JPH03255219A - Magnetic bearing device - Google Patents
Magnetic bearing deviceInfo
- Publication number
- JPH03255219A JPH03255219A JP2050394A JP5039490A JPH03255219A JP H03255219 A JPH03255219 A JP H03255219A JP 2050394 A JP2050394 A JP 2050394A JP 5039490 A JP5039490 A JP 5039490A JP H03255219 A JPH03255219 A JP H03255219A
- Authority
- JP
- Japan
- Prior art keywords
- magnetic bearing
- case
- radial direction
- bearing device
- axial
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 238000013016 damping Methods 0.000 claims abstract description 24
- 230000000694 effects Effects 0.000 claims abstract description 7
- 125000006850 spacer group Chemical group 0.000 abstract description 5
- 229910000831 Steel Inorganic materials 0.000 abstract description 4
- 239000010959 steel Substances 0.000 abstract description 4
- 238000000034 method Methods 0.000 description 5
- BGPVFRJUHWVFKM-UHFFFAOYSA-N N1=C2C=CC=CC2=[N+]([O-])C1(CC1)CCC21N=C1C=CC=CC1=[N+]2[O-] Chemical compound N1=C2C=CC=CC2=[N+]([O-])C1(CC1)CCC21N=C1C=CC=CC1=[N+]2[O-] BGPVFRJUHWVFKM-UHFFFAOYSA-N 0.000 description 3
- 239000002783 friction material Substances 0.000 description 3
- 238000004519 manufacturing process Methods 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
- 239000003190 viscoelastic substance Substances 0.000 description 1
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
- F16C32/00—Bearings not otherwise provided for
- F16C32/04—Bearings not otherwise provided for using magnetic or electric supporting means
- F16C32/0406—Magnetic bearings
- F16C32/044—Active magnetic bearings
- F16C32/0474—Active magnetic bearings for rotary movement
- F16C32/0476—Active magnetic bearings for rotary movement with active support of one degree of freedom, e.g. axial magnetic bearings
-
- 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
- F16C32/00—Bearings not otherwise provided for
- F16C32/04—Bearings not otherwise provided for using magnetic or electric supporting means
- F16C32/0406—Magnetic bearings
- F16C32/0408—Passive magnetic bearings
- F16C32/041—Passive magnetic bearings with permanent magnets on one part attracting the other part
- F16C32/0417—Passive magnetic bearings with permanent magnets on one part attracting the other part for axial load mainly
-
- 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
- F16C32/00—Bearings not otherwise provided for
- F16C32/04—Bearings not otherwise provided for using magnetic or electric supporting means
- F16C32/0406—Magnetic bearings
- F16C32/0408—Passive magnetic bearings
- F16C32/0423—Passive magnetic bearings with permanent magnets on both parts repelling each other
- F16C32/0425—Passive magnetic bearings with permanent magnets on both parts repelling each other for radial load mainly
-
- 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
- F16C2360/00—Engines or pumps
- F16C2360/44—Centrifugal pumps
- F16C2360/45—Turbo-molecular pumps
Abstract
Description
【発明の詳細な説明】
[産業上の利用分野]
この発明は、磁気軸受装置に関し、特に、ラジアル方向
に対しては永久磁石のような受動型の磁気軸受を用い、
スラスト方向に対しては制御式の能動型の磁気軸受を用
いて、1軸制御のみを行なうような磁気軸受装置に関す
る。[Detailed Description of the Invention] [Industrial Application Field] The present invention relates to a magnetic bearing device, and in particular, in the radial direction, a passive magnetic bearing such as a permanent magnet is used,
The present invention relates to a magnetic bearing device that performs only one-axis control using a controlled active magnetic bearing in the thrust direction.
