JPS59188351A - Dynamic pressure type bearing motor - Google Patents
Dynamic pressure type bearing motorInfo
- Publication number
- JPS59188351A JPS59188351A JP58061563A JP6156383A JPS59188351A JP S59188351 A JPS59188351 A JP S59188351A JP 58061563 A JP58061563 A JP 58061563A JP 6156383 A JP6156383 A JP 6156383A JP S59188351 A JPS59188351 A JP S59188351A
- Authority
- JP
- Japan
- Prior art keywords
- disc
- cylindrical member
- fluid
- shaft
- dynamic pressure
- 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
- 239000012530 fluid Substances 0.000 abstract description 21
- 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 abstract description 5
- 238000005086 pumping Methods 0.000 abstract description 2
- 238000005096 rolling process Methods 0.000 description 6
- 230000000694 effects Effects 0.000 description 3
- 239000004519 grease Substances 0.000 description 3
- 238000003754 machining Methods 0.000 description 3
- 239000000853 adhesive Substances 0.000 description 2
- 230000001070 adhesive effect Effects 0.000 description 2
- 230000007547 defect Effects 0.000 description 2
- 230000002950 deficient Effects 0.000 description 2
- 241000252203 Clupea harengus Species 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 235000019514 herring Nutrition 0.000 description 1
- 230000010365 information processing Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
Classifications
-
- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02K—DYNAMO-ELECTRIC MACHINES
- H02K5/00—Casings; Enclosures; Supports
- H02K5/04—Casings or enclosures characterised by the shape, form or construction thereof
- H02K5/16—Means for supporting bearings, e.g. insulating supports or means for fitting bearings in the bearing-shields
- H02K5/167—Means for supporting bearings, e.g. insulating supports or means for fitting bearings in the bearing-shields using sliding-contact or spherical cap bearings
- H02K5/1677—Means for supporting bearings, e.g. insulating supports or means for fitting bearings in the bearing-shields using sliding-contact or spherical cap bearings radially supporting the rotor around a fixed spindle; radially supporting the rotor directly
-
- 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
- F16C17/00—Sliding-contact bearings for exclusively rotary movement
- F16C17/10—Sliding-contact bearings for exclusively rotary movement for both radial and axial load
- F16C17/102—Sliding-contact bearings for exclusively rotary movement for both radial and axial load with grooves in the bearing surface to generate hydrodynamic pressure
- F16C17/107—Sliding-contact bearings for exclusively rotary movement for both radial and axial load with grooves in the bearing surface to generate hydrodynamic pressure with at least one surface for radial load and at least one surface for axial load
-
- 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
- F16C23/00—Bearings for exclusively rotary movement adjustable for aligning or positioning
- F16C23/02—Sliding-contact bearings
- F16C23/04—Sliding-contact bearings self-adjusting
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Power Engineering (AREA)
- Sliding-Contact Bearings (AREA)
- Motor Or Generator Frames (AREA)
- Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
Abstract
Description
【発明の詳細な説明】 本発明は、動圧型軸受モータに関する。[Detailed description of the invention] The present invention relates to a hydrodynamic bearing motor.
最近、コンピューターのメモリ・ディスク用モータ、ビ
デオ令ディスク回転駆動用モーク、ＶＴＲの磁気ヘッド
回転用のモータ等として、情ｆｕ処理機器や映像機器な
どに精密で、高信頼性、高速性を持つモータが要求され
ている。一般的にこれらのモータの軸受の多くは、ポー
ル・ベアリングなどのころがり軸受が用いられているが
、この種のころがり軸受は摩擦抵抗の小さいことやコス
トの安いこと等の長所はあるが、高速性、騒音、振動、
回転軸の振れ等について、難点を持つている。Recently, precise, highly reliable, and high-speed motors have been used in information processing equipment and video equipment, such as motors for computer memory disks, motors for video disk rotation drive, motors for rotating magnetic heads of VTRs, etc. is required. Generally, many of the bearings used in these motors are rolling bearings such as pole bearings. Although these types of rolling bearings have advantages such as low frictional resistance and low cost, noise, vibration,
There are some drawbacks such as vibration of the rotating shaft.
