JPS62228710A - Bearing device - Google Patents

Bearing device

Info

Publication number
JPS62228710A
JPS62228710A JP6956986A JP6956986A JPS62228710A JP S62228710 A JPS62228710 A JP S62228710A JP 6956986 A JP6956986 A JP 6956986A JP 6956986 A JP6956986 A JP 6956986A JP S62228710 A JPS62228710 A JP S62228710A
Authority
JP
Japan
Prior art keywords
bearing
rotating member
thrust
fixed shaft
thrust 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.)
Pending
Application number
JP6956986A
Other languages
Japanese (ja)
Inventor
Katsuhiko Tanaka
克彦 田中
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
NSK Ltd
Original Assignee
NSK Ltd
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by NSK Ltd filed Critical NSK Ltd
Priority to JP6956986A priority Critical patent/JPS62228710A/en
Publication of JPS62228710A publication Critical patent/JPS62228710A/en
Pending legal-status Critical Current

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  • Sliding-Contact Bearings (AREA)

Abstract

PURPOSE:To shorten axial dimension and obtain a compact bearing device by arranging a magnetic thrust bearing between an axial direction end of a rotary member fitted around a fixed shaft and a housing. CONSTITUTION:An upper end part in axial direction of a fixed shaft 22 is press-fit, glued and fixed into a fixed shaft supporting member 22b of a housing 20. On the peripheral surface of the fixed shaft 22 are arranged radial bearing surfaces 23 and 24 provided with dynamic pressure generating grooves 23a and 24a in herringbone shape. Further, around the lower end is rotatably fitted a hollow-shaped rotary member 32 supported with a magnetic thrust bearing. As a thrust receiving surface 44 side of a thrust receiver 40 on the rotary member 32 side is magnetized to the N pole and a thrust bearing surface 46 side of a thrust bearing 45 on the housing 20 side is also magnetized to the N pole, the thrust bearing supports the rotary member in a levitated condition by means of magnetic repulsive force.

Description

【発明の詳細な説明】 〔産業上の利用分野〕 この発明は事務機、映像機器、音響機器等の回転機構に
使用される軸受装置に関する。
DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a bearing device used in a rotating mechanism of an office machine, video equipment, audio equipment, etc.

〔従来の技術〕[Conventional technology]

従来のこの種の軸受装置としては、たとえば第2図に示
す光偏向器に使用した軸受装置が知られている。この光
偏向器は、レーザー光の透過窓2を備えるハウジング1
に固定軸3の軸方向の下端部が固着され、光偏向器4が
取り付けられた回転部材5を固定軸3の周りに回転可能
に嵌装している。
As a conventional bearing device of this type, for example, a bearing device used in an optical deflector shown in FIG. 2 is known. This optical deflector includes a housing 1 having a laser beam transmission window 2.
The lower end of the fixed shaft 3 in the axial direction is fixed to the fixed shaft 3, and a rotating member 5 to which the optical deflector 4 is attached is rotatably fitted around the fixed shaft 3.

固定軸3の軸方向の両端部には、ラジアル荷重を支持す
るのに有効なヘリングボーン状のみぞ6a、6bを形成
し、軸方向の中間部には、スラスト荷重を支持するのに
有効なスパイラル状のみぞ7を形成している。
Herringbone-shaped grooves 6a and 6b effective for supporting radial loads are formed at both ends of the fixed shaft 3 in the axial direction, and grooves 6a and 6b effective for supporting thrust loads are formed in the middle part of the fixed shaft 3 in the axial direction. A spiral groove 7 is formed.

回転部材5の軸方向の端部のうち、固定軸3の固定端側
の下端部は開口端であって、これと反対側の上端部には
、スラスト圧力調整用の排気穴8が軸方向に貫通するス
ラスト受9を嵌着して、その底面9aを固定軸3の軸方
向上端面3aに対向させている。
Among the axial ends of the rotating member 5, the lower end on the fixed end side of the fixed shaft 3 is an open end, and the upper end on the opposite side has an exhaust hole 8 for thrust pressure adjustment in the axial direction. A thrust receiver 9 penetrating through the shaft receiver 9 is fitted, and its bottom surface 9a faces the axially upper end surface 3a of the fixed shaft 3.