[従来の技術]
最近では、製造コストを低減するために、外乱の少ない
用途への磁気軸受装置は、5軸制御よりも制御軸数の少
ない3軸制御、1軸制御が用いられようとしている。1
軸制御の場合、ラジアル方向には受動的な軸受が用いら
れ、軸方向のみが制御される。このような1軸制御型の
磁気軸受装置は、制御回路が最も簡単となり、実用化の
ための種々のくふうがなされている。ところが、1軸制
御型の磁気軸受装置は、残りの非制御の4軸の回りの減
衰がほとんど期待できないため、何らかの減衰を与えな
ければ、回転上昇あるいは下降時の固有振動通過時に大
きな振動を生じる。[Prior Art] Recently, in order to reduce manufacturing costs, three-axis control and one-axis control, which have fewer control axes than five-axis control, are being used in magnetic bearing devices for applications with less disturbance. . 1
In the case of axial control, passive bearings are used in the radial direction and only the axial direction is controlled. Such a single-axis control type magnetic bearing device has the simplest control circuit, and various improvements have been made to put it into practical use. However, in a single-axis controlled magnetic bearing device, almost no damping can be expected around the remaining four uncontrolled axes, so unless some kind of damping is provided, large vibrations will occur when the bearing passes through the natural vibration when the rotation is rising or falling. .
このような、対策として、特公昭59−7731号公報
および特公昭62−37246号公報には、電気的なダ
ンピング方法を用いて減衰を与える技術が開示されてお
り、その他に機械式ダンパを用いた方法もある。As a countermeasure to this problem, Japanese Patent Publication No. 59-7731 and Japanese Patent Publication No. 62-37246 disclose a technique for applying damping using an electrical damping method. There is also a method.
[発明が解決しようとする課題]
しかしながら、上述の電気的なダンピング方法は固有振
動数と回転速度が一致していないときにのみ有効な減衰
を示すが、これらが一致したとき、つまり、固有振動通
過時は減衰力を生じないため、実用的でない。また、機
械的ダンパによる方法の場合には、独立した反発型のラ
ジアル磁気軸受を2個用いて、一方の反発型のラジアル
磁気軸受を弾性支持して、減衰機を追加する必要があり
、構造が複雑になってしまうという欠点があった。[Problems to be Solved by the Invention] However, the above-mentioned electrical damping method exhibits effective damping only when the natural frequency and rotation speed do not match, but when they match, that is, the natural vibration It is not practical because it does not produce any damping force when passing. In addition, in the case of a method using a mechanical damper, it is necessary to use two independent repulsion type radial magnetic bearings to elastically support one of the repulsion type radial magnetic bearings, and add a damper. The disadvantage is that it becomes complicated.
それゆえに、この発明の主たる目的は、新たにダンパを
設けてラジアル方向の振動に対して減衰効果を高めた磁
気軸受装置を提供することである。Therefore, the main object of the present invention is to provide a magnetic bearing device that is newly provided with a damper to enhance the damping effect against vibrations in the radial direction.
[課題を解決するための手段]
第1請求項に係る発明は、永久磁石の反発力を利用した
ラジアル磁気軸受と、軸方向磁気力を制御する制御式磁
気軸受によって回転軸を軸支し、軸方向吸引力によって
生じるラジアル剛性を利用した1軸制御型磁気軸受装置
であて、制御式磁気軸受の固定部を軸方向に剛に支持す
るための支持部材と、制御式磁気軸受の固定部のラジア
ル方向を軟に支持するための粘弾性減衰部材と、固定部
材とケースとの間に挿入される弾性体からなる摩擦ダン
パとを備えて構成したものである。[Means for Solving the Problem] The invention according to the first claim supports a rotating shaft by a radial magnetic bearing that utilizes the repulsive force of a permanent magnet and a control type magnetic bearing that controls an axial magnetic force, This is a single-axis controlled magnetic bearing device that utilizes radial rigidity generated by axial attraction force, and includes a support member for rigidly supporting the fixed part of the controlled magnetic bearing in the axial direction, and a supporting member for rigidly supporting the fixed part of the controlled magnetic bearing. It is configured to include a viscoelastic damping member for soft support in the radial direction, and a friction damper made of an elastic body inserted between the fixed member and the case.