近年、ころがり軸受に代って動圧型の軸受が注目されて
いる。動圧型軸受装置とは、軸を軸受部こ対して数μ程
度の微小な間隔をおいて配置し、この間隔に空気、オイ
ル、グリース等の流体を配置し、軸又は軸受が回転する
と、この微小な間隔内の流体が動圧を発生し、この動圧
により回転部（軸又は軸受）を支持する万代のものであ
る。一般的に動圧をより安定にかつ強く発生させるため
に、軸または軸受に螺旋状の極く浅い溝を設けている。In recent years, dynamic pressure bearings have been attracting attention as an alternative to rolling bearings. A hydrodynamic bearing device is a bearing device in which a shaft is placed against a bearing part with a very small gap of several micrometers, and a fluid such as air, oil, or grease is placed in this gap, and when the shaft or bearing rotates, this Fluid within a minute interval generates dynamic pressure, and this dynamic pressure supports the rotating part (shaft or bearing). Generally, in order to generate dynamic pressure more stably and strongly, a very shallow spiral groove is provided on the shaft or bearing.
第１図には、一般的な動圧型の軸受モータとして、ラジ
アル軸受部及びスラスト軸受部におし１て双方共、動圧
を利用した磁気ディスク駆動用のモータが示されている
。軸１の外側面１ａの上部及び下部には、それぞれへリ
ングポーンと呼ばれる非常に浅い矢はず状の溝Ｇｌ及び
Ｇ２が設けられ、更に軸１下方のやや大きい円形のフラ
ンジ部１ｃの上端面１ｄ（すなわち軸１と直角方向の面
）には、第２図に示すような螺旋状の極めて浅い溝０３
が設けられている。溝Ｇ、、ＧＺ 、Ｇ３には、空気、
オイル、グリース等の流体が配置されている。軸１は、
その軸方向の下端において基台２の中心部に固定され、
基台２の内側の面には複数個のコイル６が固定されてい
る。一方、円筒形の部材３は、その内側面３ａが軸１の
外側面１ａと数μ程度の間隔をおいて、軸１に嵌合して
おり、部材３の外側の面にはロータマグネット５が固定
され、更に軸方向の上端部には、ディスク４が固定され
、下端部には、半径方向に円形の下部端面３ｂを有する
突出部３ｃが設けられている。すなわち、軸１の溝Ｇ□
、Ｇ２と円筒部材３の内側面３ａとにより動圧型のラジ
アル軸受装置が構成され、軸１の溝Ｇ３と円筒部材３の
下部端面３ｂとにより、動圧型のスラスト軸受装置が構
成される。なお、モータの静止時には、円筒部材３（デ
ィスク４、マグネット５と共に）は、円筒部材３の下部
端面３ｂと軸１の７ラング部１ｃの上端面１ｂが接触す
るように、載置されている。このモータにおいて、コイ
ル６は電流が流れると交番磁界を発生し、円筒部材３、
ディスク４、マグネット５は共に回転する。従って溝Ｇ
□、Ｇ２によるポンプ作用により円筒部材３の内側面３
ａと軸１の外側面１ａとの間隔部の流体は高い圧力を発
生し、回転する円筒部材３は、ラジアル方向に支持され
る。−・方、溝Ｇ３のポンプ作用により円筒部材３の下
部端面３ｂと軸１のフランジ部１ｃの上端面１ｂとの間
隔部の流体も同様に高い圧力を発生して、円筒部材３は
浮き上り、軸方向に支持される。FIG. 1 shows a motor for driving a magnetic disk, which uses dynamic pressure in both a radial bearing portion and a thrust bearing portion, as a general dynamic pressure type bearing motor. Very shallow arrow-shaped grooves Gl and G2 called herring pawns are provided in the upper and lower parts of the outer surface 1a of the shaft 1, respectively, and the upper end surface 1d of a slightly larger circular flange portion 1c below the shaft 1. (that is, the surface perpendicular to the axis 1) has a spiral extremely shallow groove 03 as shown in FIG.