回転部材5の外周面には、駆動モータのロータ10を取
り付け、ロータlOの外周面に対向させて配置したステ
ータ12をハウジング1に取り付けて、回転部材5を固
定軸30周りに回転させるようにしている。
A rotor 10 of a drive motor is attached to the outer circumferential surface of the rotating member 5, and a stator 12 disposed opposite to the outer circumferential surface of the rotor IO is attached to the housing 1, so that the rotating member 5 is rotated around the fixed shaft 30. ing.

回転部材5が回転すると、固定軸3の下端部のみぞ6b
のボンピング作用による動圧が発生し、回転部材5の下
端側の開口端から固定軸3との間のラジアル軸受すき間
15に流入した空気が、中間部のみぞ7のポンピング作
用によって上昇し、この空気は、上端側のみぞ6aの動
圧に打ち勝ってさらに上昇し、スラスト受9の排気穴8
から外部へ流出する。これにより、回転部材5は固定軸
3との間のすき間に形成される高圧力の空気膜によって
固定軸3の周りに非接触状態を保って回転するとともに
、スラスト受9の底面9aが固定軸3の軸方向上端面3
aから浮上して軸方向に対しても非接触状態を保持する
When the rotating member 5 rotates, the groove 6b in the lower end of the fixed shaft 3
Dynamic pressure is generated due to the pumping action of the rotary member 5, and the air that flows into the radial bearing gap 15 between the lower end side of the rotating member 5 and the fixed shaft 3 rises due to the pumping action of the groove 7 in the intermediate portion. The air overcomes the dynamic pressure in the groove 6a on the upper end side and rises further, reaching the exhaust hole 8 of the thrust receiver 9.
leaks to the outside. As a result, the rotating member 5 rotates around the fixed shaft 3 while maintaining a non-contact state due to the high-pressure air film formed in the gap between the rotary member 5 and the fixed shaft 3, and the bottom surface 9a of the thrust receiver 9 rotates around the fixed shaft 3. Axial upper end surface 3 of 3
It levitates from a and maintains a non-contact state also in the axial direction.

〔発明が解決しようとする問題点〕[Problem that the invention seeks to solve]

上記の従来の軸受装置においては、回転部材5と固定軸
3との間のラジアル軸受すき間15には、固定軸3の軸
方向の両端部のみぞ5a、6bと中間部のみぞ7とによ
って空気膜が形成され、回転部材5と固定軸3との間の
半径方向には完全な非接触状態が保持され4から、ラジ
アル負荷容量については問題はないが、回転部材5のス
ラスト受9の底面9aと固定軸3の軸方向上端面3aと
の間で軸方向の非接触状態を保持するのに必要かつ十分
なスラスト負荷容量を得るためには、固定軸3の中間部
のみぞ7の軸方向長さを、ある程度長くする必要があり
、中間部のみぞ7で発生する動圧によってスラスト負荷
能力を得るためには固定軸3の軸方向の長さ寸法を一定
限度以下に短くすることができないので、これに応じて
回転部材5の軸方向長さも長くなるという問題がある。
In the above-mentioned conventional bearing device, the radial bearing gap 15 between the rotating member 5 and the fixed shaft 3 is filled with air by the grooves 5a, 6b at both axial ends of the fixed shaft 3 and the groove 7 at the intermediate part. A film is formed, and a complete non-contact state is maintained in the radial direction between the rotating member 5 and the fixed shaft 3.Therefore, there is no problem with the radial load capacity, but the bottom surface of the thrust receiver 9 of the rotating member 5 In order to obtain the necessary and sufficient thrust load capacity to maintain a non-contact state in the axial direction between 9a and the axial upper end surface 3a of the fixed shaft 3, it is necessary to It is necessary to increase the length in the axial direction to a certain extent, and in order to obtain thrust load capacity by the dynamic pressure generated in the groove 7 in the intermediate portion, the length in the axial direction of the fixed shaft 3 must be shortened to a certain limit or less. Since this is not possible, there is a problem in that the axial length of the rotating member 5 increases accordingly.

また、従来の軸受装置は、上記のように固定軸3の軸方
向上端面3aに回転部材5のスラスト受9の底面9aを
対向させている。このため、回転部材5の起動時および
停止時には、固定軸3の軸方向上端面3aと回転部材3
のスラスト受9の底面9aと無潤滑状態ですべり接触す
ることになり、その結果、摩擦トルクが大きぐなるほか
、固定軸3と回転部材5とのすべり接触面が摩耗しやす
く、耐久性が低下するという問題がある。
Further, in the conventional bearing device, as described above, the bottom surface 9a of the thrust bearing 9 of the rotating member 5 is opposed to the axially upper end surface 3a of the fixed shaft 3. Therefore, when starting and stopping the rotating member 5, the axial upper end surface 3a of the fixed shaft 3 and the rotating member 3
This results in sliding contact with the bottom surface 9a of the thrust receiver 9 without lubrication, which results in an increase in frictional torque, and the sliding contact surface between the fixed shaft 3 and the rotating member 5 is easily worn out, reducing durability. There is a problem with the decline.

