JP2003092867A - Dynamic pressure bearing spindle motor - Google Patents
Dynamic pressure bearing spindle motorInfo
- Publication number
- JP2003092867A JP2003092867A JP2001286294A JP2001286294A JP2003092867A JP 2003092867 A JP2003092867 A JP 2003092867A JP 2001286294 A JP2001286294 A JP 2001286294A JP 2001286294 A JP2001286294 A JP 2001286294A JP 2003092867 A JP2003092867 A JP 2003092867A
- Authority
- JP
- Japan
- Prior art keywords
- dynamic pressure
- thrust
- sleeve
- gap
- pressure 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.)
- Granted
Links
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
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/02—Parts of sliding-contact bearings
- F16C33/04—Brasses; Bushes; Linings
- F16C33/06—Sliding surface mainly made of metal
- F16C33/10—Construction relative to lubrication
- F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
- F16C33/106—Details of distribution or circulation inside the bearings, e.g. details of the bearing surfaces to affect flow or pressure of the liquid
- F16C33/107—Grooves for generating pressure
-
- 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
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、ラジアル動圧軸受
部と上下一対のスラスト動圧軸受部とを有する流体動圧
軸受によってロータがステータに支持された動圧軸受ス
ピンドルモータに関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a dynamic pressure bearing spindle motor in which a rotor is supported by a stator by a fluid dynamic pressure bearing having a radial dynamic pressure bearing portion and a pair of upper and lower thrust dynamic pressure bearing portions.
【０００２】[0002]
【従来の技術】図４は、軸受隙間を含む微小隙間を誇張
して示した従来の動圧軸受スピンドルモータ（第１従来
例）の縦断面図である。このスピンドルモータは、Ｔ字
型流体動圧軸受によって、ロータマグネット７を含むロ
ータがステータコイル８を含むステータに回転自在に支
持されたものである。ロータマグネット７は、ロータフ
レーム６の円筒部６ａの内周面に取り付けられている。
ロータフレーム６は、カップ状ハブとしても機能するも
のである。ロータフレーム６は、その円周方向中心部に
設けられた嵌合穴を、回転軸であるフランジ付シャフト
１のシャフト２の上端部に圧入し、回転軸に固定されて
いる。ステータコイル８は、ベース基板９に立設された
段付スリーブ４の外周面に取りつけられている。2. Description of the Related Art FIG. 4 is a vertical cross-sectional view of a conventional dynamic pressure bearing spindle motor (first conventional example) in which a minute clearance including a bearing clearance is exaggerated. In this spindle motor, a rotor including a rotor magnet 7 is rotatably supported by a stator including a stator coil 8 by a T-shaped fluid dynamic bearing. The rotor magnet 7 is attached to the inner peripheral surface of the cylindrical portion 6 a of the rotor frame 6.
The rotor frame 6 also functions as a cup-shaped hub. The rotor frame 6 is fixed to the rotary shaft by press-fitting a fitting hole provided in the center portion in the circumferential direction into the upper end portion of the shaft 2 of the shaft with flange 1 that is the rotary shaft. The stator coil 8 is attached to the outer peripheral surface of the stepped sleeve 4 provided upright on the base substrate 9.
【０００３】前記動圧軸受は、シャフト２にリング状フ
ランジ３が圧入されて形成されたフランジ付シャフト１
と、このフランジ付シャフト１が回転自在にして嵌合す
る段付円筒状スリーブ４と、スラスト押さえ部材５とか
ら構成されている。これらの軸受構成部材間に形成され
た微小隙間ｒ１、ｒ２、ｒ３、ｒ４、ｒ５及びｒ６には
潤滑油が充填されている。シャフト部材２の上側の外周
面とスラスト押え部材５の内周面との間に形成されたテ
ーパー状微小隙間Ｓは、毛細管現象と表面張力を利用し
て潤滑油が外部に漏出しないように機能するキャピラリ
ーシールである。The dynamic pressure bearing has a flanged shaft 1 formed by press-fitting a ring-shaped flange 3 into a shaft 2.
And a stepped cylindrical sleeve 4 into which the flanged shaft 1 is rotatably fitted, and a thrust pressing member 5. Lubricating oil is filled in the minute gaps r1, r2, r3, r4, r5, and r6 formed between these bearing constituent members. The tapered minute gap S formed between the outer peripheral surface on the upper side of the shaft member 2 and the inner peripheral surface of the thrust pressing member 5 functions to prevent the lubricating oil from leaking to the outside by utilizing the capillary phenomenon and the surface tension. It is a capillary seal that does.
【０００４】ラジアル軸受隙間ｒ５を形成するシャフト
部材２の下側の外周面にはヘリングボーン溝の如きラジ
アル動圧発生溝Ｇ１のパターンが形成され、また段付円
筒状スリーブ４の小径円筒部の内周面は平坦面とされて
いる。A pattern of a radial dynamic pressure generating groove G1 such as a herringbone groove is formed on the outer peripheral surface of the lower side of the shaft member 2 which forms the radial bearing gap r5, and a small diameter cylindrical portion of the stepped cylindrical sleeve 4 is formed. The inner peripheral surface is flat.
【０００５】スラスト軸受隙間は、リング状フランジ３
の上面とスラスト押え部材５の下面とで形成する第１の
スラスト軸受隙間ｒ２と、リング状フランジ３の下面と
段付円筒状スリーブ４の大径円筒部の底面とで形成する
第２のスラスト軸受隙間ｒ４の２つである。リング状フ
ランジ３の上面と下面には、図５に示す如きスラスト動
圧発生溝Ｇ２が形成されている。The thrust bearing gap is defined by the ring-shaped flange 3
A first thrust bearing gap r2 formed by the upper surface of the ring and the lower surface of the thrust pressing member 5, and a second thrust formed by the lower surface of the ring-shaped flange 3 and the bottom surface of the large-diameter cylindrical portion of the stepped cylindrical sleeve 4. Two bearing gaps r4. A thrust dynamic pressure generating groove G2 as shown in FIG. 5 is formed on the upper surface and the lower surface of the ring-shaped flange 3.