[作用コ
この発明に係る磁気軸受装置は支持部材によって制御式
磁気軸受の固定部を軸方向に剛に支持するとともに粘弾
性減衰部材によってラジアル方向を軟に支持し、さらに
固定部とケースとの間に摩擦ダンパを挿入したことによ
って、ラジアル方向の振動に対して減衰効果を高めるこ
とができる。[Operation] The magnetic bearing device according to the present invention rigidly supports the fixed part of the control type magnetic bearing in the axial direction by the support member, supports it softly in the radial direction by the viscoelastic damping member, and further supports the fixed part of the control type magnetic bearing in the radial direction. By inserting a friction damper between them, it is possible to enhance the damping effect against vibrations in the radial direction.
[発明の実施例コ
第1図はこの発明の一実施例の縦断面図であり、第2図
は第1図に示す線■−■に添う横断面図であり、第3図
は第1図に示す線■−■に添う横断面図である。[Embodiment of the invention] FIG. 1 is a longitudinal cross-sectional view of one embodiment of the invention, FIG. 2 is a cross-sectional view taken along the line ■-■ shown in FIG. 1, and FIG. FIG. 2 is a cross-sectional view taken along the line ■-■ shown in the figure.
第1図ないし第3図を参照して、回転軸1はケース2内
で回転するものであって、その回転軸1の一端にはロー
タ3が取り付けられている。ロータ3の内面には永久磁
石4が設けられ、この永久磁石4に対向するケース2の
外面には永久磁石5が設けられる。これらの永久磁石4
と5とによって反発型磁気軸受6が構成される。なお、
回転軸1の一端に対向するケース2の内面には上部非常
用ベアリング7が取り付けられている。ケース2のほぼ
中央部には、回転軸1を回転させるためのモータステー
タ8が設けられる。Referring to FIGS. 1 to 3, a rotating shaft 1 rotates within a case 2, and a rotor 3 is attached to one end of the rotating shaft 1. As shown in FIGS. A permanent magnet 4 is provided on the inner surface of the rotor 3, and a permanent magnet 5 is provided on the outer surface of the case 2 facing the permanent magnet 4. These permanent magnets 4
and 5 constitute a repulsion type magnetic bearing 6. In addition,
An upper emergency bearing 7 is attached to the inner surface of the case 2 facing one end of the rotating shaft 1. A motor stator 8 for rotating the rotating shaft 1 is provided approximately in the center of the case 2 .
モータステータ8の下部にはスラスト方向吸引用永久磁
石9が取り付けられた永久磁石ホルダ10が設けられて
いる。永久磁石ホルダ10に対向するようにスラスト板
11が回転軸1に設けられ、このスラスト板11の上部
には、スラスト方向吸引用永久磁石9に対向するように
永久磁石12が設けられている。スラスト板11の下部
には電磁石13が設けられ、この電磁石13はスペーサ
14を介して前述の永久磁石ホルダlOに取り付けられ
ている。電磁石13は永久磁石9と12との間に生じる
軸方向への吸引力につりあうように、図示しない制御回
路によって制御される。A permanent magnet holder 10 to which a permanent magnet 9 for thrust direction attraction is attached is provided at the lower part of the motor stator 8 . A thrust plate 11 is provided on the rotating shaft 1 so as to face the permanent magnet holder 10, and a permanent magnet 12 is provided on the upper part of the thrust plate 11 so as to face the permanent magnet 9 for attraction in the thrust direction. An electromagnet 13 is provided at the bottom of the thrust plate 11, and this electromagnet 13 is attached to the above-mentioned permanent magnet holder IO via a spacer 14. The electromagnet 13 is controlled by a control circuit (not shown) so as to balance the axial attraction force generated between the permanent magnets 9 and 12.
電磁石13の回転軸1に向く内面には下部非常用ベアリ
ング15が設けられ、回転軸1の他端にはアキシャルセ
ンサターゲット16が設けられる。A lower emergency bearing 15 is provided on the inner surface of the electromagnet 13 facing the rotating shaft 1, and an axial sensor target 16 is provided at the other end of the rotating shaft 1.