この発明は、上記のような問題を解決して、固定軸およ
び回転部材の軸方向の長さ寸法が短く、かつ耐久性にす
ぐれた軸受装置を提供することを目的とする。
SUMMARY OF THE INVENTION An object of the present invention is to solve the above problems and provide a bearing device in which the fixed shaft and rotating member have short axial length dimensions and are highly durable.

〔問題点を解決するための手段〕[Means for solving problems]

この発明の軸受装置は、ハウジングに固定軸の軸方向一
端が固着され、固定軸の周りには、固定軸の固定端側を
開口端とする回転部材がラジアル軸受すき間を介して回
転可能に嵌装されている。
In the bearing device of the present invention, one axial end of a fixed shaft is fixed to the housing, and a rotating member having an open end on the fixed end side of the fixed shaft is rotatably fitted around the fixed shaft through a radial bearing gap. equipped.

固定軸のラジアル軸受面と回転部材のラジアル受面との
少な(とも一方に動圧発生用のみぞを形成して、回転部
材を固定軸との間のラジアル軸受すき間内の流体膜によ
って半径方向に支持する動圧形のラジアル流体軸受を設
けている。
The radial bearing surface of the fixed shaft and the radial bearing surface of the rotating member are formed with a groove for generating dynamic pressure on one side, and the rotating member is moved in the radial direction by a fluid film in the radial bearing gap between the fixed shaft and the rotating member. A dynamic pressure type radial fluid bearing is installed to support the system.

回転部材の開口端とは反対側の端部とハウジングとには
、それぞれ磁石からなるスラスト受とスラスト軸受とを
対向させて、スラスト受面側とスラスト軸受面側との磁
極が同一磁極となるよに取り付け、回転部材をスラスト
受面とスラスト軸受面との間のスラスト軸受すき間の磁
気反発力によって軸方向に支持するスラスト磁気軸受を
設けている。
At the end of the rotating member opposite to the open end and the housing, a thrust receiver and a thrust bearing made of magnets are arranged to face each other, so that the magnetic poles on the thrust receiving surface side and the thrust bearing surface side are the same magnetic pole. A thrust magnetic bearing is installed to support the rotating member in the axial direction by the magnetic repulsion force in the thrust bearing gap between the thrust bearing surface and the thrust bearing surface.

〔作用〕[Effect]

この発明の軸受装置において、回転部材が固定軸の周り
を回転すると、固定軸のラジアル軸受面と回転部材のラ
ジアル受面との少なくとも一方に形成されている動圧発
生用のみぞのボンピング作用による動圧が発生し、回転
部材の開口端から固定軸との間に流入した流体による流
体膜がラジアル軸受すき間に形成されて圧力が高くなり
、この流体膜の圧力によって回転部材が半径方向に支持
され、固定軸の周りに非接触状態を保って回転する。
In the bearing device of the present invention, when the rotating member rotates around the fixed shaft, the pumping action of the groove for generating dynamic pressure formed on at least one of the radial bearing surface of the fixed shaft and the radial bearing surface of the rotating member is applied. Dynamic pressure is generated, and a fluid film formed by the fluid flowing between the open end of the rotating member and the fixed shaft is formed in the radial bearing gap, increasing the pressure, and the rotating member is supported in the radial direction by the pressure of this fluid film. and rotates around a fixed axis in a non-contact manner.

また、回転部材の開口端とは反対側の軸方向端部のスラ
スト受とこれに対向するハウジングのスラスト軸受との
間のスラスト軸受すき間には、磁石による磁気反発力が
作用し、回転部材は浮上した位置で軸方向に支持されて
いるため、軸方向の両側端部ともハウジングに対して非
接触状態を保って回転する。
In addition, a magnetic repulsion force by the magnet acts in the thrust bearing gap between the thrust bearing at the axial end opposite to the open end of the rotating member and the thrust bearing in the housing facing this, and the rotating member Since it is supported in the axial direction in the floating position, both ends in the axial direction rotate while maintaining a non-contact state with respect to the housing.

