受面１３
とを備えたスラスト流体軸受の代りに、スラスト
磁気軸受を用いても良い。即ち、回転部材１９と
基台１、固定軸３及びカバー部材５３を備えた固
定部材との両方に吸引型又は反発型の磁石をそれ
ぞれ対向して取付けて磁気軸受としても良く、ま
た回転部材１９と固定部材とのいずれか一方に磁
石を取付けて他方を磁石に対向する強磁性体とし
て吸引型の磁気軸受としても良い。また、駆動用
モータのロータ４３とステータ６１との間に働く
吸引力をスラスト磁気軸受としても良い。この場
合スリーブ２１に嵌合部材２３を取付けないでス
リーブ２１の内周面を固定軸３が貫通しても良
い。 Further, as means for supporting the rotating member 19 in the axial direction, a thrust bearing surface 29 and a thrust bearing surface 13 are used.
A thrust magnetic bearing may be used instead of a thrust fluid bearing equipped with. That is, the rotating member 19 and the fixed member including the base 1, the fixed shaft 3, and the cover member 53 may be provided with attracting or repelling magnets facing each other to form a magnetic bearing. A magnet may be attached to one of the fixed member and the other may be made of a ferromagnetic material facing the magnet to form an attraction type magnetic bearing. Further, the attractive force acting between the rotor 43 and the stator 61 of the drive motor may be provided by a thrust magnetic bearing. In this case, the fixed shaft 3 may pass through the inner peripheral surface of the sleeve 21 without attaching the fitting member 23 to the sleeve 21.
この考案によると、基台１と固定軸３とはいず
れも縦弾性係数が18000Kgｆ／mm2以上なので基台
１と固定軸３との取付部の支持剛性が高くなり、
動圧形流体軸受装置の共振周波数が向上するので
回転部材１９の高速回転限界数が向上するという
効果を有する。
According to this invention, since both the base 1 and the fixed shaft 3 have a longitudinal elastic modulus of 18000 Kgf/mm 2 or more, the support rigidity of the attachment part between the base 1 and the fixed shaft 3 is increased.
Since the resonance frequency of the hydrodynamic bearing device is improved, there is an effect that the high speed rotation limit number of the rotating member 19 is improved.
第１図はこの考案の一実施例を示す動圧形流体
軸受装置の断面図である。
図中、１は基台、３は固定軸、５は円筒状孔、
１１はラジアル受面、１２は動圧発生用みぞ、１
９は回転部材、２７はスラスト軸受面である。
FIG. 1 is a sectional view of a hydrodynamic bearing device showing an embodiment of this invention. In the figure, 1 is a base, 3 is a fixed shaft, 5 is a cylindrical hole,
11 is a radial receiving surface, 12 is a groove for generating dynamic pressure, 1
9 is a rotating member, and 27 is a thrust bearing surface.
Claims (1)
軸に回転部材の円筒状孔を嵌合し、前記固定軸
の外周面に設けた円筒状のラジアル受面が回転
部材に設けたラジアル軸受面に対向し、該ラジ
アル軸受面とラジアル受面との少なくとも一方
に動圧発生用みぞを設け、前記回転部材を軸方
向に支持する手段を備えた動圧形流体軸受装置
において、前記基台と固定軸とはいずれも縦弾
性係数が18000Kgｆ／mm2以上であることを特徴
とする動圧形流体軸受装置。 (2) 基台と固定軸とがいずれもステンレス鋼から
なる実用新案登録請求の範囲第１項記載の動圧
形流体軸受装置。[Claims for Utility Model Registration] (1) One end of a fixed shaft is attached to the base, a cylindrical hole of a rotating member is fitted to the fixed shaft, and a cylindrical hole provided on the outer circumferential surface of the fixed shaft is fitted. a radial bearing surface facing a radial bearing surface provided on a rotating member, a dynamic pressure generating groove provided in at least one of the radial bearing surface and the radial bearing surface, and means for supporting the rotating member in the axial direction. 1. A hydrodynamic bearing device according to claim 1, wherein the base and the fixed shaft both have a longitudinal elastic modulus of 18000 Kgf/mm 2 or more. (2) The hydrodynamic bearing device according to claim 1, wherein both the base and the fixed shaft are made of stainless steel.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1987164639U JPH0416014Y2 (en) | 1987-10-29 | 1987-10-29 |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP1987164639U JPH0416014Y2 (en) | 1987-10-29 | 1987-10-29 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH0169909U JPH0169909U (en) | 1989-05-10 |
| JPH0416014Y2 true JPH0416014Y2 (en) | 1992-04-10 |
Family
ID=31450425
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP1987164639U Expired JPH0416014Y2 (en) | 1987-10-29 | 1987-10-29 |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0416014Y2 (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2013099815A (en) | 2011-11-08 | 2013-05-23 | Fanuc Ltd | Robot programming device |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6132812A (en) * | 1984-07-26 | 1986-02-15 | Toshiba Corp | Optical deflecting device of polygon mirror |
| JPS61269111A (en) * | 1985-05-24 | 1986-11-28 | Toshiba Corp | Device for supporting rotary body |
| JPS61269637A (en) * | 1986-05-14 | 1986-11-29 | Toshiba Corp | Motor for polarization |
-
1987
- 1987-10-29 JP JP1987164639U patent/JPH0416014Y2/ja not_active Expired
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6132812A (en) * | 1984-07-26 | 1986-02-15 | Toshiba Corp | Optical deflecting device of polygon mirror |
| JPS61269111A (en) * | 1985-05-24 | 1986-11-28 | Toshiba Corp | Device for supporting rotary body |
| JPS61269637A (en) * | 1986-05-14 | 1986-11-29 | Toshiba Corp | Motor for polarization |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH0169909U (en) | 1989-05-10 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| DE68922397D1 (en) | Structure of a rotating polygon mirror. | |
| EP1098096A1 (en) | Dynamic pressure bearing and spindle motor | |
| JPH0416014Y2 (en) | ||
| JPH06311698A (en) | Magnetically levitated gas dynamic-pressure bearing for axial gap-type motor | |
| JPH0814255A (en) | Composite bearing device | |
| JPS61294218A (en) | Fluid bearing device | |
| JP2000161357A (en) | Bearing device | |
| JPH0731094A (en) | Motor | |
| JPS631053Y2 (en) | ||
| JPS60208629A (en) | Light deflector device | |
| JP3092026B2 (en) | Dynamic pressure air bearing type optical deflector | |
| JPH03213715A (en) | Thrust bearing | |
| JP2002130256A (en) | Air dynamic bearing unit | |
| JPS62131736A (en) | Motor spindle | |
| JPH0293120A (en) | Thrust magnetic bearing device | |
| JPS6314218U (en) | ||
| JP3186395B2 (en) | motor | |
| JP2002276648A (en) | Spindle motor | |
| JPH03256547A (en) | Spindle motor | |
| KR100459876B1 (en) | Spindle system for HDD | |
| JP3858557B2 (en) | Optical deflector | |
| JP2000092773A (en) | Disk driving device | |
| JP3048005B2 (en) | Polygon mirror motor | |
| JPH0428201Y2 (en) | ||
| JP2864319B2 (en) | Spindle motor |