【０００６】図４の流体動圧スピンドルモータは実用的
なものであるが、上下のスラスト軸受部の間隔が短いた
めに回転軸線の方向や位置のぶれがあるという問題を有
する。この問題を解決した流体動圧スピンドルモータ
（第２従来例）が、特開平８−１３０８５２号公報に開
示されている。Although the fluid dynamic pressure spindle motor shown in FIG. 4 is practical, it has a problem in that there is a deviation in the direction or position of the rotation axis due to the short distance between the upper and lower thrust bearing portions. A fluid dynamic pressure spindle motor (second conventional example) that solves this problem is disclosed in Japanese Patent Application Laid-Open No. 8-130852.
【０００７】即ち、図３はＨ字型流体動圧軸受を備えた
第２従来例の流体動圧スピンドルモータの縦断面図であ
る。このスピンドルモータは、流体動圧軸受によって、
ロータマグネット３２を含むロータがステータコイル２
４を含むステータに回転自在に支持されたものである。
ロータマグネット３２は、ロータフレーム３６の円筒部
３６ｄの内周面に取り付けられている。ロータフレーム
３６は、カップ状ハブとしても機能するものである。ス
テータコイル２４は、ベース基板３９に立設された固定
スリーブ体１２の外周面に取りつけられている。That is, FIG. 3 is a longitudinal sectional view of a second conventional fluid dynamic pressure spindle motor having an H-shaped fluid dynamic pressure bearing. This spindle motor uses a fluid dynamic bearing to
The rotor including the rotor magnet 32 is the stator coil 2
It is rotatably supported by a stator including the four.
The rotor magnet 32 is attached to the inner peripheral surface of the cylindrical portion 36d of the rotor frame 36. The rotor frame 36 also functions as a cup-shaped hub. The stator coil 24 is attached to the outer peripheral surface of the fixed sleeve body 12 provided upright on the base substrate 39.
【０００８】回転シャフト体１６は、シャフト部１６ａ
の上下に上フランジ部１６ｂと下フランジ部１６ｄが設
けられたＨ字型断面のフランジ付シャフトである。ラジ
アル動圧軸受部はシャフト部１６ａに対し潤滑剤を介し
て固定スリーブ体１２のスリーブ部１２ａを外嵌して構
成されている。なお、ラジアル動圧発生溝Ｇ１は、シャ
フト部１６ａの外周面に形成されている。The rotary shaft body 16 has a shaft portion 16a.
It is a shaft with a flange having an H-shaped cross section in which an upper flange portion 16b and a lower flange portion 16d are provided above and below. The radial dynamic pressure bearing portion is formed by externally fitting the sleeve portion 12a of the fixed sleeve body 12 to the shaft portion 16a via a lubricant. The radial dynamic pressure generating groove G1 is formed on the outer peripheral surface of the shaft portion 16a.
【０００９】上スラスト動圧軸受部は、上フランジ部１
６ｂの下側面に対し潤滑剤を介して固定スリーブ体１２
の上環状部を相対させて構成されている。また、下スラ
スト動圧軸受部は、下フランジ部１６ｄの上側面に対し
潤滑剤を介して固定スリーブ体１２の上環状部を相対さ
せて構成されている。なお、スラスト動圧発生溝Ｇ２
は、上フランジ部１６ｂの下側面と、下フランジ部１６
ｄの上側面に夫々形成されている。The upper thrust dynamic pressure bearing portion is the upper flange portion 1.
A fixed sleeve body 12 is formed on the lower surface of 6b through a lubricant.
The upper annular portion is made to face each other. Further, the lower thrust dynamic pressure bearing portion is configured such that the upper annular portion of the fixed sleeve body 12 is opposed to the upper side surface of the lower flange portion 16d via a lubricant. The thrust dynamic pressure generating groove G2
Is a lower side surface of the upper flange portion 16b and the lower flange portion 16b.
They are respectively formed on the upper side surface of d.
【００１０】そして、回転シャフト体１６の突出部１６
ｃに外嵌したロータフレーム３６の内周面は、上フラン
ジ部１６ｂの上側面とキャップ部材３８との間に挟圧固
定されている。The protruding portion 16 of the rotary shaft body 16
The inner peripheral surface of the rotor frame 36 fitted on the outer peripheral surface c is clamped and fixed between the upper side surface of the upper flange portion 16b and the cap member 38.
【００１１】上述の如く構成されたＨ字型流体動圧軸受
を備えた第２従来例の流体動圧スピンドルモータでは、
回転シャフト体の回転軸線の方向や位置のぶれが防止さ
れ、高い回転精度が実現できる。また、回転シャフト体
１６の突出部１６ｃに外嵌したロータフレーム３６の内
周部は、上フランジ部１６ｂの上側面とキャップ部材３
８との間に挟圧固定されているので、ロータフレーム３
６の内周面の軸線方向長さが圧入による固定の場合に比
し短くて足りると共に、上フランジ部１６ｂをロータフ
レーム３６の固定にも利用できるものであるため、全体
として、スピンドルモータの軸線方向長さの短縮、即ち
薄型化に有効性が高いと記載されている。In the fluid dynamic pressure spindle motor of the second conventional example having the H-shaped fluid dynamic pressure bearing configured as described above,
It is possible to prevent deviation of the direction and position of the rotation axis of the rotary shaft body, and to realize high rotation accuracy. Further, the inner peripheral portion of the rotor frame 36 fitted onto the projecting portion 16c of the rotary shaft body 16 has an upper side surface of the upper flange portion 16b and the cap member 3.