〔実施例〕〔Example〕

以下、この発明の実施例について、図面を参照して説明
する。
Embodiments of the present invention will be described below with reference to the drawings.

第1図は、この発明の軸受装置を、前記第2図の光偏向
器に適用した実施例を示す縦断面図である。
FIG. 1 is a longitudinal sectional view showing an embodiment in which the bearing device of the present invention is applied to the optical deflector shown in FIG. 2.

同図において、ハウジング20は、円筒状の側壁部材2
0aの上端側と下端側とに、それぞれ固定軸支持部材2
0bとスラスト軸受取付部材20Cとを嵌着して密閉し
、外部からの塵埃その他の異物の侵入を防止した構造に
なっており、ハウジング20の内部には空気等の気体が
封入されている。
In the figure, the housing 20 includes a cylindrical side wall member 2
A fixed shaft support member 2 is provided on the upper end side and the lower end side of 0a, respectively.
0b and the thrust bearing mounting member 20C are fitted and sealed to prevent dust and other foreign matter from entering from the outside, and the inside of the housing 20 is filled with gas such as air.

このハウジング20の固定軸支持部材20bには、固定
軸22の軸方向の上端部が圧入、接着又は焼ばめにより
固着されている。固定軸22の外周面は、軸方向の上端
部と下端部との2個所が円筒状のラジアル軸受面23.
24であり、このラジアル軸受面23.24には、それ
ぞれ矢羽根先端が同一方向であるヘリングボーン状の動
圧発生用のみぞ23a、24aが形成されている。
The upper end portion of the fixed shaft 22 in the axial direction is fixed to the fixed shaft support member 20b of the housing 20 by press fitting, adhesive, or shrink fit. The outer circumferential surface of the fixed shaft 22 has two cylindrical radial bearing surfaces 23 , an upper end and a lower end in the axial direction.
24, and herringbone-shaped grooves 23a and 24a for generating dynamic pressure are formed in the radial bearing surfaces 23 and 24, respectively, with the fletching tips facing in the same direction.

上記の固定軸22の外周には、下端部が後述するスラス
ト磁気軸受によって支持された中空状の回転部材32を
回転可能に嵌装している。
A hollow rotary member 32 whose lower end is supported by a thrust magnetic bearing, which will be described later, is rotatably fitted onto the outer periphery of the fixed shaft 22.

回転部材32は、軸方向の2個所の円筒状のラジアル受
面33.34が、それぞれ固定軸22との間のラジアル
軸受すき間35内の気体を介して固定軸22のラジアル
軸受面2.3.24と対向し、コノラジアル軸受面23
.24とラジアル受面33.34とが、回転部材32を
固定軸22の周りに半径方向に支持する動圧形のラジア
ル気一体軸受を構成している。
The rotating member 32 has two axially cylindrical radial bearing surfaces 33 and 34 that contact the radial bearing surface 2.3 of the fixed shaft 22 via gas in the radial bearing gap 35 between the rotating member 32 and the fixed shaft 22, respectively. .24 and the cono radial bearing surface 23
.. 24 and the radial bearing surfaces 33 and 34 constitute a dynamic pressure type radial air integral bearing that supports the rotating member 32 in the radial direction around the fixed shaft 22.

このように、固定軸22と回転部材32との軸方向の上
下両端部の2個所に、それぞれラジアル軸受面23.2
4とラジアル受面33.34とを設けると、回転部材3
2の回転時における振れが少なくなり、安定した高速回
転性能が得られる。
In this way, radial bearing surfaces 23.
4 and the radial receiving surfaces 33 and 34, the rotating member 3
2. Runout during rotation is reduced, and stable high-speed rotation performance is obtained.

なお、固定軸22と回転部材32の材質としては、スラ
スト磁気軸受の影響を受けにくい非磁性体が好ましい。
The fixed shaft 22 and the rotating member 32 are preferably made of a non-magnetic material that is less susceptible to the effects of thrust magnetic bearings.