アキシャルセンサターゲット16に対向するように、軸
方向の位置を検出するためのアキシャル方向位置センサ
17がセンサ取付部材18によって電磁石13の下面に
固定される。永久磁石ホルダ10と電磁石13とスペー
サ14とアキシャル方向位置センサ17とからなるステ
ータユニットは数本の鋼線19によってケース2に取付
けられる。An axial position sensor 17 for detecting an axial position is fixed to the lower surface of the electromagnet 13 by a sensor mounting member 18 so as to face the axial sensor target 16 . A stator unit consisting of a permanent magnet holder 10, an electromagnet 13, a spacer 14, and an axial position sensor 17 is attached to the case 2 by several steel wires 19.
その結果、ステータユニットは鋼線19によって軸方向
に剛く、ラジアル方向に柔らかく支持されることになる
。As a result, the stator unit is supported by the steel wires 19 to be rigid in the axial direction and soft in the radial direction.
ステータユニットとケース2との間の数箇所には第3図
に示すように軸方向にそって溝が形成されていて、そこ
にゴムなどの粘弾性減衰部材20が挿入されていて、ラ
ジアル方向の振動に対して減衰が与えられるとともに、
ステータユニットの回り止めの役割を果たしている。As shown in FIG. 3, grooves are formed along the axial direction at several locations between the stator unit and the case 2, into which viscoelastic damping members 20 such as rubber are inserted. Damping is provided to the vibration of
It plays the role of preventing the stator unit from rotating.
ところで、ターボ分子ポンプのような大きな慣性モーメ
ントを持つロータ3を高速回転させる場合、このジャイ
ロモーメントによって固有振動数が回転速度とともに変
化し、前回りと後回りの固有振動数が生じる。後回りの
固有振動数に対しては、前記ゴムなどの粘弾性体からな
る減衰部材20による減衰が可能である。しかし、この
減衰部材20では前回り固有振動数のような高い周波数
に対しての減衰性能が小さい。By the way, when the rotor 3 having a large moment of inertia, such as a turbo molecular pump, is rotated at high speed, the natural frequency changes with the rotational speed due to the gyroscopic moment, and forward and rearward natural frequencies are generated. The rear natural frequency can be damped by the damping member 20 made of a viscoelastic material such as the rubber. However, this damping member 20 has low damping performance for high frequencies such as the front rotation natural frequency.
そこで、この発明の一実施例では、第2図に示すような
摩擦ダンパ21がステータユニット8とケース2との間
に挿入される。第2図に示した摩擦ダンパ21は薄いば
ね用板材を数枚重ねてステータユニットとケース2との
間に挿入されている。Therefore, in one embodiment of the present invention, a friction damper 21 as shown in FIG. 2 is inserted between the stator unit 8 and the case 2. The friction damper 21 shown in FIG. 2 is inserted between the stator unit and the case 2 by stacking several thin spring plates.
これにより、ステータユニットはラジアル方向に押し付
けられている。このように摩擦ダンパ21を設けること
によって、ステータユニットの振動によりステータユニ
ットおよび板ばね間あるいは板ばね間に摩擦力が生じ、
この摩擦力により振動エネルギーが吸収され、ステータ
ユニットの振動を押さえることができる。Thereby, the stator unit is pressed in the radial direction. By providing the friction damper 21 in this way, frictional force is generated between the stator unit and the leaf spring or between the leaf springs due to the vibration of the stator unit.
Vibration energy is absorbed by this frictional force, and vibration of the stator unit can be suppressed.
第4図はこの発明の他の実施例を示す要部断面図である
。この第4図に示した例は、ケース2の底面に板ばね2
2を配置し、この板ばね22とステータユニットの間に
摩擦材23を挿入したものであり、摩擦材23と板ばね
22は軸方向に押し付けられている。ステータユニット
のラジアル方向の振動はステータユニットと摩擦材23
の摩擦力により減衰される。FIG. 4 is a sectional view of a main part showing another embodiment of the present invention. In the example shown in FIG. 4, a leaf spring 2 is attached to the bottom of the case 2.