Since it is clamped and fixed between the rotor frame 3 and
Since the axial length of the inner peripheral surface of 6 is shorter than that in the case of fixing by press fitting, and the upper flange portion 16b can be used for fixing the rotor frame 36, the axis line of the spindle motor as a whole. It is described that it is highly effective in shortening the direction length, that is, reducing the thickness.
【００１２】このような数々の特長を有するが、第２従
来例の流体動圧スピンドルモータには次のような問題点
もある。先ず、回転シャフト体１６の突出部１６ｃへの
キャップ部材３８を圧入によって、上フランジ部１６ｂ
の内周部に大きな応力が加わり、上フランジ部１６ｂの
変形が発生することである。上フランジ部１６ｂが変形
すると、ＲＲＯもＮＲＲＯも悪くなるという問題があ
る。次に、下フランジ部１６ｄは、その嵌合突部１６ｅ
をシャフト部１６ａの下方に開口する嵌合穴１６ａ１に
圧入してシャフト部１６ａに固着されるものであるが、
圧入によってシャフト部１６ａの下部が膨らむことであ
る。シャフト部１６ａの下部が膨らむと、ラジアル動圧
軸受部でかじり現象が起こり、シャフトが回らなくなる
という問題がある。更に、第１従来例の流体動圧スピン
ドルモータに比べて部品点数が多く、しかも個々の部品
の加工精度は高くなければならないので、加工コストが
高いという問題がある。Despite the various features described above, the fluid dynamic spindle motor of the second conventional example has the following problems. First, the cap member 38 is press-fitted into the protruding portion 16c of the rotary shaft body 16 to press the upper flange portion 16b.
This is because a large stress is applied to the inner peripheral portion of the above and the upper flange portion 16b is deformed. When the upper flange portion 16b is deformed, there is a problem that both RRO and NRRO are deteriorated. Next, the lower flange portion 16d has the fitting protrusion 16e.
Is press-fitted into a fitting hole 16a1 opened below the shaft portion 16a and fixed to the shaft portion 16a.
That is, the lower part of the shaft portion 16a swells by press fitting. When the lower part of the shaft portion 16a swells, there is a problem that a galling phenomenon occurs in the radial dynamic pressure bearing portion and the shaft cannot rotate. Further, the number of parts is larger than that of the fluid dynamic pressure spindle motor of the first conventional example, and moreover, the processing accuracy of individual parts must be high, which causes a problem of high processing cost.
【００１３】[0013]
【発明が解決しようとする課題】解決しようとする第１
の課題は、Ｈ字型流体動圧軸受を備えた動圧軸受スピン
ドルモータにおいて、Ｈ字型動圧軸受を構成する部品の
数を少なくすることである。解決しようとする第２の課
題は、振れの良いＨ字型流体動圧軸受を備えた動圧軸受
スピンドルモータを提供することである。First problem to be solved
The problem is to reduce the number of parts constituting the H-shaped dynamic pressure bearing in the dynamic pressure bearing spindle motor including the H-shaped fluid dynamic pressure bearing. A second problem to be solved is to provide a dynamic pressure bearing spindle motor including an H-shaped fluid dynamic pressure bearing with good runout.
【００１４】[0014]
【課題を解決するための手段】上記課題を解決する請求
項１の発明は、ラジアル動圧軸受部と上スラスト動圧軸
受部と下スラスト動圧軸受部とを有する流体動圧軸受に
よってロータがステータに支持された動圧軸受スピンド
ルモータにおいて、ロータマグネットが取り付けられ且
つ負荷搭載面が形成されたロータフレームを、上スラス
ト動圧軸受部を構成する上スラスト部材に兼用したこと
を特徴とするものである。According to a first aspect of the invention for solving the above-mentioned problems, a rotor is constituted by a fluid dynamic bearing having a radial dynamic pressure bearing portion, an upper thrust dynamic pressure bearing portion and a lower thrust dynamic pressure bearing portion. In a dynamic pressure bearing spindle motor supported by a stator, a rotor frame to which a rotor magnet is attached and a load mounting surface is formed is also used as an upper thrust member forming an upper thrust dynamic pressure bearing portion. Is.
【００１５】また、上記課題を解決する請求項２の発明
は、円環状上端面と円環状下端面とを有するスリーブ
と、前記円環状下端面に対向配置される下スラスト部材
が端部に形成されたフランジ付シャフトと、前記円環状
上端面に対向配置されて前記フランジ付シャフトの上端
部に圧入によって固着された上スラスト部材と、ラジア
ル隙間を形成する前記スリーブの内周面と前記フランジ
付シャフトの外周面のいずれか一方に設けられたラジア
ル動圧発生溝と、第１スラスト隙間を形成する前記スリ
ーブの円環状上端面と前記上スラスト部材の下面のいず
れか一方に設けられた第１スラスト動圧発生溝と、第２
スラスト隙間を形成する前記スリーブの円環状下端面と
前記下スラスト部材の上面のいずれか一方に設けられた
第２スラスト動圧発生溝と、前記ラジアル隙間と第１ス
ラスト隙間と第２スラスト隙間を含む前記構成部材間の
微小隙間に充填された潤滑油とで構成された流体動圧軸
受によって、ロータマグネットを含むロータがステータ
コイルを含むステータに回転自在に支持された動圧軸受
スピンドルモータであって、その特徴は、前記ロータマ
グネットが取り付けられ且つ負荷搭載面が形成されたロ
ータフレームを、前記上スラスト部材に兼用したことで
ある。According to a second aspect of the invention for solving the above-mentioned problems, a sleeve having an annular upper end surface and an annular lower end surface, and a lower thrust member arranged to face the annular lower end surface is formed at an end portion. Flanged shaft, an upper thrust member that is arranged to face the annular upper end surface and is fixed to the upper end of the flanged shaft by press fitting, an inner peripheral surface of the sleeve that forms a radial gap, and the flanged member. A radial dynamic pressure generating groove provided on one of the outer peripheral surfaces of the shaft, a first annular ring of the sleeve forming a first thrust gap, and a first surface provided on the lower surface of the upper thrust member. The thrust dynamic pressure generating groove and the second
A second thrust dynamic pressure generating groove provided on one of the annular lower end surface of the sleeve forming the thrust gap and the upper surface of the lower thrust member, the radial gap, the first thrust gap, and the second thrust gap. A hydrodynamic bearing spindle motor in which a rotor including a rotor magnet is rotatably supported by a stator including a stator coil by a fluid dynamic pressure bearing formed of a lubricating oil filled in a minute gap between the constituent members. The characteristic is that the rotor frame to which the rotor magnet is attached and the load mounting surface is formed is also used as the upper thrust member.
