JP2002199655A - High speed motor - Google Patents
High speed motorInfo
- Publication number
- JP2002199655A JP2002199655A JP2000399537A JP2000399537A JP2002199655A JP 2002199655 A JP2002199655 A JP 2002199655A JP 2000399537 A JP2000399537 A JP 2000399537A JP 2000399537 A JP2000399537 A JP 2000399537A JP 2002199655 A JP2002199655 A JP 2002199655A
- Authority
- JP
- Japan
- Prior art keywords
- rotor
- magnetic bearing
- rotor shaft
- stator
- magnetic
- 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
- 238000006073 displacement reaction Methods 0.000 claims abstract description 46
- 238000004904 shortening Methods 0.000 abstract description 3
- 238000005452 bending Methods 0.000 description 9
- 230000002093 peripheral effect Effects 0.000 description 9
- XEEYBQQBJWHFJM-UHFFFAOYSA-N Iron Chemical compound [Fe] XEEYBQQBJWHFJM-UHFFFAOYSA-N 0.000 description 6
- 230000000694 effects Effects 0.000 description 4
- 238000010586 diagram Methods 0.000 description 3
- 238000000034 method Methods 0.000 description 3
- 229910000831 Steel Inorganic materials 0.000 description 2
- 229910052742 iron Inorganic materials 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 239000010959 steel Substances 0.000 description 2
- 238000004804 winding Methods 0.000 description 2
- 102100032566 Carbonic anhydrase-related protein 10 Human genes 0.000 description 1
- 101000867836 Homo sapiens Carbonic anhydrase-related protein 10 Proteins 0.000 description 1
- 229910000576 Laminated steel Inorganic materials 0.000 description 1
- 101001094026 Synechocystis sp. (strain PCC 6803 / Kazusa) Phasin PhaP Proteins 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 238000000926 separation 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
- 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
- F16C32/0444—Details of devices to control the actuation of the electromagnets
- F16C32/0446—Determination of the actual position of the moving member, e.g. details of sensors
-
- 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
- F16C2380/00—Electrical apparatus
- F16C2380/26—Dynamo-electric machines or combinations therewith, e.g. electro-motors and generators
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Electromagnetism (AREA)
- Magnetic Bearings And Hydrostatic Bearings (AREA)
- Motor Or Generator Frames (AREA)
- Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、ロータ軸長を短縮
化できる高速電動機に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a high-speed motor capable of shortening a rotor shaft length.
【０００２】[0002]
【従来の技術】ターボ圧縮機は、レシプロ圧縮機やスク
リュウ圧縮機に比較して大容量化、小型化に適し、かつ
オイルフリー化が容易である。そのためターボ圧縮機
は、工場の空気源、空気分離の原料空気やプロセス関係
の空気源等の汎用圧縮機として多用されている。2. Description of the Related Art A turbo compressor is more suitable for increasing the capacity and miniaturization than a reciprocating compressor or a screw compressor, and is easily oil-free. For this reason, turbo compressors are frequently used as general-purpose compressors for air sources in factories, raw air for air separation, and air sources for processes.
【０００３】図４は、上述するターボ圧縮機等を直結駆
動する従来の高速電動機の模式図である。この図におい
て高速電動機１には、ケーシング３の内周面４に、非回
転の固定子５が取付けられている。この固定子５は、固
定子鉄心７と図示しない固定子巻線からなり、高速電動
機のステータ部６を形成する。固定子鉄心７は、鉄損を
軽減するため複数枚の薄板鋼板を軸方向に積層させてい
る。FIG. 4 is a schematic view of a conventional high-speed motor for directly driving the above-described turbo compressor or the like. In this figure, a non-rotating stator 5 is attached to an inner peripheral surface 4 of a casing 3 of the high-speed motor 1. The stator 5 includes a stator core 7 and a stator winding (not shown), and forms a stator portion 6 of a high-speed motor. The stator core 7 has a plurality of thin steel plates laminated in the axial direction to reduce iron loss.
【０００４】一方、ステータ部６の内周面と所定の間隙
δを保持して回転子１０が配置されている。回転子１０
は中央部近傍にロータ部１１を形成する積層鉄心（ロー
タコア）１２と、ロータ軸１４からなる。ロータ軸１４
の両端には例えば図示しない１段インペラと２段インペ
ラが取付けられる。On the other hand, a rotor 10 is arranged while maintaining a predetermined gap δ from the inner peripheral surface of the stator portion 6. Rotor 10
Is composed of a laminated iron core (rotor core) 12 forming a rotor portion 11 near the center and a rotor shaft 14. Rotor shaft 14
For example, a one-stage impeller and a two-stage impeller (not shown) are attached to both ends.
【０００５】上述した回転子１０のロータ部１１と固定
子５のステータ部６とにより高速回転（例えば、１０万
ｍｉｎ-1以上）する高速電動機を形成している。A high-speed motor that rotates at high speed (for example, 100,000 min -1 or more) is formed by the rotor portion 11 of the rotor 10 and the stator portion 6 of the stator 5 described above.
