JPH05126151A - Bearing device - Google Patents
Bearing deviceInfo
- Publication number
- JPH05126151A JPH05126151A JP3315138A JP31513891A JPH05126151A JP H05126151 A JPH05126151 A JP H05126151A JP 3315138 A JP3315138 A JP 3315138A JP 31513891 A JP31513891 A JP 31513891A JP H05126151 A JPH05126151 A JP H05126151A
- Authority
- JP
- Japan
- Prior art keywords
- bearing
- displacement
- rotary shaft
- rotating shaft
- bearings
- 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
- 238000006073 displacement reaction Methods 0.000 claims abstract description 34
- 238000001514 detection method Methods 0.000 claims abstract description 3
- 238000005096 rolling process Methods 0.000 claims description 12
- 238000005452 bending Methods 0.000 abstract description 11
- 230000010355 oscillation Effects 0.000 abstract 2
- 230000010360 secondary oscillation Effects 0.000 abstract 1
- 230000002093 peripheral effect Effects 0.000 description 9
- 125000006850 spacer group Chemical group 0.000 description 4
- 230000006835 compression Effects 0.000 description 2
- 238000007906 compression Methods 0.000 description 2
- 230000005284 excitation Effects 0.000 description 2
- 210000001015 abdomen Anatomy 0.000 description 1
- 238000007796 conventional method Methods 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
- F16C27/00—Elastic or yielding bearings or bearing supports, for exclusively rotary movement
- F16C27/04—Ball or roller bearings, e.g. with resilient rolling bodies
- F16C27/045—Ball or roller bearings, e.g. with resilient rolling bodies with a fluid film, e.g. squeeze film damping
-
- 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
- F16C32/0402—Bearings not otherwise provided for using magnetic or electric supporting means combined with other supporting means, e.g. hybrid bearings with both magnetic and fluid supporting means
-
- 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
- F16C32/048—Active magnetic bearings for rotary movement with active support of two degrees of freedom, e.g. radial 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
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
- F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
- F16C19/16—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls
- F16C19/163—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls with angular contact
-
- 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
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/54—Systems consisting of a plurality of bearings with rolling friction
- F16C19/546—Systems with spaced apart rolling bearings including at least one angular contact bearing
- F16C19/547—Systems with spaced apart rolling bearings including at least one angular contact bearing with two angular contact rolling bearings
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Support Of The Bearing (AREA)
- Magnetic Bearings And Hydrostatic Bearings (AREA)
- Rolling Contact Bearings (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】この発明は、軸受装置、特に防振
軸受装置に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a bearing device, and more particularly to a vibration-proof bearing device.
【０００２】[0002]
【従来の技術】従来の技術の高速回転転がり軸受装置に
おいては、高速回転時の振動を抑制するために軸受ハウ
ジング・転がり軸受の外輪間に形成される油膜ダンパを
用いている。2. Description of the Related Art In a conventional high-speed rotary rolling bearing device, an oil film damper formed between a bearing housing and an outer ring of a rolling bearing is used in order to suppress vibration during high-speed rotation.
【０００３】[0003]
【発明が解決しようとする課題】上記の従来の技術のよ
る高速転がり回転軸受装置における油膜ダンパを用いた
振動抑制手段は、回転軸の１次振動（コニカルモード）
や２次振動（パラレルモード）を吸収することができる
が、軸受による２点支持において使用回転数範囲内に３
次の危険速度がある場合、２支点による曲げモードにな
る結果、殆ど機能しなくなる。The vibration suppressing means using the oil film damper in the high-speed rolling rotary bearing device according to the above-mentioned conventional technique is a primary vibration (conical mode) of the rotary shaft.
And secondary vibration (parallel mode) can be absorbed, but in the case of two-point support by bearings, it can be 3
When there is the following critical speed, the bending mode with two fulcrums results in almost no function.