2 is arranged, and a friction material 23 is inserted between the leaf spring 22 and the stator unit, and the friction material 23 and the leaf spring 22 are pressed in the axial direction. The vibration in the radial direction of the stator unit is caused by the vibration between the stator unit and the friction material 23.
damped by the frictional force of
[発明の効果コ
以上のように、この発明によれば、ステータユニットか
らなる固定部を軸方向に剛に支持するとともに、ラジア
ル方向に軟に支持し、固定部とケースとの間に粘弾性体
からなる摩擦ダンパを挿入するようにしたので、ラジア
ル方向の振動に対して減衰効果を高めることができる。[Effects of the Invention] As described above, according to the present invention, the fixed part consisting of the stator unit is supported rigidly in the axial direction and supported softly in the radial direction, and there is a viscoelastic bond between the fixed part and the case. Since a friction damper made of a body is inserted, it is possible to enhance the damping effect against vibrations in the radial direction.
第1図はこの発明の一実施例の縦断面図である。
第2図は第1図に示す線■−Hに沿う横断面図である。
第3図は第1図に示す線■−■に沿う横断面図である。
第4図はこの発明の他の実施例の要部を示す縦断面図で
ある。
図において、1は回転軸、2はケース、3はロータ、4
. 5. 9. 12は永久磁石、6は反発型磁気軸受
、7は上部非常用ベアリング、8はモータステータ、1
0は永久磁石ホルダ、11はスラスト板、13は電磁石
、14はスペーサ、15は下部非常用ベアリング、16
はアキシャルセンサターゲット、17はアキシャル方向
位置センサ、18はセンサ取付部材、19は鋼線、20
は粘弾性減衰部材、21.23は摩擦ダンパ、22は板
ばねを示す。FIG. 1 is a longitudinal sectional view of an embodiment of the present invention. FIG. 2 is a cross-sectional view taken along line -H shown in FIG. FIG. 3 is a cross-sectional view taken along the line ■--■ shown in FIG. FIG. 4 is a longitudinal sectional view showing the main parts of another embodiment of the invention. In the figure, 1 is the rotating shaft, 2 is the case, 3 is the rotor, and 4
.. 5. 9. 12 is a permanent magnet, 6 is a repulsive magnetic bearing, 7 is an upper emergency bearing, 8 is a motor stator, 1
0 is a permanent magnet holder, 11 is a thrust plate, 13 is an electromagnet, 14 is a spacer, 15 is a lower emergency bearing, 16
is an axial sensor target, 17 is an axial position sensor, 18 is a sensor mounting member, 19 is a steel wire, 20
is a viscoelastic damping member, 21 and 23 are friction dampers, and 22 is a leaf spring.
Claims (3)
、軸方向磁気力を制御する制御式磁気軸受によって回転
軸を軸支し、軸方向吸引力によって生じるラジアル剛性
を利用した1軸制御型磁気軸受装置において、 前記制御式磁気軸受の固定部を軸方向に剛に支持するた
めの支持部材と、 前記制御式磁気軸受の固定部のラジアル方向を軟に支持
するための粘弾性減衰部材と、 前記固定部とケースとの間に挿入される弾性体からなる
摩擦ダンパとを備え、 ラジアル方向の振動に対して減衰効果を高めたことを特
徴とする、磁気軸受装置。(1) A single-axis control type that uses the radial rigidity generated by the axial attractive force to support the rotating shaft with a radial magnetic bearing that uses the repulsive force of a permanent magnet and a control type magnetic bearing that controls the axial magnetic force. In the magnetic bearing device, a support member for rigidly supporting the fixed portion of the control type magnetic bearing in the axial direction; and a viscoelastic damping member for supporting the fixed portion of the control type magnetic bearing soft in the radial direction. A magnetic bearing device comprising: a friction damper made of an elastic body inserted between the fixing portion and the case, the magnetic bearing device having an enhanced damping effect against vibrations in the radial direction.