【０００６】また、ロータ軸１４のロータ部１１を挟ん
だ状態でロータ部１１の外径より小径の軸部１５が設け
られている。更に夫々の軸部１５と所定の間隙Ｃ１を有
してケーシング３の内周面４に磁気軸受１６が配置され
ている。磁気軸受１６は、ロータ軸１４に発生する半径
方向の変位を制御し、高速回転可能にロータ軸１４を無
接触で支持する。更に、夫々の磁気軸受１６のロータ部
１１と反対側には、夫々の軸部１５と所定の間隙Ｃ２を
有して複数の変位センサ１７が、ケーシング３の内周面
４に配置されている。この変位センサ１７は、ロータ軸
１４の変位を検出する。なお、磁気軸受１６と変位セン
サ１７で高速電動機の磁気軸受ユニットが形成されてい
る。A shaft portion 15 having a diameter smaller than the outer diameter of the rotor portion 11 is provided with the rotor portion 11 of the rotor shaft 14 sandwiched therebetween. Further, a magnetic bearing 16 is arranged on the inner peripheral surface 4 of the casing 3 with a predetermined gap C1 from each of the shaft portions 15. The magnetic bearing 16 controls the displacement of the rotor shaft 14 in the radial direction, and supports the rotor shaft 14 in a non-contact manner so that the rotor shaft 14 can rotate at a high speed. Further, a plurality of displacement sensors 17 are arranged on the inner peripheral surface 4 of the casing 3 on the opposite side of each magnetic bearing 16 from the rotor section 11 with a predetermined gap C2 from each shaft section 15. . The displacement sensor 17 detects a displacement of the rotor shaft 14. The magnetic bearing 16 and the displacement sensor 17 form a magnetic bearing unit of a high-speed motor.
【０００７】[0007]
【発明が解決しようとする課題】図４において上述した
ようにロータ軸１４の小径の軸部１５の両端近傍には、
磁気軸受１６と変位センサ１７から構成される磁気軸受
ユニットが配置されている。しかし、このように変位セ
ンサが、磁気軸受の外側延長部に配置されているので、
その分ロータ軸の全長が長くなり、危険速度が低下す
る。また場合によっては曲げ一次危険速度速度を超えた
定格回転数となるため、磁気軸受の制御が複雑となると
いう問題点があった。このため、ロータ軸バランスや磁
気軸受の調整が困難で、またコストアップとなるという
問題点があった。更に、ロータ軸長が長いと、ロータ軸
の剛性が低下し回転軸に振れが生じて弾性モードとな
り、これにより回転軸の安定性が悪くなり回転数が低下
するという問題点があった。As described above with reference to FIG. 4, near both ends of the small-diameter shaft portion 15 of the rotor shaft 14,
A magnetic bearing unit including a magnetic bearing 16 and a displacement sensor 17 is provided. However, since the displacement sensor is thus arranged on the outer extension of the magnetic bearing,
Accordingly, the overall length of the rotor shaft becomes longer, and the critical speed decreases. Further, in some cases, the rated rotation speed exceeds the critical bending speed, which causes a problem that control of the magnetic bearing is complicated. Therefore, there is a problem that it is difficult to adjust the rotor shaft balance and the magnetic bearing, and the cost is increased. Further, when the length of the rotor shaft is long, the rigidity of the rotor shaft is reduced, and the rotating shaft oscillates to be in an elastic mode, whereby the stability of the rotating shaft is deteriorated and the number of revolutions is reduced.
【０００８】次に、前述したロータ軸の長さの影響につ
いて、図５に示す３質点ロータモデルを使って簡単に説
明する。図５において、均一な軸の等分の位置に３個の
質量ｍを取付け、両端部の質量ｍをばね定数ｋの軸受で
支持している。Next, the influence of the length of the rotor shaft described above will be briefly described using a three-mass rotor model shown in FIG. In FIG. 5, three masses m are mounted at equal positions on a uniform shaft, and the masses m at both ends are supported by bearings having a spring constant k.
【０００９】縦弾性係数をＥ、断面二次モーメントを
Ｉ、３質量ｍ間の全長をＬとすると、この場合の曲げ一
次固有値ωは、（１）式で表される。 ω＝（７２・Ｅ・Ｉ／ｍ・Ｌ3 ）0.5 ・・・（１） 次に、３質量ｍ間の全長をＬより短いＬ´とした場合を
考えてみると、この時の質量をｍ´とすると、ｍ´＝ｍ
・（Ｌ´／Ｌ）となるので、この時の曲げ一次固有値ω
´は、（２）式となる。 ω´＝（７２・Ｅ・Ｉ・Ｌ／ｍ・Ｌ´4 ）0.5 ・・・（２）Assuming that the longitudinal elastic modulus is E, the secondary moment of area is I, and the total length between 3 and m is L, the primary bending eigenvalue ω in this case is expressed by the following equation (1). ω = (72 · E · I / m · L 3 ) 0.5 (1) Next, considering the case where the total length between 3 mass m is L ′ shorter than L, the mass at this time is If m ′, m ′ = m
・ (L ′ / L), the primary bending eigenvalue ω at this time
'Is expressed by the following equation (2). ω ′ = (72 · E · I · L / m · L ′ 4 ) 0.5 ... (2)
【００１０】従って、（１）（２）から、（３）式が導
かれる。 ω´／ω＝（Ｌ4 ／Ｌ´4 ）0.5 ＝（Ｌ／Ｌ´）2 ・・・（３） この（３）式に示すように、軸の全長を短くすることに
より曲げ一次固有値が二乗に比例して大きな値となるの
で、回転軸の安定性を向上させることが可能となる。Therefore, from (1) and (2), equation (3) is derived. ω ′ / ω = (L 4 / L ′ 4 ) 0.5 = (L / L ′) 2 (3) As shown in the equation (3), by reducing the total length of the shaft, the bending primary eigenvalue becomes Since the value becomes larger in proportion to the square, the stability of the rotating shaft can be improved.