【００１６】[0016]
【発明の実施の形態】本発明の第１実施形態の動圧軸受
スピンドルモータは、図１に縦断面図で示す如く、Ｈ字
型流体動圧軸受によってロータがステータに回転自在に
支持されたものである。BEST MODE FOR CARRYING OUT THE INVENTION In a hydrodynamic bearing spindle motor according to a first embodiment of the present invention, a rotor is rotatably supported by a stator by an H-shaped fluid dynamic bearing, as shown in a longitudinal sectional view in FIG. It is a thing.
【００１７】図１の第１実施形態の動圧軸受スピンドル
モータにおいて、ロータはロータフレーム６とロータマ
グネット７とから構成されている。ロータフレーム６
は、円盤部６ｃと円環部６ｂと円筒部６ａを有する部材
で、カップ状ハブとして機能する部材である。ロータマ
グネット７は環状の永久磁石であって、ロータフレーム
６の円筒部６ａの内周面に取り付けられている。また、
ステータは、ベース基板９とステータコイル８を含んで
構成されている。ベース基板９は中央部に形成された突
出した円筒部９ａを有している。ステータコイル８は、
ベース基板９の円筒部９ａの外周面に取り付けられてい
る。In the dynamic pressure bearing spindle motor of the first embodiment shown in FIG. 1, the rotor is composed of a rotor frame 6 and a rotor magnet 7. Rotor frame 6
Is a member having a disc portion 6c, an annular portion 6b, and a cylindrical portion 6a, and functions as a cup-shaped hub. The rotor magnet 7 is an annular permanent magnet, and is attached to the inner peripheral surface of the cylindrical portion 6 a of the rotor frame 6. Also,
The stator includes a base substrate 9 and a stator coil 8. The base substrate 9 has a protruding cylindrical portion 9a formed at the center. The stator coil 8 is
It is attached to the outer peripheral surface of the cylindrical portion 9 a of the base substrate 9.
【００１８】第１実施形態におけるＨ字型流体動圧軸受
は、円環状上端面と円環状下端面とを有する肉厚のスリ
ーブ４と、フランジ３が下端部に形成されたフランジ付
シャフト１と、フランジ付シャフト１の上端部に圧入に
よって固着されたロータフレーム６と、フランジ３が収
納される凹部が形成されたベース基板９とで構成されて
いる。スリーブ４は、円筒部９ａに内嵌されてベース基
板９に固着されている。The H-shaped fluid dynamic bearing according to the first embodiment includes a thick sleeve 4 having an annular upper end surface and an annular lower end surface, and a flanged shaft 1 having a flange 3 formed at the lower end. The rotor frame 6 is press-fitted to the upper end of the flanged shaft 1, and the base substrate 9 is provided with a recess for accommodating the flange 3. The sleeve 4 is fitted in the cylindrical portion 9 a and fixed to the base substrate 9.
【００１９】第１実施形態におけるＨ字型流体動圧軸受
において、ラジアル動圧発生溝Ｇ１は、スリーブ４の内
周面との間にラジアル隙間Ｒ３を形成するフランジ付シ
ャフト１の外周面に設けられている。また、第１スラス
ト動圧発生溝Ｇ２は、ロータフレーム６の内周側下面と
の間に第１スラスト隙間Ｒ２を形成するスリーブ４の円
環状上端面に設けられている。更に、第２スラスト動圧
発生溝Ｇ２は、フランジ３の上面との間に第２スラスト
隙間Ｒ４を形成するスリーブ４の円環状下端面に設けら
れている。そして、前記ラジアル隙間Ｒ３と第１スラス
ト隙間Ｒ２と第２スラスト隙間Ｒ４を含む前記構成部材
間の微小隙間Ｒ１〜Ｒ６には潤滑油が充填されている。In the H-shaped fluid dynamic bearing of the first embodiment, the radial dynamic pressure generating groove G1 is provided on the outer peripheral surface of the flanged shaft 1 forming a radial gap R3 between the radial dynamic pressure generating groove G1 and the inner peripheral surface of the sleeve 4. Has been. Further, the first thrust dynamic pressure generating groove G2 is provided on the annular upper end surface of the sleeve 4 which forms a first thrust gap R2 with the inner circumferential lower surface of the rotor frame 6. Further, the second thrust dynamic pressure generating groove G2 is provided on the annular lower end surface of the sleeve 4 which forms a second thrust gap R4 with the upper surface of the flange 3. Lubricating oil is filled in the minute gaps R1 to R6 between the constituent members including the radial gap R3, the first thrust gap R2, and the second thrust gap R4.