【０００４】この発明は、高速回転軸における１次振動
や２次振動は勿論のこと、３次の危険速度における３次
振動（曲げモード）が生じる場合でも、それらの振動を
抑制する軸受装置を提供する。The present invention provides a bearing device which suppresses not only primary vibration and secondary vibration of a high-speed rotating shaft but also tertiary vibration (bending mode) at a critical speed of the third order. provide.
【０００５】[0005]
【課題を解決するための手段】この発明の軸受装置は、
回転軸を回転自在に軸線方向に互に間隔をあけた位置で
支承する油膜ダンパを備えた複数の転がり軸受、回転軸
を回転自在に各転がり軸受より軸線方向に間隔をあけた
位置で支承する磁気軸受、磁気軸受支承位置の回転軸の
ラジアル方向変位を検出する変位検出器、変位検出器の
検出信号に基づいて前記変位を相殺するような変位を回
転軸に与えるように磁気軸受に対し制御励磁電流を供給
する制御装置から構成されている。The bearing device of the present invention comprises:
Rotating shafts are rotatably supported at positions spaced apart from each other in the axial direction.A plurality of rolling bearings equipped with oil film dampers, and rotating shafts are rotatably supported at positions spaced apart from each rolling bearing in the axial direction. Magnetic bearing, displacement detector for detecting radial displacement of rotating shaft at magnetic bearing support position, control for magnetic bearing so as to give displacement to rotor shaft based on detection signal of displacement detector It is composed of a control device for supplying an exciting current.
【０００６】[0006]
【作用】ラジアル磁気軸受のソレノイドに制御装置から
制御励磁電流が供給され、両側が転がり軸受に支承され
た回転軸の中間部は周囲から吸引され、浮上状態とな
る。そして、回転軸は、駆動源により回転駆動される。
そして、回転中の回転軸に１次振動（コニカルモード）
や２次振動（パラレルモード）が生じると、それらは、
両側の転がり軸受に形成された油膜ダンパーにより吸収
される。A control exciting current is supplied from the control device to the solenoid of the radial magnetic bearing, and the intermediate portion of the rotary shaft, both sides of which are supported by the rolling bearing, is attracted from the surroundings and is in a floating state. Then, the rotating shaft is rotationally driven by the drive source.
Then, the primary vibration (conical mode) is applied to the rotating rotating shaft.
And secondary vibrations (parallel mode),
It is absorbed by the oil film dampers formed on the rolling bearings on both sides.
【０００７】更に、回転中における回転軸の中間部が回
転軸線からラジアル方向に変位すると、変位検出器は、
変位方向と変位量に応じた変位信号を制御装置に入力
し、制御装置においては、当該変位を相殺するような変
位を回転軸に与えるようにラジアル磁気軸受のソレノイ
ドに対し制御励磁電流が供給され、回転軸の中間部のラ
ジアル方向の変位は抑制される。Further, when the intermediate portion of the rotating shaft during rotation is displaced in the radial direction from the rotating shaft line, the displacement detector
A displacement signal corresponding to the displacement direction and the displacement amount is input to the control device, and the control device supplies a control excitation current to the solenoid of the radial magnetic bearing so as to give a displacement to the rotation shaft that cancels the displacement. The radial displacement of the intermediate portion of the rotary shaft is suppressed.
【０００８】従って、高速回転における３次振動（曲げ
モード）が生じても、既にその節部となっている転がり
軸受部の振動は既に上記のように油膜ダンパーにより吸
収され、三次振動の腹部となる転がり軸受の中間部にお
ける回転軸の変位、即ち回転軸の曲げモードの振動は、
磁気軸受により抑制される。Therefore, even if the third-order vibration (bending mode) occurs at high speed rotation, the vibration of the rolling bearing, which is already the node, is already absorbed by the oil film damper as described above, and the third-order vibration is generated. The displacement of the rotating shaft in the middle part of the rolling bearing, that is, the bending mode vibration of the rotating shaft,
Suppressed by magnetic bearings.