【００１１】図６は、磁気軸受長さによる速度裕度を示
す図表である。なお横軸に磁気軸受の短縮率（％）、縦
軸に曲げ速度からの裕度（％）とした。FIG. 6 is a table showing the speed tolerance depending on the length of the magnetic bearing. The abscissa indicates the shortening rate (%) of the magnetic bearing, and the ordinate indicates the margin (%) from the bending speed.
【００１２】図６において縦軸上の裕度０％をロータ軸
の高速回転における曲げ一次危険速度の限界として、裕
度０％を挟んでプラス側は磁気軸受けにてロータ軸の回
転支持に問題のない剛体モードを、またマイナス側はロ
ータ軸の回転支持が困難である弾性モードをあらわした
ものである。この図表を参照すれば、従来から使用して
いるロータ軸長を約２０％以上短縮すれば弾性モードか
らロータ軸の回転に問題のない剛体モードに移行するこ
とができる。言い換えれば、これまでよりロータ軸の全
長を少なくとも２０％短縮化できれば、危険速度を問題
のない範囲まで向上させることができる。また、曲げ一
次危険速度速度内の定格回転数に抑えることができるの
で、磁気軸受の制御が容易となる。In FIG. 6, a margin of 0% on the vertical axis is defined as a limit of a critical primary bending speed in high-speed rotation of the rotor shaft. The negative side represents the rigid mode, and the minus side represents the elastic mode in which it is difficult to support the rotation of the rotor shaft. Referring to this table, if the conventionally used rotor shaft length is reduced by about 20% or more, the mode can be shifted from the elastic mode to the rigid mode in which there is no problem in the rotation of the rotor shaft. In other words, if the overall length of the rotor shaft can be reduced by at least 20% than before, the critical speed can be improved to a range where there is no problem. In addition, since the rotation speed can be suppressed to the rated rotation speed within the critical bending speed, the control of the magnetic bearing is facilitated.
【００１３】本発明は、かかる課題を達成するために創
案されたものである。すなわち、本発明の目的は、ロー
タ軸長を短縮化でき、これによりロータ軸剛性を増して
危険速度を問題のない範囲まで向上させることができ、
かつ回転軸の安定性を向上させることができる高速電動
機を提供することにある。The present invention has been made in order to achieve such a task. That is, an object of the present invention is to reduce the length of the rotor shaft, thereby increasing the rigidity of the rotor shaft and improving the critical speed to a range where there is no problem.
Another object of the present invention is to provide a high-speed electric motor capable of improving the stability of a rotating shaft.
【００１４】[0014]
【解決するための手段】本発明によれば、回転自在な回
転子を形成するロータ部（３１）を有するロータ軸（３
４）と、前記ロータ部と所定の間隙を有して半径方向に
対向配置され固定子（２５）を形成する非回転のステー
タ部（２６）と、前記ロータ部を挟んで所定の間隙を有
してロータ軸を回転自在に支持する磁気軸受（３６、３
６´）と、ロータ軸の変位を検出する少なくとも２本の
変位センサ（４０）と、を備え、該変位センサが、磁気
軸受ステータの間又は磁気軸受ステータ内部に設置され
ている、ことを特徴とする高速電動機が提供される。According to the present invention, a rotor shaft (3) having a rotor portion (31) forming a rotatable rotor is provided.
4) a non-rotating stator portion (26) radially opposed to the rotor portion with a predetermined gap to form a stator (25), and a predetermined gap across the rotor portion. Bearings (36, 3) that rotatably support the rotor shaft
6 ′) and at least two displacement sensors (40) for detecting displacement of the rotor shaft, wherein the displacement sensors are installed between the magnetic bearing stators or inside the magnetic bearing stator. Is provided.
【００１５】上記本発明の構成によれば、ロータ軸の変
位を検出する少なくとも２本（本実施形態では４本）の
変位センサを磁気軸受ステータの間又は磁気軸受ステー
タ内部に設置するので、ロータ軸長を短縮化できる。従
って、ロータ軸の全長が短くなることにより曲げ一次固
有値が二乗で増大し、剛体モードに移行することがで
き、回転軸の安定性を向上させることができる。According to the configuration of the present invention, at least two (four in this embodiment) displacement sensors for detecting displacement of the rotor shaft are installed between the magnetic bearing stators or inside the magnetic bearing stator. The shaft length can be shortened. Therefore, as the overall length of the rotor shaft becomes shorter, the first-order bending eigenvalue increases in the square, and the mode can be shifted to the rigid body mode, and the stability of the rotating shaft can be improved.