【００２０】なお、第１実施形態におけるＨ字型流体動
圧軸受において、ラジアル動圧発生溝Ｇ１はスリーブ４
の内周面に設けられてもよい。また、第１スラスト動圧
発生溝Ｇ２はロータフレーム６の内周側下面に設けても
よい。更に、第２スラスト動圧発生溝Ｇ２はフランジ３
の上面に設けてもよい。In the H-shaped fluid dynamic bearing according to the first embodiment, the radial dynamic pressure generating groove G1 has the sleeve 4
May be provided on the inner peripheral surface. Further, the first thrust dynamic pressure generating groove G2 may be provided on the inner peripheral side lower surface of the rotor frame 6. Further, the second thrust dynamic pressure generating groove G2 is formed on the flange 3
May be provided on the upper surface of.
【００２１】また、第１実施形態におけるＨ字型流体動
圧軸受において、微小隙間Ｒ１を形成するベース基板９
の円筒部９ａの上端部をスリーブ４の上端面よりも低く
し、代わりに図２に示す如く、スリーブ４の上端面の外
周側に突出した円筒部を形成してもよい。Further, in the H-shaped fluid dynamic bearing in the first embodiment, the base substrate 9 forming the minute gap R1.
The upper end portion of the cylindrical portion 9a may be lower than the upper end surface of the sleeve 4, and instead, as shown in FIG. 2, a cylindrical portion protruding toward the outer peripheral side of the upper end surface of the sleeve 4 may be formed.
【００２２】上述の如く、第１実施形態の動圧軸受スピ
ンドルモータは、フランジ付シャフト１、スリーブ４、
ロータフレーム６、ロータマグネット７、ステータコイ
ル８、及びベース基板９の６点の部品から構成されてい
る。従って、第１実施形態の動圧軸受スピンドルモータ
は、その部品点数は、図４の第１従来例の動圧軸受スピ
ンドルモータに比べて１個少なく、また図３の第２従来
例の動圧軸受スピンドルモータに比べて２個少ない。し
かも、ロータフレーム６は、その上面は負荷搭載面、且
つその下面はスラスト動圧軸受部のスラスト隙間形成面
として夫々機能するものである。従って、第１実施形態
の動圧軸受スピンドルモータは、第１従来例や第２従来
例の動圧軸受スピンドルモータに比べて、負荷搭載面と
スラスト隙間形成面との平行度が非常によい。As described above, the dynamic pressure bearing spindle motor of the first embodiment has the flanged shaft 1, sleeve 4,
The rotor frame 6, the rotor magnet 7, the stator coil 8 and the base substrate 9 are composed of six parts. Therefore, the dynamic pressure bearing spindle motor of the first embodiment has one less component than the dynamic pressure bearing spindle motor of the first conventional example shown in FIG. 4, and the dynamic pressure of the second conventional example shown in FIG. Two less than the bearing spindle motor. Moreover, the upper surface of the rotor frame 6 functions as a load mounting surface, and the lower surface thereof functions as a thrust gap forming surface of the thrust dynamic pressure bearing portion. Therefore, in the dynamic pressure bearing spindle motor of the first embodiment, the parallelism between the load mounting surface and the thrust gap forming surface is very good as compared with the dynamic pressure bearing spindle motors of the first conventional example and the second conventional example.
【００２３】次に、本発明の第２実施形態の動圧軸受ス
ピンドルモータは、図２に縦断面図で示す如く、Ｈ字型
流体動圧軸受によってロータがステータに回転自在に支
持されたものである。Next, in the dynamic pressure bearing spindle motor of the second embodiment of the present invention, the rotor is rotatably supported by the stator by the H-shaped fluid dynamic pressure bearing as shown in the longitudinal sectional view of FIG. Is.
【００２４】図２の第２実施形態の動圧軸受スピンドル
モータにおいて、ロータはロータフレーム６とロータマ
グネット７とから構成されている。ロータフレーム６
は、円盤部６ｃと円環部６ｂと円筒部６ａを有する部材
で、カップ状ハブとして機能する部材である。ロータマ
グネット７は環状の永久磁石であって、ロータフレーム
６の円筒部６ａの内周面に取り付けられている。また、
ステータは、ベース基板９とステータコイル８を含んで
構成されている。ベース基板９の中央部には、流体動圧
軸受が立設される貫通穴が形成されている。ステータコ
イル８は、ベース基板９の中央部に形成された貫通穴に
立設された流体動圧軸受の肉厚のスリーブ４の外周面に
取り付けられている。In the hydrodynamic bearing spindle motor of the second embodiment shown in FIG. 2, the rotor comprises a rotor frame 6 and a rotor magnet 7. Rotor frame 6
Is a member having a disc portion 6c, an annular portion 6b, and a cylindrical portion 6a, and functions as a cup-shaped hub. The rotor magnet 7 is an annular permanent magnet, and is attached to the inner peripheral surface of the cylindrical portion 6 a of the rotor frame 6. Also,
The stator includes a base substrate 9 and a stator coil 8. At the center of the base substrate 9, a through hole is formed in which a fluid dynamic bearing is erected. The stator coil 8 is attached to the outer peripheral surface of the thick walled sleeve 4 of the fluid dynamic bearing which is provided upright in a through hole formed in the central portion of the base substrate 9.
【００２５】第２実施形態におけるＨ字型流体動圧軸受
は、円環状上端面と円環状下端面とを有するスリーブ４
と、フランジ３が下端部に形成されたフランジ付シャフ
ト１と、フランジ付シャフト１の上端部に圧入によって
固着されたロータフレーム６と、スリーブ４に形成され
ているフランジ３の収納凹部の開放端を封止する円盤状
蓋部材１０とで構成されている。The H-shaped fluid dynamic bearing of the second embodiment has a sleeve 4 having an annular upper end surface and an annular lower end surface.