【０００９】[0009]
【実施例】この発明の実施例における軸受装置を図面に
従って説明する。なお以下の説明における左右方向は、
図１における方向である。図１において、軸受ハウジン
グ１には、図示しない駆動源に結合された回転軸２が両
側のアンギュラ玉軸受３，４（３点接触玉軸受、又は深
溝玉軸受でもよい）とその中間の一対のラジアル磁気軸
受５Ａ，５Ｂとにより回転自在に支承されている。DESCRIPTION OF THE PREFERRED EMBODIMENTS A bearing device according to an embodiment of the present invention will be described with reference to the drawings. In addition, the left-right direction in the following description,
This is the direction in FIG. In FIG. 1, a bearing housing 1 includes a rotary shaft 2 coupled to a drive source (not shown) on both sides of angular ball bearings 3 and 4 (which may be three-point contact ball bearings or deep groove ball bearings) and a pair of intermediate members. It is rotatably supported by radial magnetic bearings 5A and 5B.
【００１０】詳述すると、軸受ハウジング１の中空孔６
の左端には、アンギュラ玉軸受３の外輪31が内周面の段
部61と押え環７とにより挟まれて且つ外周面・両端面に
微小隙間をあけて嵌着され、同じく右端には、アンギュ
ラ玉軸受４の外輪41が内周面の段部62と圧縮コイルばね
８を介する押え環９とにより挟まれて外周面及び段部62
に対する端面に微小隙間をあけて嵌着されている。More specifically, the hollow hole 6 of the bearing housing 1
The outer ring 31 of the angular contact ball bearing 3 is sandwiched between the step portion 61 of the inner peripheral surface and the retaining ring 7 and is fitted to the left end of the outer peripheral surface and both end surfaces with a small gap. The outer ring 41 of the angular contact ball bearing 4 is sandwiched between the step portion 62 on the inner peripheral surface and the holding ring 9 via the compression coil spring 8, and the outer peripheral surface and the step portion 62 are provided.
Is fitted to the end face with a small gap.
【００１１】回転軸２には、左側のフランジ部26に当接
したアンギュラ玉軸受３の内輪32、筒状スペーサ10、及
びアンギュラ玉軸受４の内輪42が順次嵌着され、内輪42
の右側で回転軸２に螺合したねじ環11により座金12を介
して締着けられている。The inner ring 32 of the angular ball bearing 3, the cylindrical spacer 10, and the inner ring 42 of the angular ball bearing 4, which are in contact with the left flange portion 26, are fitted to the rotary shaft 2 in this order.
Is fastened via a washer 12 by a screw ring 11 screwed to the rotary shaft 2 on the right side of the.
【００１２】軸受ハウジング１の中空孔６の内周面に
は、アンギュラ玉軸受３の外輪31及びアンギュラ玉軸受
４の外輪41の外周面に対向して環状油溝63，64が形成さ
れ、軸受ハウジング１には、外部から環状油溝63，64に
開口した油供給孔13，14が穿設されている。On the inner peripheral surface of the hollow hole 6 of the bearing housing 1, annular oil grooves 63, 64 are formed so as to face the outer peripheral surfaces of the outer ring 31 of the angular ball bearing 3 and the outer ring 41 of the angular ball bearing 4, respectively. The housing 1 is provided with oil supply holes 13 and 14 which are opened to the annular oil grooves 63 and 64 from the outside.