【００１６】本発明の好ましい実施形態によれば前記磁
気軸受（３６、３６´）は、ロータ軸を囲むステータの
磁極が軸方向に隣接してＮ極とＳ極を構成するホモポー
ラ形磁気軸受である。According to a preferred embodiment of the present invention, the magnetic bearing (36, 36 ') is a homopolar magnetic bearing in which the magnetic poles of the stator surrounding the rotor shaft are adjacent to each other in the axial direction to form an N pole and an S pole. is there.
【００１７】この構成によれば、変位センサを、ホモポ
ーラ形磁気軸受ステータの間又は磁気軸受ステータ内部
に設置して、ロータ軸長を従来の長さより短縮化するこ
とができる。これにより、ロータ軸を剛体モードで設計
できるため、ロータ軸の回転バランス取りが容易とな
り、製造時間の短縮化ができる。また、危険速度を大幅
に向上して、高速回転でも従来制御法を適用できるので
安定した軸支持ができる。更に、磁気軸受を適用する回
転磁界の全体装置を小型化できる。According to this structure, the displacement sensor is installed between the homopolar magnetic bearing stators or inside the magnetic bearing stator, so that the rotor shaft length can be made shorter than the conventional length. As a result, the rotor shaft can be designed in the rigid mode, so that it is easy to balance the rotation of the rotor shaft and shorten the manufacturing time. In addition, the critical speed is greatly improved, and the conventional control method can be applied even at high speed rotation, so that stable shaft support can be achieved. Further, the entire device for the rotating magnetic field to which the magnetic bearing is applied can be reduced in size.
【００１８】また、別の本発明の好ましい実施形態は、
前記磁気軸受（３６、３６´）は、ロータ軸を囲むステ
ータの磁極が周方向に隣接してＮ極とＳ極を構成するヘ
テロポーラ形磁気軸受である。Another preferred embodiment of the present invention is:
The magnetic bearings (36, 36 ') are heteropolar magnetic bearings in which the magnetic poles of the stator surrounding the rotor shaft are adjacent to each other in the circumferential direction to form N and S poles.
【００１９】この構成によれば、変位センサを、ヘテロ
ポーラ形磁気軸受内部に設置したので、ロータ軸長をホ
モポーラ形磁気軸受と同様に大幅に短縮し、同様の効果
を得ることができる。According to this configuration, since the displacement sensor is installed inside the heteropolar magnetic bearing, the rotor shaft length can be greatly reduced like the homopolar magnetic bearing, and the same effect can be obtained.
【００２０】更に、別の本発明の好ましい実施形態は、
前記変位センサ（４０）は、渦電流形又はインダクタン
ス形又は静電容量形とした。Further, another preferred embodiment of the present invention is:
The displacement sensor (40) is of an eddy current type, an inductance type, or a capacitance type.
【００２１】渦電流形のセンサを磁気軸受間又は磁気軸
受内部に設置した場合、ロータ軸が中心から変位した場
合、渦電流のエネルギー損失から容易かつ迅速にロータ
軸の変位を推定することができ、これによりロータ軸の
変位の制御が容易にできる。また、もうインダクタンス
形の変位センサを磁気軸受間又は磁気軸受内部に設置し
た場合も、ロータ軸が中心から変位すれば、コイルのイ
ンダクタンス変化から前述の渦電流形と同様にロータ軸
の変位を容易に推定し制御することができる。また、静
電容量形は、軸の変位による静電容量の変化から前述の
センサ同様に、ロータ軸の変位を推定し、制御すること
ができる。When an eddy current sensor is installed between magnetic bearings or inside a magnetic bearing, when the rotor shaft is displaced from the center, the displacement of the rotor shaft can be easily and quickly estimated from the energy loss of the eddy current. Thus, the displacement of the rotor shaft can be easily controlled. Also, when an inductance type displacement sensor is installed between magnetic bearings or inside a magnetic bearing, if the rotor shaft is displaced from the center, the displacement of the rotor shaft can be easily changed from the inductance change of the coil as in the case of the eddy current type. Can be estimated and controlled. Further, the capacitance type can estimate and control the displacement of the rotor shaft from the change in capacitance due to the displacement of the shaft, similarly to the above-described sensor.
【００２２】[0022]
【発明の実施の形態】以下、本発明の好ましい実施形態
を図面を参照して説明する。なお、各図において、共通
する部分には同一の符号を付し、重複した説明を省略す
る。DESCRIPTION OF THE PREFERRED EMBODIMENTS Preferred embodiments of the present invention will be described below with reference to the drawings. In each of the drawings, common portions are denoted by the same reference numerals, and redundant description will be omitted.
【００２３】図１は、ターボ圧縮機等を直結駆動する高
速電動機を示す全体構成図である。図２は、図１のＡ−
Ａ矢視図で、ホモポーラ形磁気軸受に本発明を適用した
ものである。同様に図３は、図１のＡ−Ａ矢視図の別の
実施形態のヘテロポーラ形磁気軸受に本発明を適用した
ものである。FIG. 1 is an overall configuration diagram showing a high-speed motor for directly driving a turbo compressor or the like. FIG. 2 is a cross-sectional view of FIG.