is provided. Grooves G, GZ, and G3 contain air,
A fluid such as oil or grease is placed there. Axis 1 is
fixed to the center of the base 2 at its lower end in the axial direction,
A plurality of coils 6 are fixed to the inner surface of the base 2. On the other hand, the cylindrical member 3 is fitted onto the shaft 1 with its inner surface 3a spaced from the outer surface 1a of the shaft 1 by a distance of approximately several micrometers, and the outer surface of the member 3 is fitted with a rotor magnet 5. Further, a disk 4 is fixed to the upper end in the axial direction, and a protrusion 3c having a circular lower end surface 3b in the radial direction is provided at the lower end. That is, the groove G□ of shaft 1
, G2 and the inner surface 3a of the cylindrical member 3 constitute a dynamic pressure type radial bearing device, and the groove G3 of the shaft 1 and the lower end surface 3b of the cylindrical member 3 constitute a dynamic pressure type thrust bearing device. Note that when the motor is at rest, the cylindrical member 3 (together with the disk 4 and the magnet 5) is placed such that the lower end surface 3b of the cylindrical member 3 and the upper end surface 1b of the seven rungs 1c of the shaft 1 are in contact with each other. . In this motor, the coil 6 generates an alternating magnetic field when current flows, and the cylindrical member 3,
The disk 4 and magnet 5 rotate together. Therefore, the groove G
□, the inner surface 3 of the cylindrical member 3 due to the pump action by G2
The fluid in the space between a and the outer surface 1a of the shaft 1 generates high pressure, and the rotating cylindrical member 3 is supported in the radial direction. - On the other hand, due to the pumping action of the groove G3, the fluid in the space between the lower end surface 3b of the cylindrical member 3 and the upper end surface 1b of the flange portion 1c of the shaft 1 similarly generates high pressure, and the cylindrical member 3 floats up. , axially supported.
この場合、円筒部材３の下部端面３ｂと軸ｌのフランジ
部の上端面１ｂの間隔部は、数賜程度に保持される。以
上のような構成から従来の動圧型の軸受モータにおいて
は、軸ｌと各軸受部との間隔は数−程度であるので、ラ
ジアル軸受部の内側面３ａとスラスト軸受部の１部端面
３ｂ、及び軸ｌの外側面１ａと上端面１ｂとの直角度を
かなり高精度に加工しなければならず、製作コストが高
くなる。一般的に、上記の間隔量が数μ程度である場合
には、直角度の精度は１−以下にしなければならない。In this case, the distance between the lower end surface 3b of the cylindrical member 3 and the upper end surface 1b of the flange portion of the shaft l is maintained at a distance of about a few degrees. From the above-described structure, in the conventional hydrodynamic bearing motor, the distance between the shaft l and each bearing part is about a few inches, so the inner surface 3a of the radial bearing part, the end face 3b of one part of the thrust bearing part, Also, the perpendicularity between the outer surface 1a and the upper end surface 1b of the shaft l must be machined with considerably high precision, which increases the manufacturing cost. Generally, when the above-mentioned spacing is on the order of several microns, the accuracy of the squareness must be 1- or less.