【００１３】ラジアル磁気軸受５Ａ，５Ｂは、軸受ハウ
ジング１の中空孔６においてアンギュラ玉軸受３とアン
ギュラ玉軸受４の中間に軸線方向に並設されており、各
ラジアル磁気軸受は、軸受電磁石51が筒状スペーサ10に
おける環状磁性体52の外周面に対向して放射状（例えば
９０度間隔）に設けられて構成され、両ラジアル磁気軸
受５Ａ，５Ｂの中間には、ラジアル位置センサ20が設け
られ、ラジアル位置センサ20は、電磁石51と同様の電磁
石21が軸受電磁石51と同位相位置で筒状スペーサ10にお
ける環状磁性体22の外周面に対向して設けられて構成さ
れている。The radial magnetic bearings 5A and 5B are axially arranged side by side in the hollow hole 6 of the bearing housing 1 between the angular ball bearing 3 and the angular ball bearing 4, and each radial magnetic bearing has a bearing electromagnet 51. The cylindrical spacer 10 is arranged radially (for example, at intervals of 90 degrees) facing the outer peripheral surface of the annular magnetic body 52, and a radial position sensor 20 is provided between the radial magnetic bearings 5A and 5B. The radial position sensor 20 is configured such that an electromagnet 21 similar to the electromagnet 51 is provided facing the outer peripheral surface of the annular magnetic body 22 in the tubular spacer 10 at the same phase position as the bearing electromagnet 51.
【００１４】ラジアル位置センサ20は、環状磁性体22、
即ち回転軸２の中間部の回転軸線からのラジアル方向の
変位を各放射方向の電磁石21のソレノイドに流れる電流
のインダクタンスの変化として検出する変位信号を変位
信号処理部Ｐに入力するように接続され、変位信号処理
部Ｐは、更に制御装置Ｃに入力するように接続されてい
る。各放射方向の軸受電磁石51のソレノイドは、制御装
置Ｃから制御励磁電流が供給されるように接続されてい
る。The radial position sensor 20 includes an annular magnetic body 22,
That is, the displacement signal is connected to the displacement signal processing unit P so as to detect the displacement in the radial direction from the rotation axis of the intermediate portion of the rotary shaft 2 as a change in the inductance of the current flowing through the solenoid of the electromagnet 21 in each radial direction. , The displacement signal processing unit P is further connected so as to be input to the control device C. The solenoids of the bearing electromagnets 51 in each radial direction are connected so that a control excitation current is supplied from the control device C.
【００１５】上記の軸受装置の作用について説明する
と、先ず各放射方向の軸受電磁石51のソレノイドに制御
装置から制御励磁電流が供給され、環状磁性体52，52が
周囲から吸引される。そして、駆動源により回転駆動さ
れる回転軸２は、軸受装置の両側のアンギュラ玉軸受
３，４に支承されると共に、その中間部がラジアル磁気
軸受５Ａ，５Ｂで支承されて回転する。Explaining the operation of the above bearing device, first, a control exciting current is supplied from the control device to the solenoid of the bearing electromagnet 51 in each radial direction, and the annular magnetic bodies 52, 52 are attracted from the surroundings. The rotary shaft 2 that is rotationally driven by the drive source is supported by the angular ball bearings 3 and 4 on both sides of the bearing device, and the intermediate portions thereof are supported by the radial magnetic bearings 5A and 5B to rotate.
【００１６】そして、油供給孔13，14から環状油溝63，
64に圧油が供給され、アンギュラ玉軸受５Ａ，５Ｂの外
輪31，41の外周面の微小間隙に油膜ダンパが形成され
る。その結果、回転中の回転軸２のアンギュラ玉軸受
３，４における振動、即ち回転軸２の１次振動（コニカ
ルモード）や２次振動（パラレルモード）は吸収され
る。From the oil supply holes 13 and 14, the annular oil groove 63,
Pressure oil is supplied to 64, and an oil film damper is formed in a minute gap on the outer peripheral surfaces of the outer rings 31, 41 of the angular ball bearings 5A, 5B. As a result, the vibrations of the rotating angular contact ball bearings 3 and 4 of the rotating shaft 2, that is, the primary vibration (conical mode) and the secondary vibration (parallel mode) of the rotating shaft 2 are absorbed.