FIG. 3 is a view as viewed from the direction of the arrow A, in which the present invention is applied to a homopolar magnetic bearing. Similarly, FIG. 3 shows an embodiment in which the present invention is applied to a heteropolar magnetic bearing according to another embodiment of the present invention as viewed from the direction of arrows AA in FIG.
【００２４】図１において、本発明の高速電動機２１
は、ケーシング２３の内周面２４に、非回転の固定子２
５が取付けられている。この固定子２５は、固定子鉄心
２７と図示しない固定子巻線とからなり、高速電動機の
ステータ部２６を形成する。固定子鉄心２７は、鉄損を
軽減するため複数枚の薄板鋼板を軸方向に積層させてい
る。Referring to FIG. 1, the high-speed motor 21 of the present invention
Is provided on the inner peripheral surface 24 of the casing 23 with the non-rotating stator 2
5 are attached. The stator 25 includes a stator core 27 and a stator winding (not shown), and forms a stator section 26 of a high-speed motor. The stator iron core 27 has a plurality of thin steel plates laminated in the axial direction to reduce iron loss.
【００２５】一方、ステータ部２６の内周面と所定の間
隙δを保持して回転子３０が配置されている。回転子３
０は中央部近傍に高速電動機のをなすロータ部３１を形
成する積層鉄心（ロータコア）３２と、ロータ軸３４か
らなる。ロータ軸３４の両端には例えば図示しない１段
インペラと２段インペラを取付けている。On the other hand, the rotor 30 is arranged so as to maintain a predetermined gap δ from the inner peripheral surface of the stator portion 26. Rotor 3
Reference numeral 0 denotes a laminated core (rotor core) 32 forming a rotor section 31 forming a high-speed motor near the center, and a rotor shaft 34. For example, a one-stage impeller and a two-stage impeller (not shown) are attached to both ends of the rotor shaft 34.
【００２６】上述した回転子３０のロータ部３１と固定
子２５のステータ部２６により、高速回転（例えば、１
０万ｍｉｎ-1以上）する高速電動機を形成している。The above-described rotor 31 of the rotor 30 and the stator 26 of the stator 25 rotate at high speed (for example, 1
(More than 100,000 min -1 ).
【００２７】また、ロータ軸３４のロータ部３１を挟ん
だ状態でロータ部３１の外径より小径の軸部３５が設け
られている。更に夫々の軸部３５と所定の間隙Ｃ１を有
してケーシング２３の内周面２４に磁気軸受３６が配置
されている。磁気軸受３６は、ロータ軸３４に発生する
半径方向の変位を制御し、高速で回転自在にロータ軸３
４を無接触で支持する。A shaft 35 having a smaller diameter than the outer diameter of the rotor 31 is provided with the rotor 31 of the rotor shaft 34 interposed therebetween. Further, a magnetic bearing 36 is disposed on the inner peripheral surface 24 of the casing 23 with a predetermined gap C1 from each of the shaft portions 35. The magnetic bearing 36 controls the radial displacement generated on the rotor shaft 34 and is rotatable at high speed.
4 is supported without contact.
【００２８】更に、図１及び図２において、磁気軸受３
６は、ロータ軸３４を囲むステータ部２６の磁極３７が
軸方向に隣接してＮ極とＳ極を構成するホモポーラ形磁
気軸受である。このホモポーラ形磁気軸受３６は、ケー
シング２３内に取付けられている。図２（Ｃ）に示すよ
うに、各磁気軸受３６は、断面形状がコ字形状でかつ積
層鋼板で形成されたステータコア３８とコイル３９から
なる。この構成により軸方向に隣接して、磁極３７にＮ
極とＳ極を有し、非接触でロータ軸３４を支持する。Further, in FIG. 1 and FIG.
Numeral 6 denotes a homopolar magnetic bearing in which the magnetic poles 37 of the stator section 26 surrounding the rotor shaft 34 are adjacent to each other in the axial direction to form N and S poles. The homopolar magnetic bearing 36 is mounted in the casing 23. As shown in FIG. 2C, each magnetic bearing 36 has a stator core 38 and a coil 39 each having a U-shaped cross section and formed of a laminated steel plate. With this configuration, the magnetic pole 37 is N
It has a pole and an S pole, and supports the rotor shaft 34 in a non-contact manner.
【００２９】また、本発明では、ロータ軸３４の変位を
検出する４本の変位センサ４０を、図２（Ａ）では、４
等分されたホモポーラ形磁気軸受３６の間にケーシング
２３を貫通させて設置させた。また、図２（Ｂ）、
（Ｃ）の例では、同じく４本の変位センサ４０を４等分
された夫々のホモポーラ形磁気軸受３６内部にケーシン
グ２３と共に貫通させて配置させた。According to the present invention, four displacement sensors 40 for detecting the displacement of the rotor shaft 34 are provided in FIG.
The casing 23 was penetrated and installed between the equally divided homopolar magnetic bearings 36. FIG. 2B,
In the example of (C), similarly, four displacement sensors 40 are penetrated and arranged inside the homopolar magnetic bearing 36 equally divided into four together with the casing 23.