第３図及び第４図は、それぞれ軸１の外側面１ａとフラ
ンジ部１ｃの上端面１ｂとの直角度が不良の場合、及び
円筒部材３の下部端面３ｂと内側面３ａとの直角度が不
良の場合の軸と軸受部の縦断面図である。このいずれの
場合にも、フランジ部１ｃの上端面１ｂと円筒部材３の
下部端面３ｂとは平行でなくなるため、それぞれ上端面
１ｂと回転する円筒部材３の下部端面３ｂとの間隔部の
流体の圧力は不均一となる。この圧力は１間隔部が小さ
いほど大きくなる。従って下部端面３ｂの各部分が受け
る流体の圧力は、円筒部材３の回転に従って周期的に変
化する。すなわちこの圧力の変化により、円筒部材３を
支持する力が不均一に変化し、モータが振動したり、回
転体３．４．５が揺れたれする欠点がある。実際の場合
には、第３図すなわち軸１の加工不良、及び第４図すな
わち円筒部材３の加工不良が共存しており、モータの複
雑な振動の原因となっている。3 and 4 show cases in which the perpendicularity between the outer surface 1a of the shaft 1 and the upper end surface 1b of the flange portion 1c is poor, and the perpendicularity between the lower end surface 3b and the inner surface 3a of the cylindrical member 3, respectively. FIG. 6 is a longitudinal cross-sectional view of the shaft and bearing portion in the case of a defect. In any of these cases, the upper end surface 1b of the flange portion 1c and the lower end surface 3b of the cylindrical member 3 are no longer parallel, so that the fluid in the space between the upper end surface 1b and the lower end surface 3b of the rotating cylindrical member 3 is not parallel to each other. The pressure becomes uneven. This pressure increases as the interval becomes smaller. Therefore, the pressure of the fluid that each portion of the lower end surface 3b receives changes periodically as the cylindrical member 3 rotates. That is, due to this change in pressure, the force supporting the cylindrical member 3 changes non-uniformly, resulting in the disadvantage that the motor vibrates and the rotating body 3.4.5 shakes. In actual cases, the defective machining of the shaft 1 shown in FIG. 3 and the defective machining of the cylindrical member 3 shown in FIG. 4 coexist, causing complex vibrations of the motor.
本発明は、上記従来例の欠点に鑑み、回転中は回転部と
軸受部との角度を一定に維持するようにした動圧型軸受
モータを提供することにある。SUMMARY OF THE INVENTION In view of the above-mentioned drawbacks of the conventional example, an object of the present invention is to provide a hydrodynamic bearing motor in which the angle between the rotating part and the bearing part is maintained constant during rotation.
以下、図面を参照して本発明の一実施例を説明する。第
５図は、本発明の一実施例の縦断面図である。尚、図に
おいて、第１図の部材と同一の部材には同一の符号を賄
す。Hereinafter, one embodiment of the present invention will be described with reference to the drawings. FIG. 5 is a longitudinal sectional view of one embodiment of the present invention. In the drawings, the same members as those in FIG. 1 are designated by the same reference numerals.
軸ｌＯの軸方向の下部には、軸１０の直径より大きく、
かつ軸方向に両端部から中央部に向けて直径が漸増する
球状部１０ｒが形成されている。球状部１０ｒには、半
径方向に円環状の板７が滑らかに嵌合して係止されてお
り、この円板７の軸１に対する角度は任意に変えること
ができる構成になっている。軸１０の下端部は、基台２
の内側の底の中央孔に嵌合、固定されている。円板７の
上面７ａには、第２図と同様な螺旋状の溝Ｇ３が形成さ
れ、軸１０の外側面１０ａの上部及び下部には、第１図
と同様に、それぞれへリングボーンと呼ばれる非常に浅
い溝Ｇ□及びＧ２が形成され、溝Ｇ１、Ｇ２、Ｇ３には
、空気、オイル、グリース等の流体が配置されている。At the lower part of the axis lO in the axial direction, there is a diameter larger than the diameter of the axis 10,
A spherical portion 10r is formed whose diameter gradually increases in the axial direction from both ends toward the center. A circular plate 7 is smoothly fitted and locked in the radial direction of the spherical portion 10r, and the angle of the circular plate 7 with respect to the axis 1 can be changed as desired. The lower end of the shaft 10 is connected to the base 2
It fits into the center hole on the inside bottom and is fixed. A spiral groove G3 similar to that shown in FIG. 2 is formed on the upper surface 7a of the disk 7, and a herringbone called a herringbone is formed on the upper and lower portions of the outer surface 10a of the shaft 10, respectively, as in FIG. Very shallow grooves G□ and G2 are formed, and fluids such as air, oil, and grease are placed in the grooves G1, G2, and G3.
円筒形の部材３は、その内側面３ａが軸ｌＯの外側面１
０ａと数μ程度の間隔をおいて、ＷＢｌＯに嵌合してお
り、また軸方向の上端部には、ディスク４が固定され、
下端部には、半径方向に円環状の下部端面３ｂを有する
突出部３ｃが形成されている。すなわち、軸１の溝Ｇ１
、Ｇ２（及び流体）と円筒部材３の内側面３ａとにより
動圧型のラジアル軸受装置が構成され、円板７の溝０３
（及び流体）と円筒部材３の下部端面３ｃとにより動
圧型のスラスト軸受装置が構成Ｓれる。The cylindrical member 3 has an inner surface 3a aligned with the outer surface 1 of the axis lO.