【００１７】更に、回転中における回転軸２の中間部、
即ち環状磁性体22が回転軸線からラジアル方向に変位す
ると、ラジアル位置センサ20がその変位を検出して、各
放射方向の電磁石21のソレノイドに流れる電流のインダ
クタンスの変化としての変位信号を変位信号処理部Ｐに
入力し、変位信号処理部Ｐは、変位の大きさと位相とを
制御装置Ｃに入力する。制御装置においては、当該変位
を相殺するような変位を回転軸２に与えるようにラジア
ル磁気軸受５Ａ，５Ｂの各軸受電磁石51のソレノイドに
対し制御励磁電流を供給され、回転軸２の中間部のラジ
アル方向の変位は抑制される。Further, an intermediate portion of the rotating shaft 2 during rotation,
That is, when the annular magnetic body 22 is displaced in the radial direction from the rotation axis, the radial position sensor 20 detects the displacement, and displacement signal processing is performed on the displacement signal as a change in the inductance of the current flowing through the solenoid of the electromagnet 21 in each radial direction. The displacement signal processing unit P inputs the displacement magnitude and phase to the control device C. In the control device, a control exciting current is supplied to the solenoids of the bearing electromagnets 51 of the radial magnetic bearings 5A and 5B so as to give a displacement that cancels the displacement to the rotating shaft 2, and a control exciting current is supplied to the intermediate portion of the rotating shaft 2. Displacement in the radial direction is suppressed.
【００１８】従って、高速回転における３次振動（曲げ
モード）が生じると、振動の腹部となるアンギュラ玉軸
受５Ａ，５Ｂの中間部における回転軸２の変位、即ち回
転軸２の曲げモードの振動は、上記のようにして抑制さ
れる。Therefore, when the third-order vibration (bending mode) occurs at high speed rotation, the displacement of the rotating shaft 2 at the intermediate portion of the angular ball bearings 5A, 5B, which is the antinode of the vibration, that is, the bending mode vibration of the rotating shaft 2 occurs. , Is suppressed as described above.
【００１９】上記の説明においては、アンギュラ玉軸受
は、２組を例示したが、３組以上の列設する形式におい
ても同様に考えられる。又、３次振動（曲げモード）を
抑制する磁気軸受は、アンギュラ玉軸受５Ａ，５Ｂの中
間に限らず、アンギュラ玉軸受５Ａ，５Ｂの外側におけ
る回転軸２の曲げモード振動の腹部該当位置にも設けら
れてもよい。In the above description, two sets of angular contact ball bearings are exemplified, but the same is conceivable in a form in which three or more sets are arranged in a row. Further, the magnetic bearing that suppresses the third-order vibration (bending mode) is not limited to the intermediate position between the angular ball bearings 5A and 5B, but also at the corresponding position of the abdomen of the bending mode vibration of the rotary shaft 2 outside the angular ball bearings 5A and 5B. It may be provided.
【００２０】[0020]
【発明の効果】この発明の軸受装置は回転軸の１次振動
（コニカルモード）や２次振動（パラレルモード）を吸
収することができるる上、軸受による２点支持において
使用回転数範囲内に３次の危険速度がある場合、２支点
による曲げモードとなる３次振動（曲げモード）が生じ
る場合でも、それらの振動を抑制することができる。The bearing device of the present invention can absorb the primary vibration (conical mode) and the secondary vibration (parallel mode) of the rotating shaft, and within the operating speed range in the case of two-point support by the bearing. When there is a third-order critical speed, even if a third-order vibration (bending mode) that is a bending mode due to a second fulcrum occurs, those vibrations can be suppressed.
【図１】この発明の実施例における軸受装置の断面図で
ある。FIG. 1 is a sectional view of a bearing device according to an embodiment of the present invention.