A flanged shaft 1 having a flange 3 formed at the lower end, a rotor frame 6 fixed to the upper end of the flanged shaft 1 by press fitting, and an open end of a storage recess of the flange 3 formed in the sleeve 4. And a disk-shaped lid member 10 for sealing the.
【００２６】第２実施形態におけるＨ字型流体動圧軸受
において、ラジアル動圧発生溝Ｇ１は、スリーブ４の内
周面との間にラジアル隙間Ｒ３を形成するフランジ付シ
ャフト１の外周面に設けられている。また、第１スラス
ト動圧発生溝Ｇ２は、スリーブ４の円環状上端面の間に
第１スラスト隙間Ｒ２を形成するロータフレーム６の内
周側下面に設けられている。更に、第２スラスト動圧発
生溝Ｇ２は、スリーブ４の円環状下端面との間に第２ス
ラスト隙間Ｒ４を形成するフランジ３の上面に設けられ
ている。そして、前記ラジアル隙間Ｒ３と第１スラスト
隙間Ｒ２と第２スラスト隙間Ｒ４を含む前記構成部材間
の微小隙間Ｒ１〜Ｒ６には潤滑油が充填されている。In the H-shaped fluid dynamic bearing according to the second embodiment, the radial dynamic pressure generating groove G1 is provided on the outer peripheral surface of the flanged shaft 1 forming a radial gap R3 between the radial dynamic pressure generating groove G1 and the inner peripheral surface of the sleeve 4. Has been. Further, the first thrust dynamic pressure generating groove G2 is provided on the inner peripheral side lower surface of the rotor frame 6 forming the first thrust gap R2 between the annular upper end surfaces of the sleeve 4. Further, the second thrust dynamic pressure generating groove G2 is provided on the upper surface of the flange 3 which forms a second thrust gap R4 between the second thrust dynamic pressure generating groove G2 and the annular lower end surface of the sleeve 4. Lubricating oil is filled in the minute gaps R1 to R6 between the constituent members including the radial gap R3, the first thrust gap R2, and the second thrust gap R4.
【００２７】なお、第２実施形態におけるＨ字型流体動
圧軸受において、ラジアル動圧発生溝Ｇ１はスリーブ４
の内周面に設けてもよい。また、第１スラスト動圧発生
溝Ｇ２はスリーブ４の円環状上端面に設けてもよい。更
に、第２スラスト動圧発生溝Ｇ２はスリーブ４の円環状
下端面に設けてもよい。In the H-shaped fluid dynamic bearing according to the second embodiment, the radial dynamic pressure generating groove G1 has the sleeve 4
It may be provided on the inner peripheral surface. Further, the first thrust dynamic pressure generating groove G2 may be provided on the annular upper end surface of the sleeve 4. Further, the second thrust dynamic pressure generating groove G2 may be provided on the annular lower end surface of the sleeve 4.
【００２８】また、第２実施形態における動圧軸受スピ
ンドルモータにおいて、スリーブ４の軸方向の半分より
も上から下の部分の外径を小さくし、且つスリーブ４の
前記小さな外径の外周面に外嵌する内周面を備えた円筒
部をベース基板９に形成し、スリーブ４をベース基板９
に固着するようにしてもよい。In the dynamic pressure bearing spindle motor according to the second embodiment, the outer diameter of the portion of the sleeve 4 above and below the axial half of the sleeve 4 is reduced, and the outer peripheral surface of the sleeve 4 having the smaller outer diameter is used. A cylindrical portion having an inner peripheral surface to be fitted is formed on the base substrate 9, and the sleeve 4 is attached to the base substrate 9.
You may make it stick to.
【００２９】上述の如く、第２実施形態の動圧軸受スピ
ンドルモータは、フランジ付シャフト１、スリーブ４、
ロータフレーム６、ロータマグネット７、ステータコイ
ル８、ベース基板９、及び円盤状蓋部材１０の７点の部
品から構成されている。従って、第１実施形態の動圧軸
受スピンドルモータは、その部品点数は図４の第１従来
例の動圧軸受スピンドルモータと同じであるが、図３の
第２従来例の動圧軸受スピンドルモータに比べて１個少
ない。しかも、ロータフレーム６は、その上面は負荷搭
載面、且つその下面はスラスト動圧軸受部のスラスト隙
間形成面として夫々機能するものである。従って、第１
実施形態の動圧軸受スピンドルモータは、第１従来例や
第２従来例の動圧軸受スピンドルモータに比べて、負荷
搭載面とスラスト隙間形成面との平行度が非常によい。As described above, the dynamic pressure bearing spindle motor of the second embodiment has the flanged shaft 1, sleeve 4,
The rotor frame 6, the rotor magnet 7, the stator coil 8, the base substrate 9, and the disc-shaped lid member 10 are composed of seven parts. Therefore, the dynamic pressure bearing spindle motor of the first embodiment has the same number of parts as the dynamic pressure bearing spindle motor of the first conventional example of FIG. 4, but the dynamic pressure bearing spindle motor of the second conventional example of FIG. 1 less than. Moreover, the upper surface of the rotor frame 6 functions as a load mounting surface, and the lower surface thereof functions as a thrust gap forming surface of the thrust dynamic pressure bearing portion. Therefore, the first
The dynamic pressure bearing spindle motor of the embodiment has much better parallelism between the load mounting surface and the thrust gap forming surface than the dynamic pressure bearing spindle motors of the first conventional example and the second conventional example.
【００３０】なお、第１実施形態及び第２実施形態のい
ずれにおいても、潤滑油の注入口であり、且つキャピラ
リーシール部である微小隙間Ｒ１には、図４の第１従来
例に採用されている如きテーパー状の開口部を形成する
のが望ましい。In both the first embodiment and the second embodiment, the minute gap R1 which is the lubricating oil injection port and the capillary seal portion is adopted in the first conventional example of FIG. It is desirable to form a tapered opening as shown in FIG.