The disk 4 is fitted into the WBLO with an interval of several μ from 0a, and a disk 4 is fixed to the upper end in the axial direction.
A protrusion 3c having a radially annular lower end surface 3b is formed at the lower end. That is, the groove G1 of the shaft 1
, G2 (and fluid) and the inner surface 3a of the cylindrical member 3 constitute a dynamic pressure type radial bearing device.
(and the fluid) and the lower end surface 3c of the cylindrical member 3 constitute a dynamic pressure type thrust bearing device S.
５は、ローフマグ２ツト、６は、コイルである。5 is two loaf mugs, and 6 is a coil.
」二足実施例の作動を説明すると、コイル６は、電流が
流れると交番磁界を発生し、円筒部材３、ディスク４、
マグネット５は、共に回転する。” To explain the operation of the two-legged embodiment, the coil 6 generates an alternating magnetic field when a current flows, and the cylindrical member 3, the disk 4,
The magnet 5 rotates together.
溝０３のポンプ作用により、円筒部材３の下部端面３ｂ
と円板７の上面７ａと間の間隙部の流体は、高い圧力を
発生して、円筒部材７は円板７に対して浮き上り、軸方
向に支持される。ここで加工不良等により、円筒部材３
の内側面３ａと下端面３ｂとが完全な直角でない場合、
下部端面３ｂと内板７の上面７ａの間の流体は不均一な
圧力を発生する。この不均一な圧力は、間隙部材が小さ
いほど大きく、間隙部が大きいほど小さい。従って間隙
部の小さい部分における円板７の当該部分は、より大き
な圧力により円筒部材３の下部端面３ｂとの距離が大き
くなり、一方、間隙部の大きい部分における円板７の当
該部分は、より小さな圧力により下部端面３ｂとの距離
が小さくなる。このように時間の経過に従い、流体の圧
力が全ての間隙部において均一になるように、円板７が
軸ｌに対して角度を変え、円板７の上面７ａと円筒部材
３の下部端面３ｂとが全ての領域において平行となる。Due to the pump action of the groove 03, the lower end surface 3b of the cylindrical member 3
The fluid in the gap between the upper surface 7a of the disc 7 generates high pressure, and the cylindrical member 7 floats up relative to the disc 7 and is supported in the axial direction. Here, due to processing defects etc., the cylindrical member 3
If the inner surface 3a and the lower end surface 3b are not at a perfect right angle,
The fluid between the lower end surface 3b and the upper surface 7a of the inner plate 7 generates non-uniform pressure. This non-uniform pressure increases as the gap member becomes smaller, and decreases as the gap becomes larger. Therefore, the distance between the part of the disc 7 in the small gap part and the lower end surface 3b of the cylindrical member 3 becomes larger due to the larger pressure, while the part of the disc 7 in the large gap part becomes more distant from the lower end surface 3b of the cylindrical member 3 due to the larger pressure The distance from the lower end surface 3b becomes smaller due to the smaller pressure. In this way, as time passes, the angle of the disk 7 changes with respect to the axis l so that the pressure of the fluid becomes uniform in all the gaps, and the upper surface 7a of the disk 7 and the lower end surface 3b of the cylindrical member 3 are parallel in all regions.
このように加工精度が悪くとも、流体の平衡作用により
、振動や揺れのない安定した動圧型軸受モータを実現す
ることかでさる。Even if the machining accuracy is poor, it is still possible to create a stable hydrodynamic bearing motor that does not vibrate or shake due to the fluid's equilibrium effect.