上記の回転部材32の軸方向端部のうち、固定軸22の
固定端側の上端部は開口端であるが、これと反対側の下
端部にはスラスト受40が嵌着されている。このスラス
ト受40は外周及び下側の、金属製リング43と該金属
製リング43に一体に成形固着された内周及び上下側の
プラスチックを備えた磁性体の永久磁石41とを有し、
永久磁石41の下端面が平面状のスラスト受面44にな
っている。
Among the axial ends of the rotating member 32, the upper end on the fixed end side of the fixed shaft 22 is an open end, and the thrust receiver 40 is fitted to the lower end on the opposite side. This thrust receiver 40 has a metal ring 43 on the outer periphery and the lower side, and a magnetic permanent magnet 41 with plastic on the inner periphery and upper and lower sides integrally molded and fixed to the metal ring 43,
The lower end surface of the permanent magnet 41 is a flat thrust receiving surface 44.

また、ハウジング20のスラスト軸受取付部材20cは
、回転部材32の下端部と対向する位置にスラスト軸受
45を取り付けている。このスラスト軸受45もプラス
チックを備えた磁性体の永久磁石からなり、上端面が平
面状のスラスト軸受面46になっている。
Further, the thrust bearing mounting member 20c of the housing 20 has a thrust bearing 45 mounted at a position facing the lower end of the rotating member 32. This thrust bearing 45 is also made of a magnetic permanent magnet made of plastic, and has a flat thrust bearing surface 46 on its upper end surface.

回転部材32側のスラスト受40は、スラスト受面44
側がN極に着磁され、ハウジング20側のスラスト軸受
45も同様にスラスト軸受面46側がN極に着磁されて
おり、互いに同−磁極側を対向させて配置して、回転部
材&2をスラスト受面44とスラスト軸受面46との間
のスラスト軸受すき間48に作用する磁気反発力により
浮上させた状態で軸方向に支持するスラスト磁気軸受を
構成している。
The thrust receiver 40 on the rotating member 32 side has a thrust receiving surface 44
The side of the thrust bearing 45 on the housing 20 side is similarly magnetized as a north pole, and the thrust bearing surface 46 side of the thrust bearing 45 on the housing 20 side is similarly magnetized as a north pole. The thrust magnetic bearing is supported in the axial direction in a floating state by a magnetic repulsion force acting on the thrust bearing gap 48 between the receiving surface 44 and the thrust bearing surface 46.

上記のように、回転部材32のスラスト受40は、外周
側の金属製リング43にプラスチックを備えた磁性体が
一体成形で固着されているため、回転部材32が高速回
転する場合に、遠心力による大きな力を受けても破損す
ることはない、この金属製リング43の素材としては、
鋼材、とくに焼入れ処理を施したステンレス鋼を使用す
るのが好ましい。
As described above, the thrust receiver 40 of the rotating member 32 has a magnetic body made of plastic fixed to the metal ring 43 on the outer peripheral side by integral molding, so that when the rotating member 32 rotates at high speed, centrifugal force The material of this metal ring 43, which will not be damaged even when subjected to a large force due to
It is preferable to use steel, especially hardened stainless steel.

なお、回転部材32のスラスト受40の軸方向に貫通す
る穴42は、固定軸22を回転部材32に挿入して組み
立てるときの作業を容易にするための排気用として設け
られたものである。
Note that the hole 42 that passes through the thrust receiver 40 of the rotating member 32 in the axial direction is provided for exhaust to facilitate the work when inserting and assembling the fixed shaft 22 into the rotating member 32.

回転部材32がスラスト磁気軸受によって軸方向に支持
されて浮上位置を保っている状態において、スラスト受
40の上端面と固定軸22の下端面との間には、軸方向
中間部が保たれるようにしである。この軸方向間隔Aは
、回転部材32の開口端面とハウジング20の固定軸支
持部材20bの内面との間の軸方曲間隔日よりも大きく
なるように設定して、回転部材32の回転時における浮
上位置に異変が起こった場合でも、スラスト受40が固
定軸22の下端面に接触するのを防止し、スラスト受4
0の磁石と固定軸z2の下端面とが接触した状態のまま
にならないようにしている。
In a state where the rotating member 32 is axially supported by the thrust magnetic bearing and maintained in the floating position, an axially intermediate portion is maintained between the upper end surface of the thrust receiver 40 and the lower end surface of the fixed shaft 22. That's how it is. This axial distance A is set to be larger than the axial curvature interval between the open end surface of the rotating member 32 and the inner surface of the fixed shaft support member 20b of the housing 20, and Even if an abnormality occurs in the floating position, the thrust receiver 40 is prevented from contacting the lower end surface of the fixed shaft 22, and the thrust receiver 4
This prevents the magnet 0 and the lower end surface of the fixed shaft z2 from remaining in contact with each other.