【００３０】このように変位センサの設置場所を、ホモ
ポーラ形磁気軸受の間又は磁気軸受内部としたので、ロ
ータ軸長を従来の長さより大幅に短縮することができ
る。これにより前述の図５の（３）式に示したように曲
げ一次固有値が増大して回転軸の安定性が向上する。更
に図６で説明したように例えば従来設計のロータ軸でも
変位センサを磁気軸受ユニットの領域内に挿入すれば、
ロータ軸長を短縮化できれば、ロータ軸を剛体モードで
設計できるため、高速回転でも従来制御法を適用できる
ので安定した軸支持ができる。またロータ軸の回転バラ
ンス取りが容易となり、製造時間の短縮化ができる。更
に危険速度を向上させる共に磁気軸受を適用する回転磁
界の全体装置を小型化できる。Since the displacement sensor is installed between the homopolar magnetic bearings or inside the magnetic bearings, the rotor shaft length can be greatly reduced compared to the conventional length. As a result, as shown in the above-mentioned equation (3) of FIG. 5, the primary bending eigenvalue increases, and the stability of the rotating shaft improves. Further, as described with reference to FIG. 6, for example, even if the displacement sensor is inserted into the area of the magnetic bearing unit even with the rotor shaft of the conventional design,
If the rotor shaft length can be reduced, the rotor shaft can be designed in the rigid body mode, and the conventional control method can be applied even at high speed rotation, so that stable shaft support can be achieved. Further, it is easy to balance the rotation of the rotor shaft, and the manufacturing time can be reduced. Further, it is possible to improve the critical speed and reduce the size of the entire device for the rotating magnetic field to which the magnetic bearing is applied.
【００３１】次に、図３は本発明の別の実施形態で、ヘ
テロポーラ形磁気軸受と変位センサとの関連を示す配置
図である。図３において、図２と同様に、ロータ軸３４
のロータ部３１を挟んだ状態でロータ部３１の外径より
小径の軸部３５が設けられている。更に軸部３５と所定
の間隙Ｃ１を有して、ケーシング２３の内周面２４にロ
ータ軸３４を支持する磁気軸受３６´が配置されてい
る。Next, FIG. 3 is a layout view showing a relation between a heteropolar magnetic bearing and a displacement sensor according to another embodiment of the present invention. In FIG. 3, as in FIG.
A shaft portion 35 having a smaller diameter than the outer diameter of the rotor portion 31 is provided with the rotor portion 31 interposed therebetween. Further, a magnetic bearing 36 ′ that supports the rotor shaft 34 is disposed on the inner peripheral surface 24 of the casing 23 with a predetermined gap C1 from the shaft portion 35.
【００３２】また、この例で、磁気軸受３６´は、ロー
タ軸３４の軸部３５を囲むステータ４１の磁極４２が周
方向に隣接してＮ極とＳ極を構成するヘテロポーラ形磁
気軸受３６´である。更にこのヘテロポーラ形磁気軸受
３６´は、図３に示すように回転するロータ軸３４の軸
部３５を所定の間隙Ｃ１を有してケーシング２３内に取
付けられ、ロータ軸３４の軸部３５を囲むステータ４１
の磁極４２が，周方向に隣接してコイル４３により磁石
のＮ極とＳ極を構成し、対向位置にある磁極４２の吸引
力を制御してロータ軸３４を非接触で支持している。In this example, the magnetic bearing 36 'is a heteropolar type magnetic bearing 36' in which the magnetic poles 42 of the stator 41 surrounding the shaft portion 35 of the rotor shaft 34 are adjacent to each other in the circumferential direction to form N poles and S poles. It is. Further, in the heteropolar magnetic bearing 36 ', as shown in FIG. 3, the shaft 35 of the rotating rotor shaft 34 is mounted in the casing 23 with a predetermined gap C1, and surrounds the shaft 35 of the rotor shaft 34. Stator 41
The magnetic poles 42 constitute the N pole and the S pole of the magnet by the coil 43 adjacent to each other in the circumferential direction, and control the attractive force of the magnetic pole 42 at the opposing position to support the rotor shaft 34 in a non-contact manner.
【００３３】このように構成されたヘテロポーラ形磁気
軸受３６´に対して、図３（Ａ）に示す例では、４本の
変位センサ４０を、周方向に隣接する磁極のＮ極とＮ極
の間、及びＳ極とＳ極の間にケーシング２３を貫通させ
て設置している。また、図３（Ｂ）の例では、同じく４
本の変位センサ４０を４５度移動させて周方向に隣接す
る磁極のＮ極とＳ極の間にケーシング２３を貫通させて
配置ししている。このように変位センサの設置場所を、
ヘテロポーラ形磁気軸受の内部としたので、ロータ軸長
をホモポーラ形磁気軸受と同様に従来より短縮化でき、
前述のホモポーラ形磁気軸受と同様な効果を得ることが
できる。In the example shown in FIG. 3A, with respect to the heteropolar type magnetic bearing 36 'configured as described above, in the example shown in FIG. The casing 23 is penetrated and installed between the S poles and between the S poles. Also, in the example of FIG.