上記の実施例において、流体の平衡作用を受ける円板は
、軸に対し移動可能に係止されている、が、基台に係止
しても同様の効果が得られる。第６図において、円環状
の板７１は、その外周部を円環状の板バネ８の内周部に
固定され、更に板バネ８の外周部は基台２の内側面に固
定されている。In the embodiments described above, the disc subjected to the fluid balancing action is movably locked to the shaft, but the same effect can be obtained even if it is locked to the base. In FIG. 6, an annular plate 71 has its outer circumference fixed to the inner circumference of an annular plate spring 8, and the outer circumference of the plate spring 8 is further fixed to the inner surface of the base 2. As shown in FIG.
このような構成により、板バネ８は流体の平衡作用によ
り弾性変形し、従って円板７１は角度を変え、その上面
７１ａと円筒部材３の下部端面３ｂは平行になる。第７
図は、円環状の板７２を基部２の底部に係止した場合を
示す。すなわち円板７２の下面は、ゴム等の弾性部材９
の上面に接着剤等により固定され、更に弾性部材９の下
面は、基台２の内底面に接着剤等により固定されている
。従って、円板７２の上面７２ａと円筒部材３の下部端
面３ｂとの間の流体の平衡作用により、弾性部材９は弾
性変形し、円板７２は角度を変え、上面？２ａ と下部
端面３ｂとは全ての領域において平行になる。With such a configuration, the leaf spring 8 is elastically deformed by the equilibrium action of the fluid, so that the disk 71 changes its angle so that its upper surface 71a and the lower end surface 3b of the cylindrical member 3 become parallel. 7th
The figure shows a case where an annular plate 72 is locked to the bottom of the base 2. That is, the lower surface of the disc 72 is made of an elastic member 9 such as rubber.
The elastic member 9 is fixed to the upper surface with an adhesive or the like, and the lower surface of the elastic member 9 is fixed to the inner bottom surface of the base 2 with an adhesive or the like. Therefore, due to the equilibrium action of the fluid between the upper surface 72a of the disk 72 and the lower end surface 3b of the cylindrical member 3, the elastic member 9 is elastically deformed, the disk 72 changes its angle, and the upper surface? 2a and the lower end surface 3b are parallel to each other in all regions.
」二記第５図、第６図及び第７図の実施例において、動
圧型のラジアル軸受装置として、軸１０、及び１２に溝
Ｇ１、Ｇ２がされているが、従来のころがり軸受を用い
てもよく、すなわちラジアルころがり軸受と動圧型のス
ラスト軸受の組み合わせのモータにも、本発明を適用−
することが可能である。In the embodiments shown in Figures 5, 6, and 7, grooves G1 and G2 are formed on the shafts 10 and 12 as a dynamic pressure type radial bearing device, but it is not possible to use conventional rolling bearings. In other words, the present invention can also be applied to motors with a combination of radial rolling bearings and hydrodynamic thrust bearings.
It is possible to do so.
一方、動圧型のラジアル軸受装置を用いたモータにも本
発明を適用することは可能である。すなわち第８図に示
すように、円環状の板７３は、基台２の内底面に固定さ
れ、軸１３の下端部は、弾性部材９０を介して基台２の
底部に支持されている。この場合、軸１３の外側面１３
ａと円筒部材３の内側面３ａとの間の流体の平衡作用に
より、軸１３は軸方向に傾斜する。尚、図において動圧
型のスラスト軸受装置として円板７３に溝Ｇ３がされて
いるが、従来のころがり軸受の場合にも同様の効果があ
る。On the other hand, the present invention can also be applied to a motor using a dynamic pressure type radial bearing device. That is, as shown in FIG. 8, the annular plate 73 is fixed to the inner bottom surface of the base 2, and the lower end of the shaft 13 is supported by the bottom of the base 2 via the elastic member 90. In this case, the outer surface 13 of the shaft 13
The shaft 13 is tilted in the axial direction due to the fluid balancing action between a and the inner surface 3a of the cylindrical member 3. In the figure, a groove G3 is formed in the disk 73 as a dynamic pressure type thrust bearing device, but the same effect can be obtained in the case of a conventional rolling bearing.
以上説明したように、回転部と軸受部の角度を回転中は
一定に維持し得る構成にしたので、安価な、また振動や
揺れのない安定した動圧型軸受モータを実現することが
できる効果がある。As explained above, since the angle between the rotating part and the bearing part can be maintained constant during rotation, it is possible to realize an inexpensive hydrodynamic bearing motor that is stable without vibration or shaking. be.