上記の回転部材32の回転駆動機構としては、下端側の
外周面の段部にロータ50を取り付けてその下面をリン
グ部材53によって支持固定し、ロータ50の外周側に
円筒面で対向するステータ52を、ハウジング20の支
台21に取り付けている。
As a rotational drive mechanism for the rotating member 32, a rotor 50 is attached to a stepped portion of the outer circumferential surface of the lower end side, the lower surface of which is supported and fixed by a ring member 53, and a stator 52 is opposed to the outer circumferential side of the rotor 50 with a cylindrical surface. is attached to the abutment 21 of the housing 20.

また、回転部材32の軸方向中間部のフランジ37には
、光偏向鏡55を取り付けその上端側からリング部材5
6を挟着して固定している。この光偏向鏡55には、図
示しない光源からレーザ光が入射され、光偏向鏡55に
当たって反射したレーザ光がハウジング20の側壁部材
20aの透過窓58を経て外部の感光体(図示せず)に
照射されるようになっている。
Further, an optical deflection mirror 55 is attached to the flange 37 at the axially intermediate portion of the rotating member 32, and the ring member 55 is attached from the upper end side.
6 is clamped and fixed. A laser beam is incident on the optical deflection mirror 55 from a light source (not shown), and the laser beam reflected by the optical deflection mirror 55 passes through the transmission window 58 of the side wall member 20a of the housing 20 and hits an external photoreceptor (not shown). It is now irradiated.

また、ロータ50を固定するリング部材53の下面には
環状の凹部54が設けてあり、光偏向鏡55を固定する
リング部材56の上面にも同様に環状の凹部57が設け
である。これらのリング部材53.56の凹部54,5
7には、必要に応じて適宜量の接着剤等を塗着すること
により、回転部材32の質量を調整して半径方向のアン
バランスを修正するようにしている。
Further, an annular recess 54 is provided on the lower surface of the ring member 53 that fixes the rotor 50, and an annular recess 57 is similarly provided on the upper surface of the ring member 56 that fixes the optical deflection mirror 55. Recesses 54, 5 of these ring members 53, 56
7, the mass of the rotating member 32 is adjusted and the unbalance in the radial direction is corrected by applying an appropriate amount of adhesive or the like as necessary.

前記実施例においては、固定軸22のラジアル軸受面2
3.24にヘリングボーン状のみぞ23a、24aを形
成しているが、このみぞ23a。
In the embodiment, the radial bearing surface 2 of the fixed shaft 22
Herringbone-shaped grooves 23a and 24a are formed at 3.24, and this groove 23a.

24aは回転部材32のラジアル受面33.34に形成
してもよく、またラジアル軸受面23,24とラジアル
受面33.34との双方に形成してもよい。
24a may be formed on the radial bearing surface 33.34 of the rotating member 32, or may be formed on both the radial bearing surfaces 23, 24 and the radial bearing surface 33.34.

また、スラスト磁気軸受を構成する永久磁石は、前記実
施例のようにプラスチックを備えた磁性体を用いること
により、量産が可能であって、安価に製作することがで
きるが、このほかフェライト、希土類元素などの粉末成
形体からなる焼結磁石を使用することもできる。
In addition, the permanent magnets constituting the thrust magnetic bearing can be mass-produced and manufactured at low cost by using a magnetic material with plastic as in the above embodiment. It is also possible to use sintered magnets made of powder compacts such as elements.

また、回転部材32の駆動モータは、前記実施例の円筒
形のロータ50とステータ52に代えて円盤状のロータ
を回転部材に取り付け、ステータはロータの下面側に平
面で対向させてハウジングに取り付けることもできる。
Further, in the drive motor of the rotating member 32, a disk-shaped rotor is attached to the rotating member instead of the cylindrical rotor 50 and stator 52 of the above embodiment, and the stator is attached to the housing with a plane facing the lower surface of the rotor. You can also do that.

このようにした場合は、ロータにステータの吸引力が働
いて回転部材32の回転時におけるふらつきを少なくす
ることができるから、軸受装置を水平にした横型とじて
使用することもできる。
In this case, since the suction force of the stator acts on the rotor and the wobbling of the rotating member 32 during rotation can be reduced, it is also possible to use the bearing device horizontally.