The displacement sensor 40 is moved by 45 degrees, and the casing 23 is disposed so as to penetrate between the N pole and the S pole of the magnetic poles adjacent in the circumferential direction. Thus, the installation location of the displacement sensor is
Since it is inside the heteropolar type magnetic bearing, the rotor shaft length can be shortened as compared with the conventional homopolar type magnetic bearing,
The same effect as that of the above-described homopolar magnetic bearing can be obtained.
【００３４】また、変位センサ４０には、渦電流形又は
インダクタンス形又は静電容量形を用いる。これらの変
位センサを夫々の磁気軸受の磁気軸受の間又は磁気軸受
内部に、等配の位置に設置するのがよい。渦電流形の変
位センサを設置した場合に、ロータ軸が中心から変位し
た場合は渦電流のエネルギー損失から容易かつ迅速にロ
ータ軸の変位を推定することができ、これによりロータ
軸の変位の制御が容易にできる。また、インダクタンス
形の変位センサを設置しても、ロータ軸が中心から変位
すれば、コイルのインダクタンス変化から前述の渦電流
形と同様にロータ軸の変位を容易に推定し制御すること
ができる。また、静電容量形は、軸変位による静電容量
変化により、変位を推定でき、同様の効果が得られる。As the displacement sensor 40, an eddy current type, an inductance type, or a capacitance type is used. These displacement sensors are preferably installed at equal positions between or within the magnetic bearings of the respective magnetic bearings. If the rotor shaft is displaced from the center when an eddy current type displacement sensor is installed, the displacement of the rotor shaft can be easily and quickly estimated from the energy loss of the eddy current, thereby controlling the displacement of the rotor shaft. Can be easily done. Even if an inductance type displacement sensor is provided, if the rotor shaft is displaced from the center, the displacement of the rotor shaft can be easily estimated and controlled from the change in the inductance of the coil in the same manner as in the eddy current type. In the capacitance type, displacement can be estimated by capacitance change due to axial displacement, and the same effect can be obtained.
【００３５】なお、本発明は上述した実施形態に限定さ
れず、本発明の要旨を逸脱しない範囲で種々変更できる
ことは勿論である。It should be noted that the present invention is not limited to the above-described embodiment, but can be variously modified without departing from the gist of the present invention.
【００３６】[0036]
【発明の効果】上述したように本発明の高速電動機によ
れば、ロータ軸長を短縮化でき、これにより軸ロータ剛
性が増して危険速度を向上させることができ、かつ回転
軸の安定性を向上させることができる、等の優れた効果
を有する。As described above, according to the high-speed electric motor of the present invention, the rotor shaft length can be shortened, whereby the rigidity of the shaft rotor can be increased and the critical speed can be improved, and the stability of the rotating shaft can be improved. It has excellent effects such as being able to be improved.
【図１】ターボ圧縮機等を直結駆動する本発明の高速電
動機を示す全体構成図である。FIG. 1 is an overall configuration diagram showing a high-speed motor of the present invention that directly drives a turbo compressor or the like.
【図２】図１のＡ−Ａ矢視図である。FIG. 2 is a view taken along the line AA of FIG. 1;
【図３】別の実施形態を示す図２と同様の矢視図であ
る。FIG. 3 is a view similar to FIG. 2, showing another embodiment.
【図４】従来の高速電動機の模式図である。FIG. 4 is a schematic view of a conventional high-speed motor.
【図５】３質点ロータモデルを示す模式図である。FIG. 5 is a schematic diagram showing a three-mass rotor model.
【図６】磁気軸受長さによる速度裕度を示す図表であ
る。FIG. 6 is a table showing a speed tolerance according to a magnetic bearing length.
１、２１ 高速電動機駆動圧縮機 ３、２３ ケーシング ４、２４ 内周面 ５、２５ 固定子 ６、２６ ステータ部 ７、２７ 固定子鉄心 １０、３０ 回転子 １１、３１ ロータ部 １２、３２ 積層鉄心（ロータコア） １４、３４ ロータ軸 １５、３５ 軸部 １６ 磁気軸受 １７、４０ 変位センサ ３６ ホモポーラ形磁気軸受（磁気軸受） ３６´ ヘテロポーラ形磁気軸受（磁気軸受） ３７、４２ 磁極 ３８ ステータコア ３９、４３ コイル ４１ ステータ δ、Ｃ１、Ｃ２ 間隙 1,21 High-speed motor driven compressor 3,23 Casing 4,24 Inner peripheral surface 5,25 Stator 6,26 Stator part 7,27 Stator core 10,30 Rotor 11,31 Rotor part 12,32 Laminated core ( Rotor core) 14, 34 Rotor shaft 15, 35 Shaft 16 Magnetic bearing 17, 40 Displacement sensor 36 Homopolar magnetic bearing (magnetic bearing) 36 'Heteropolar magnetic bearing (magnetic bearing) 37, 42 Magnetic pole 38 Stator core 39, 43 Coil 41 Stator δ, C1, C2 gap