第１図は、従来の動圧型軸受モータの縦断面図、第２図
は、８１図のフランジ部の上面図、第３図及び第４図は
、第１図の軸及び軸受部の縦断面図、第５図は、本発明
の一実施例の縦断面図、第６図、第７図及び第８図は、
それぞれ本発明の他の実施例の縦断面図である。
１．１０．１１．１２．１３・・・軸、 ３・・
・円筒部材、７．７１．７２．７３・・・円板、
８・・・へネ９．９０・・・弾性部材、１０ｒ・・・
球状部。
第１図 １゜
／
１
２７６−
第５図
第６図Fig. 1 is a longitudinal cross-sectional view of a conventional hydrodynamic bearing motor, Fig. 2 is a top view of the flange portion of Fig. 81, and Figs. 3 and 4 are longitudinal cross-sections of the shaft and bearing portion of Fig. 1. 5 is a longitudinal sectional view of one embodiment of the present invention, and FIGS. 6, 7, and 8 are
FIG. 6 is a vertical cross-sectional view of another embodiment of the present invention, respectively. 1.10.11.12.13...axis, 3...
・Cylindrical member, 7.71.72.73...disc,
8... Hene 9.90... Elastic member, 10r...
Globular part. Figure 1 1°/ 1 276- Figure 5 Figure 6
Claims (1)
有する動圧型のモータであって、該軸受部が該回転部に
対し遊動可能である手段を設けたことを特徴とする動圧
型軸受モータ。1. A dynamic pressure type bearing motor having a bearing part that supports a rotating part by dynamic pressure generated by rotation, characterized in that the bearing part is provided with means that allows the bearing part to freely move with respect to the rotating part.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP58061563A JPS59188351A (en) | 1983-04-09 | 1983-04-09 | Dynamic pressure type bearing motor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP58061563A JPS59188351A (en) | 1983-04-09 | 1983-04-09 | Dynamic pressure type bearing motor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS59188351A true JPS59188351A (en) | 1984-10-25 |
Family
ID=13174703
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP58061563A Pending JPS59188351A (en) | 1983-04-09 | 1983-04-09 | Dynamic pressure type bearing motor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS59188351A (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6445029U (en) * | 1987-09-12 | 1989-03-17 | ||
| JPH0186454U (en) * | 1987-11-25 | 1989-06-08 | ||
| US4984480A (en) * | 1989-12-14 | 1991-01-15 | Carrier Corporation | Rolling rotor motor balancing means |
| US5332237A (en) * | 1990-07-26 | 1994-07-26 | Taiho Kogyo Co., Ltd. | Metal gasket with welded shim |
| US9885418B2 (en) | 2014-08-07 | 2018-02-06 | Nok Corporation | Metal gasket |
-
1983
- 1983-04-09 JP JP58061563A patent/JPS59188351A/en active Pending
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6445029U (en) * | 1987-09-12 | 1989-03-17 | ||
| JPH0518489Y2 (en) * | 1987-09-12 | 1993-05-17 | ||
| JPH0186454U (en) * | 1987-11-25 | 1989-06-08 | ||
| US4984480A (en) * | 1989-12-14 | 1991-01-15 | Carrier Corporation | Rolling rotor motor balancing means |
| US5332237A (en) * | 1990-07-26 | 1994-07-26 | Taiho Kogyo Co., Ltd. | Metal gasket with welded shim |
| US5385354A (en) * | 1990-07-26 | 1995-01-31 | Taiho Kogyo Co., Ltd. | Metal gasket |
| US5393076A (en) * | 1990-07-26 | 1995-02-28 | Taiho Kogyo Co., Ltd. | Metal gasket with base plate having coatings of diverse thicknesses |
| US5472217A (en) * | 1990-07-26 | 1995-12-05 | Taiho Kogyo Co., Ltd. | Metal gasket |
| US9885418B2 (en) | 2014-08-07 | 2018-02-06 | Nok Corporation | Metal gasket |
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