また、上記実施例におけるハウジングは、ハウジングの
構成部材によって完全に密閉されているが、ハウジング
の内部の気体をフィルタを介して外気と連通させる間接
密閉構造にすることもできる。さらに、ハウジングが一
部開放された場合は、ハウジングが設置される機器全体
が密閉構造となっていてもよい。
Further, although the housing in the above embodiment is completely sealed by the constituent members of the housing, an indirect sealing structure may be used in which the gas inside the housing is communicated with the outside air through a filter. Furthermore, when the housing is partially opened, the entire device in which the housing is installed may have a sealed structure.

なお、上記実施例では、ハウジング内に空気等の気体を
封入して使用する場合について説明したが、この発明の
軸受装置は、上記実施例に限らず、ラジアル軸受すき間
内に潤滑油を入れて、ラジアル軸受を動圧形流体軸受と
して使用する機器についても適用することができる。
In addition, in the above embodiment, a case was explained in which a gas such as air is sealed in the housing, but the bearing device of the present invention is not limited to the above embodiment. The present invention can also be applied to devices that use radial bearings as hydrodynamic bearings.

〔発明の効果〕〔Effect of the invention〕

以上説明したように、この発明の軸受装置は、固定軸の
周りに嵌装された回転部材の軸方向端部とハウジングと
の間に、スラスト磁気軸受を設けて、回転部材を軸方向
に支持しているから、ラジアル流体軸受を構成するラジ
アル軸受面とラジアル受面とは、ラジアル荷重のみを支
持する負荷容量を有しておればよく、固定軸にスラスト
負荷容量を付与するための流体軸受を設ける必要がなく
なる。したがって、この発明によれば固定軸および回転
部材の軸方向の長さ寸法を従来のものに比べて短縮する
ことができ、コンパクトで、製造も簡単な軸受装置が得
られる。
As explained above, the bearing device of the present invention includes a thrust magnetic bearing between the axial end of the rotating member fitted around the fixed shaft and the housing to support the rotating member in the axial direction. Therefore, the radial bearing surface and radial bearing surface that make up a radial fluid bearing only need to have a load capacity that supports only radial loads. There is no need to provide Therefore, according to the present invention, the axial length dimensions of the fixed shaft and the rotating member can be shortened compared to the conventional bearing device, and a bearing device that is compact and easy to manufacture can be obtained.

また、この発明によれば、回転部材はスラスト磁気軸受
の磁気反発力によって、常時浮上した状態で軸方向に支
持されているから、回転部材の起動時および停止時にお
いても、その軸方向両側端面がハウジングに対してすべ
り接触することがなく、摩擦トルクが低くなるだけでな
く、スラスト軸受面とスラスト受面との摩耗が少なくな
るため、耐久性にすぐれた軸受装置が得られる。
Further, according to the present invention, since the rotating member is supported in the axial direction in a constantly floating state by the magnetic repulsion of the thrust magnetic bearing, even when the rotating member is started and stopped, both end faces in the axial direction Since there is no sliding contact with the housing, not only the friction torque is reduced, but also the wear between the thrust bearing surfaces and the thrust bearing surfaces is reduced, so that a bearing device with excellent durability can be obtained.

【図面の簡単な説明】[Brief explanation of drawings]

第1図はこの発明の実施例を示す縦断面図、第2図は従
来の軸受装置の一例を示す縦断面図である。 図中、20はハウジング、22は固定軸、23゜24は
ラジアル軸受面、23a、24aは動圧発生用のみぞ、
32は回転部材、33.34はラジアル受面、35はラ
ジアル軸受すき間、40はスラスト受、44はスラスト
受面、45はスラスト軸゛受、46はスラスト軸受面、
48はスラスト軸受すき間である。
FIG. 1 is a longitudinal sectional view showing an embodiment of the present invention, and FIG. 2 is a longitudinal sectional view showing an example of a conventional bearing device. In the figure, 20 is a housing, 22 is a fixed shaft, 23° and 24 are radial bearing surfaces, 23a and 24a are grooves for generating dynamic pressure,
32 is a rotating member, 33, 34 is a radial bearing surface, 35 is a radial bearing clearance, 40 is a thrust bearing, 44 is a thrust bearing surface, 45 is a thrust shaft bearing, 46 is a thrust bearing surface,
48 is a thrust bearing clearance.