複数の箇所に軸方向に挿入される、請求項第1項記載の
磁気軸受装置。(2) The magnetic bearing device according to claim 1, wherein the friction damper is inserted in the axial direction at a plurality of locations between the fixed portion and the case.
スの底面との間に挿入される、請求項第1項記載の磁気
軸受装置。(3) The magnetic bearing device according to claim 1, wherein the friction damper is inserted between an end surface of the fixed portion and a bottom surface of the case.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2050394A JPH0730793B2 (en) | 1990-02-28 | 1990-02-28 | Magnetic bearing device |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2050394A JPH0730793B2 (en) | 1990-02-28 | 1990-02-28 | Magnetic bearing device |
Publications (2)
Publication Number | Publication Date |
---|---|
JPH03255219A true JPH03255219A (en) | 1991-11-14 |
JPH0730793B2 JPH0730793B2 (en) | 1995-04-10 |
Family
ID=12857658
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP2050394A Expired - Fee Related JPH0730793B2 (en) | 1990-02-28 | 1990-02-28 | Magnetic bearing device |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPH0730793B2 (en) |
Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS50102750A (en) * | 1974-01-24 | 1975-08-14 |
-
1990
- 1990-02-28 JP JP2050394A patent/JPH0730793B2/en not_active Expired - Fee Related
Patent Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS50102750A (en) * | 1974-01-24 | 1975-08-14 |
Also Published As
Publication number | Publication date |
---|---|
JPH0730793B2 (en) | 1995-04-10 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US6448679B1 (en) | Passive magnetic support and damping system | |
JP3046533B2 (en) | Bearing unit | |
US5561335A (en) | Integrated passive magnetic bearing system and spindle permanent magnet for use in a spindle motor | |
JPS5993995A (en) | Pump | |
WO2003073586A1 (en) | Three axis magnetic bearing having permanent magnets | |
US6603230B1 (en) | Active magnetic bearing assembly using permanent magnet biased homopolar and reluctance centering effects | |
JP4280320B2 (en) | Vibration damping device for rotor supported by magnetic bearing mechanism | |
JP3114085B2 (en) | Magnetic bearing device with radial position correcting electromagnet | |
JP4528974B2 (en) | Vibration suppression device | |
JPH03255219A (en) | Magnetic bearing device | |
US6118200A (en) | Magnetic bearing | |
JPH0645698Y2 (en) | 1-axis control type magnetic bearing device | |
JPS6220407B2 (en) | ||
JPH0730792B2 (en) | Magnetic bearing device | |
JPH0629535Y2 (en) | Magnetic bearing device | |
JPH0833269A (en) | Turbo molecular drag pump | |
Nenninger et al. | Magnetic circuit design of a bearingless single-phase slice motor | |
KR100267696B1 (en) | A motor for disk driving | |
JPH03255220A (en) | Magnetic bearing device | |
JPH04171316A (en) | Magnetic bearing device | |
JP3454540B2 (en) | Magnetic bearing device | |
JPH0614087Y2 (en) | Magnetic bearing device | |
JPH04339194A (en) | Damping mechanism | |
JPH0749805B2 (en) | Magnetic bearing device | |
JP2024055181A (en) | Propulsion |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
R250 | Receipt of annual fees |
Free format text: JAPANESE INTERMEDIATE CODE: R250 |
|
R250 | Receipt of annual fees |
Free format text: JAPANESE INTERMEDIATE CODE: R250 |
|
R250 | Receipt of annual fees |
Free format text: JAPANESE INTERMEDIATE CODE: R250 |
|
R250 | Receipt of annual fees |
Free format text: JAPANESE INTERMEDIATE CODE: R250 |
|
FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20090410 Year of fee payment: 14 |
|
LAPS | Cancellation because of no payment of annual fees |