【００３１】[0031]
【発明の効果】ロータフレームの一部をスラスト動圧軸
受部のスラスト隙間形成部材として兼用して構成されて
いることを特長とする本発明に係るＨ字型流体動圧軸受
を備えたスピンドルモータは、従来のＨ字型流体動圧軸
受を備えたスピンドルモータに比べて、部品点数を少な
くすることができ、同時にコスト低減を図ることができ
た。A spindle motor having an H-shaped fluid dynamic bearing according to the present invention, characterized in that a part of the rotor frame is also used as a thrust gap forming member of the thrust dynamic pressure bearing portion. In comparison with the conventional spindle motor equipped with an H-shaped fluid dynamic pressure bearing, the number of parts can be reduced, and at the same time, the cost can be reduced.
【００３２】本発明においては、ロータフレームは圧入
によってシャフトに固着されるが、この圧入によってス
ラスト部材として兼用されているロータフレームが変形
することがない。また、本発明におけるロータフレーム
は、その上面は負荷搭載面、且つその下面はスラスト動
圧軸受部のスラスト隙間形成面として夫々機能するもの
であるから、負荷搭載面とスラスト動圧軸受部のスラス
ト隙間形成面との平行度が非常によい。従って、本発明
に係る動圧軸受ピンドルモータは、従来のＨ字型流体動
圧軸受を備えたスピンドルモータに比べて、振れが良く
なった。In the present invention, the rotor frame is fixed to the shaft by press fitting, but the press fitting does not deform the rotor frame that also serves as the thrust member. Further, since the upper surface of the rotor frame in the present invention functions as a load mounting surface and the lower surface thereof functions as a thrust gap forming surface of the thrust dynamic pressure bearing portion, the thrust load bearing surface and thrust dynamic pressure bearing portion thrust surfaces are formed. Very good parallelism with the gap forming surface. Therefore, the dynamic pressure bearing pindle motor according to the present invention has better runout than the conventional spindle motor including the H-shaped fluid dynamic pressure bearing.
【図１】微小隙間を誇張して示した本発明の第１実施形
態のＨ字型流体動圧軸受を備えたスピンドルモータの縦
断面図である。FIG. 1 is a vertical cross-sectional view of a spindle motor including an H-shaped fluid dynamic bearing of a first embodiment of the present invention in which a minute gap is exaggeratedly shown.
【図２】微小隙間を誇張して示した本発明の第２実施形
態のＨ字型流体動圧軸受を備えたスピンドルモータの縦
断面図である。FIG. 2 is a vertical cross-sectional view of a spindle motor including an H-shaped fluid dynamic bearing according to a second embodiment of the present invention in which a minute gap is exaggerated.
【図３】微小隙間を誇張して示したＨ字型流体動圧軸受
を備えた従来のスピンドルモータ（第２従来例）の縦断
面図である。FIG. 3 is a vertical cross-sectional view of a conventional spindle motor (second conventional example) including an H-shaped fluid dynamic bearing in which a minute gap is exaggeratedly shown.
【図４】微小隙間を誇張して示したＴ字型流体動圧軸受
を備えた従来のスピンドルモータ（第１従来例）の縦断
面図である。FIG. 4 is a vertical cross-sectional view of a conventional spindle motor (first conventional example) including a T-shaped fluid dynamic bearing in which a minute gap is exaggeratedly shown.
【図５】スラスト動圧発生溝Ｇ２の一例を示す図であ
る。FIG. 5 is a diagram showing an example of a thrust dynamic pressure generating groove G2.
１ フランジ付シャフト ２ シャフト ３ フランジ ４ スリーブ ５ スラスト押え部材 ６ ロータフレーム ７ ロータマグネット ８ ステータコイル ９ ベース基板 １０ 円盤状蓋部材 １２ 固定スリーブ体 １６ 回転シャフト体 １６ａ シャフト部 １６ｂ 上フランジ部 １６ｃ 突出部 １６ｄ 下フランジ部 １６ｅ 嵌合突出部 ２４ ステータコイル ３２ ロータマグネット ３６ ロータフレーム ３８ キャップ部材 1 Shaft with flange 2 shafts 3 flange 4 sleeve 5 Thrust holding member 6 rotor frame 7 rotor magnet 8 Stator coil 9 Base substrate 10 Disc-shaped lid member 12 Fixed sleeve body 16 rotating shaft body 16a shaft part 16b Upper flange part 16c protrusion 16d Lower flange part 16e Fitting protrusion 24 stator coil 32 rotor magnet 36 rotor frame 38 Cap member
───────────────────────────────────────────────────── フロントページの続き (72)発明者 太田 敦司 千葉県千葉市美浜区中瀬１丁目８番地 セ イコーインスツルメンツ株式会社内 Ｆターム(参考） 3J011 AA20 BA02 BA08 CA02 KA02 KA03 5H019 AA09 CC04 DD01 EE14 FF03 5H605 AA07 BB05 CC04 EB02 EB06 EB15 5H607 AA11 AA12 BB01 BB07 BB09 BB14 BB17 BB25 CC01 DD03 DD16 GG01 GG02 GG09 GG12 GG15 ─────────────────────────────────────────────────── ─── Continued front page (72) Inventor Atsushi Ota 1-8 Nakase, Nakase, Mihama-ku, Chiba City, Chiba Prefecture Ico Instruments Co., Ltd. F-term (reference) 3J011 AA20 BA02 BA08 CA02 KA02 KA03 5H019 AA09 CC04 DD01 EE14 FF03 5H605 AA07 BB05 CC04 EB02 EB06 EB15 5H607 AA11 AA12 BB01 BB07 BB09 BB14 BB17 BB25 CC01 DD03 DD16 GG01 GG02 GG09 GG12 GG15
Claims (2)
受部と下スラスト動圧軸受部とを有する流体動圧軸受に
よってロータがステータに支持された動圧軸受スピンド
ルモータにおいて、ロータマグネットが取り付けられ且
つ負荷搭載面が形成されたロータフレームを、前記上ス
ラスト動圧軸受部を構成する上スラスト部材に兼用した
ことを特徴とする動圧軸受スピンドルモータ。1. A hydrodynamic bearing spindle motor in which a rotor is supported by a stator by a fluid dynamic bearing having a radial dynamic pressure bearing portion, an upper thrust dynamic pressure bearing portion, and a lower thrust dynamic pressure bearing portion. And a load bearing surface is formed on the rotor frame, and the rotor frame is also used as an upper thrust member constituting the upper thrust dynamic pressure bearing portion.