Claims (6)

【特許請求の範囲】[Claims] (1)ハウジングに固定軸の軸方向の一端を固着し、固
定軸の固定端側を開口端とする回転部材を、固定軸の周
りにラジアル軸受すき間を介して回転可能に嵌装し、前
記ラジアル軸受すき間を介して対向する固定軸のラジア
ル軸受面と回転部材のラジアル受面との少なくとも一方
に動圧発生用のみぞ形成して、前記回転部材をラジアル
軸受すき間内の流体膜によって半径方向に支持する動圧
形のラジアル流体軸受を構成し、回転部材の開口端とは
反対側の軸方向端部とハウジングとに、それぞれ磁石か
らなるスラスト受とスラスト軸受とを対向させて取り付
け、スラスト受のスラスト受面側とスラスト軸受のスラ
スト軸受面側との磁極を同一磁極にして、前記回転部材
をスラスト受面とスラスト軸受面との間のスラスト軸受
すき間の磁気反発力によって軸方向に支持するスラスト
磁気軸受を構成したことを特徴とする軸受装置。
(1) One axial end of a fixed shaft is fixed to the housing, and a rotating member having an open end on the fixed end side of the fixed shaft is rotatably fitted around the fixed shaft through a radial bearing gap, and A groove for generating dynamic pressure is formed in at least one of the radial bearing surface of the fixed shaft and the radial bearing surface of the rotating member that face each other across the radial bearing gap, and the rotating member is moved in the radial direction by a fluid film within the radial bearing gap. A thrust bearing made of a magnet and a thrust bearing are installed facing each other at the axial end of the rotating member opposite to the open end and the housing, and the thrust bearing is supported by a dynamic pressure radial fluid bearing. The magnetic poles on the thrust bearing surface side of the bearing and the thrust bearing surface side of the thrust bearing are made the same magnetic pole, and the rotating member is supported in the axial direction by the magnetic repulsion force in the thrust bearing gap between the thrust bearing surface and the thrust bearing surface. A bearing device comprising a thrust magnetic bearing.
(2)固定軸の固定端とは反対側の軸方向端面と回転部
材のスラスト受との間の軸方向間隔が、回転部材の開口
端とハウジングとの間の軸方向間隔よりも大きく設定さ
れている特許請求の範囲第1項記載の軸受装置。
(2) The axial distance between the axial end surface of the fixed shaft opposite to the fixed end and the thrust receiver of the rotating member is set larger than the axial distance between the open end of the rotating member and the housing. A bearing device according to claim 1.
(3)回転部材に、半径方向の質量調整材接着用の凹部
を設けたリング部部材が取り付けられている特許請求の
範囲第1項または第2項記載の軸受装置。
(3) The bearing device according to claim 1 or 2, wherein a ring member provided with a recess for adhering a mass adjustment material in a radial direction is attached to the rotating member.
(4)固定軸と回転部材とが、それぞれ軸方向の2個所
にラジアル軸受面とラジアル受面とを有している特許請
求の範囲第1項ないし第3項のいずれかに記載の軸受装
置。
(4) The bearing device according to any one of claims 1 to 3, wherein the fixed shaft and the rotating member each have a radial bearing surface and a radial bearing surface at two locations in the axial direction. .
(5)回転部材のスラスト受とハウジングのスラスト軸
受とが、プラスチックを備えた磁性体の永久磁石である
特許請求の範囲第1項ないし第4項のいずれかに記載の
軸受装置。
(5) The bearing device according to any one of claims 1 to 4, wherein the thrust bearing of the rotating member and the thrust bearing of the housing are permanent magnets made of magnetic material made of plastic.
(6)回転部材のスラスト受が、外周側の金属製リング
と該金属製リングに一体に成形固着されたプラスチック
を備えた磁性体とを有する特許請求の範囲第5項記載の
軸受装置。
(6) The bearing device according to claim 5, wherein the thrust bearing of the rotating member includes a metal ring on the outer peripheral side and a magnetic body made of plastic integrally molded and fixed to the metal ring.
JP6956986A 1986-03-27 1986-03-27 Bearing device Pending JPS62228710A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP6956986A JPS62228710A (en) 1986-03-27 1986-03-27 Bearing device

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP6956986A JPS62228710A (en) 1986-03-27 1986-03-27 Bearing device

Publications (1)

Publication Number Publication Date
JPS62228710A true JPS62228710A (en) 1987-10-07

Family

ID=13406542

Family Applications (1)

Application Number Title Priority Date Filing Date
JP6956986A Pending JPS62228710A (en) 1986-03-27 1986-03-27 Bearing device

Country Status (1)

Country Link
JP (1) JPS62228710A (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH02101124U (en) * 1989-01-27 1990-08-13

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH02101124U (en) * 1989-01-27 1990-08-13

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