１ 軸受ハウジング ２ 回転軸 ３，４ アンギュラ玉軸受 31，41 外輪 32，42 内輪 ５Ａ，５Ｂ ラジアル磁気軸受 51 軸受電磁石 52 環状磁性体 ６ 中空孔 61，62 段部 63，64 環状油溝 ７ 押え環 ８ 圧縮コイルばね ９ 押え環 10 筒状スペーサ 11 ねじ環 12 座金 13，14 油供給孔 20 ラジアル位置センサ 21 電磁石 22 環状磁性体 Ｃ 制御装置 Ｐ 変位信号処理部 1 Bearing housing 2 Rotating shaft 3,4 Angular ball bearing 31,41 Outer ring 32,42 Inner ring 5A, 5B Radial magnetic bearing 51 Bearing electromagnet 52 Annular magnetic body 6 Hollow hole 61,62 Step 63,64 Annular oil groove 7 Presser ring 8 Compression coil spring 9 Presser ring 10 Cylindrical spacer 11 Screw ring 12 Washers 13, 14 Oil supply hole 20 Radial position sensor 21 Electromagnet 22 Annular magnetic body C Controller P Displacement signal processor
Claims (2)
をあけた位置で支承する複数の転がり軸受、回転軸を回
転自在に各転がり軸受より軸線方向に間隔をあけた位置
で支承する磁気軸受、磁気軸受支承位置の回転軸のラジ
アル方向変位を検出する変位検出器、変位検出器の検出
信号に基づいて前記変位を相殺するような変位を回転軸
に与えるように磁気軸受に対し制御励磁電流を供給する
制御装置から構成された軸受装置。1. A plurality of rolling bearings that rotatably support a rotating shaft at positions spaced apart from each other in the axial direction, and a rotating shaft that is rotatably supported at positions spaced apart from each rolling bearing in the axial direction. Magnetic bearing, displacement detector for detecting radial displacement of rotating shaft at magnetic bearing support position, control for magnetic bearing so as to give displacement to rotor shaft based on detection signal of displacement detector A bearing device including a control device that supplies an exciting current.
求項１に記載の軸受装置。2. The bearing device according to claim 1, wherein the rolling bearing includes an oil film damper.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP31513891A JP3267649B2 (en) | 1991-11-05 | 1991-11-05 | Bearing device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP31513891A JP3267649B2 (en) | 1991-11-05 | 1991-11-05 | Bearing device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH05126151A true JPH05126151A (en) | 1993-05-21 |
| JP3267649B2 JP3267649B2 (en) | 2002-03-18 |
Family
ID=18061869
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP31513891A Expired - Fee Related JP3267649B2 (en) | 1991-11-05 | 1991-11-05 | Bearing device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3267649B2 (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2016537564A (en) * | 2013-11-05 | 2016-12-01 | ターボネティクス ホールディングス, インコーポレイテッドTurbonetics Holdings, Inc. | Turbocharger double ball bearing system |
| CN110233536A (en) * | 2019-06-13 | 2019-09-13 | 清华大学 | The electromagnetic actuator and motor that high-speed rotating shaft is fastened |
| CN115051498A (en) * | 2022-07-11 | 2022-09-13 | 苏州晋胜技术有限公司 | Radial load balanced permanent magnet synchronous direct drive motor |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP3997351A1 (en) * | 2019-07-11 | 2022-05-18 | LORD Corporation | Rotatable shaft bearing with electromagnetically controlled support impedance |
-
1991
- 1991-11-05 JP JP31513891A patent/JP3267649B2/en not_active Expired - Fee Related
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2016537564A (en) * | 2013-11-05 | 2016-12-01 | ターボネティクス ホールディングス, インコーポレイテッドTurbonetics Holdings, Inc. | Turbocharger double ball bearing system |
| JP2019218952A (en) * | 2013-11-05 | 2019-12-26 | ターボネティクス ホールディングス, インコーポレイテッドTurbonetics Holdings, Inc. | Turbocharger double ball bearing system |
| CN110233536A (en) * | 2019-06-13 | 2019-09-13 | 清华大学 | The electromagnetic actuator and motor that high-speed rotating shaft is fastened |
| CN115051498A (en) * | 2022-07-11 | 2022-09-13 | 苏州晋胜技术有限公司 | Radial load balanced permanent magnet synchronous direct drive motor |
Also Published As
| Publication number | Publication date |
|---|---|
| JP3267649B2 (en) | 2002-03-18 |
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