フロントページの続き (72)発明者 高橋 俊雄 東京都江東区豊洲２丁目１番１番地 石川 島播磨重工業株式会社東京第一工場内 (72)発明者 桑田 厳 東京都江東区豊洲２丁目１番１番地 石川 島播磨重工業株式会社東京第一工場内 (72)発明者 杉谷 宗寧 東京都江東区豊洲２丁目１番１番地 石川 島播磨重工業株式会社東京第一工場内 Ｆターム(参考） 3J102 AA01 BA03 BA17 CA09 CA10 CA19 DA03 DA09 DA30 DB01 DB05 DB10 GA13 5H605 AA04 BB07 CC02 CC04 EB12 5H607 AA04 BB01 BB14 BB26 CC01 DD03 DD09 DD16 FF07 GG01 GG17 HH01 HH05 HH09 5H611 AA01 AA03 PP03 QQ03 RR00 TT00 UA05 Continued on the front page (72) Inventor Toshio Takahashi 2-1-1, Toyosu, Koto-ku, Tokyo Ishikawa Shima-Harima Heavy Industries Co., Ltd. Tokyo 1st Plant (72) Inventor Takeshi Kuwata 2-1-1, Toyosu, Koto-ku, Tokyo Address Ishikawa Shima-Harima Heavy Industries, Ltd., Tokyo Daiichi Plant (72) Inventor, Soneya 2-1-1, Toyosu, Koto-ku, Tokyo Ishikawa Shima-Harima Heavy Industries Co., Ltd. Tokyo Daiichi Plant F-term (reference) 3J102 AA01 BA03 BA17 CA09 CA10 CA19 DA03 DA09 DA30 DB01 DB05 DB10 GA13 5H605 AA04 BB07 CC02 CC04 EB12 5H607 AA04 BB01 BB14 BB26 CC01 DD03 DD09 DD16 FF07 GG01 GG17 HH01 HH05 HH09 5H611 AA01 AA03 PP03 QQ03 RR00 RR00
Claims (4)
（３１）を有するロータ軸（３４）と、前記ロータ部と
所定の間隙を有して半径方向に対向配置され固定子（２
５）を形成する非回転のステータ部（２６）と、前記ロ
ータ部を挟んで所定の間隙を有してロータ軸を回転自在
に支持する磁気軸受（３６、３６´）と、ロータ軸の変
位を検出する少なくとも２本の変位センサ（４０）と、
を備え、 該変位センサが、磁気軸受ステータの間又は磁気軸受ス
テータ内部に設置されている、ことを特徴とする高速電
動機。1. A rotor shaft (34) having a rotor portion (31) forming a rotatable rotor, and a stator (2) disposed radially opposed to the rotor portion with a predetermined gap therebetween.
5) a non-rotating stator portion (26), magnetic bearings (36, 36 ') rotatably supporting the rotor shaft with a predetermined gap sandwiching the rotor portion, and displacement of the rotor shaft At least two displacement sensors (40) for detecting
Wherein the displacement sensor is installed between the magnetic bearing stators or inside the magnetic bearing stator.
タ軸を囲むステータの磁極が軸方向に隣接してＮ極とＳ
極を構成するホモポーラ形磁気軸受である、ことを特徴
とする請求項１に記載の高速電動機。2. The magnetic bearing (36, 36 '), wherein the magnetic poles of the stator surrounding the rotor shaft are adjacent to each other in the axial direction and the N pole and the S pole are adjacent to each other.
The high-speed electric motor according to claim 1, wherein the high-speed electric motor is a homopolar magnetic bearing that forms a pole.
タ軸を囲むステータの磁極が周方向に隣接してＮ極とＳ
極を構成するヘテロポーラ形磁気軸受である、ことを特
徴とする請求項１に記載の高速電動機。3. The magnetic bearing (36, 36 '), wherein the magnetic poles of the stator surrounding the rotor shaft are adjacent to each other in the circumferential direction and the N pole and the S pole are
2. The high-speed electric motor according to claim 1, wherein the high-speed electric motor is a heteropolar magnetic bearing constituting a pole.
はインダクタンス形又は静電容量形である、ことを特徴
とする請求項１乃至３のいずれかに記載の高速電動機。4. The high-speed motor according to claim 1, wherein the displacement sensor is of an eddy current type, an inductance type, or a capacitance type.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2000399537A JP2002199655A (en) | 2000-12-27 | 2000-12-27 | High speed motor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2000399537A JP2002199655A (en) | 2000-12-27 | 2000-12-27 | High speed motor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JP2002199655A true JP2002199655A (en) | 2002-07-12 |
Family
ID=18864302
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2000399537A Pending JP2002199655A (en) | 2000-12-27 | 2000-12-27 | High speed motor |
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| JP2002286036A (en) * | 2001-03-27 | 2002-10-03 | Ebara Corp | Magnetic bearing apparatus |
| JP2008048560A (en) * | 2006-08-20 | 2008-02-28 | Tokyo Univ Of Science | Bearing-less rotating machine |
| WO2013191422A1 (en) * | 2012-06-19 | 2013-12-27 | 한국기계연구원 | Composite magnetic bearing having auxiliary bearing combined thereto |
| WO2017006844A1 (en) * | 2015-07-07 | 2017-01-12 | エドワーズ株式会社 | Electromagnet unit, magnetic bearing device, and vacuum pump |
| JP2018105457A (en) * | 2016-12-27 | 2018-07-05 | 三菱電機株式会社 | Radial magnetic bearing and blower |
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