スリーブと、前記円環状下端面に対向配置される下スラ
スト部材が端部に形成されたフランジ付シャフトと、前
記円環状上端面に対向配置されて前記フランジ付シャフ
トの上端部に圧入によって固着された上スラスト部材
と、ラジアル隙間を形成する前記スリーブの内周面と前
記フランジ付シャフトの外周面のいずれか一方に設けら
れたラジアル動圧発生溝と、第１スラスト隙間を形成す
る前記スリーブの円環状上端面と前記上スラスト部材の
下面のいずれか一方に設けられた第１スラスト動圧発生
溝と、第２スラスト隙間を形成する前記スリーブの円環
状下端面と前記下スラスト部材の上面のいずれか一方に
設けられた第２スラスト動圧発生溝と、前記ラジアル隙
間と第１スラスト隙間と第２スラスト隙間を含む前記構
成部材間の微小隙間に充填された潤滑油とで構成された
流体動圧軸受によって、ロータマグネットを含むロータ
がステータコイルを含むステータに回転自在に支持され
た動圧軸受スピンドルモータであって、前記ロータマグ
ネットが取り付けられ且つ負荷搭載面が形成されたロー
タフレームを、前記上スラスト部材に兼用したことを特
徴とする動圧軸受スピンドルモータ。2. A sleeve having a ring-shaped upper end surface and a ring-shaped lower end surface, a flanged shaft having a lower thrust member, which is arranged opposite to the ring-shaped lower end surface, formed at an end thereof, and the ring-shaped upper end surface. Is provided on either one of the inner peripheral surface of the sleeve and the outer peripheral surface of the flanged shaft, which are arranged to face each other and are fixed by press fitting to the upper end portion of the flanged shaft, and the inner peripheral surface of the sleeve that forms a radial gap. The radial dynamic pressure generating groove, the first thrust dynamic pressure generating groove provided on one of the annular upper end surface of the sleeve forming the first thrust gap and the lower surface of the upper thrust member, and the second thrust gap are provided. A second thrust dynamic pressure generating groove provided on one of the annular lower end surface of the sleeve to be formed and the upper surface of the lower thrust member, the radial gap and the first thrust gap. And a rotor including a rotor magnet rotatably supported by a stator including a stator coil by a fluid dynamic pressure bearing including a lubricating oil filled in a minute gap between the constituent members including a second thrust gap. A hydrodynamic bearing spindle motor, wherein a rotor frame to which the rotor magnet is attached and a load mounting surface is formed is also used as the upper thrust member.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2001286294A JP4959078B2 (en) | 2001-09-20 | 2001-09-20 | Hydrodynamic bearing spindle motor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2001286294A JP4959078B2 (en) | 2001-09-20 | 2001-09-20 | Hydrodynamic bearing spindle motor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JP2003092867A true JP2003092867A (en) | 2003-03-28 |
| JP4959078B2 JP4959078B2 (en) | 2012-06-20 |
Family
ID=19109307
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2001286294A Expired - Fee Related JP4959078B2 (en) | 2001-09-20 | 2001-09-20 | Hydrodynamic bearing spindle motor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP4959078B2 (en) |
Cited By (27)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US7021829B2 (en) | 2003-07-22 | 2006-04-04 | Nidec Corporation | Fluid-dynamic-pressure bearing, spindle motor furnished with the fluid-dynamic-pressure bearing, method of manufacturing rotor assembly applied in the spindle motor, and recording-disk drive furnished with the spindle motor |
| US7345392B2 (en) * | 2004-04-08 | 2008-03-18 | Minebea Co., Ltd. | Spindle motor having a hydrodynamic bearing system |
| US7622837B2 (en) | 2005-04-21 | 2009-11-24 | Panasonic Corporation | Hydrodynamic bearing device and spindle motor having the bearing device, and recording and/or reproducing apparatus using the spindle motor |
| US7866047B2 (en) | 2005-03-18 | 2011-01-11 | Nidec Corporation | Sleeve-unit manufacturing method |
| US7988810B2 (en) | 2006-09-20 | 2011-08-02 | Nidec Corporation | Sleeve unit, method of manufacturing thereof, and motor using the sleeve unit |
| US8277125B2 (en) | 2009-06-12 | 2012-10-02 | Nidec Corporation | Bearing apparatus, spindle motor, and disk drive apparatus |
| US8337086B2 (en) | 2009-06-18 | 2012-12-25 | Nidec Corporation | Bearing apparatus, spindle motor, and disk drive apparatus |
| CN102938599A (en) * | 2012-11-21 | 2013-02-20 | 中国船舶重工集团公司第七0七研究所 | Permanent magnet gyro motor with double stators and through-hole bearing |
| US8472132B2 (en) | 2008-05-26 | 2013-06-25 | Nidec Corporation | Fluid dynamic bearing apparatus arranged to discharge air bubbles generated therein and a spindle motor and a disk drive apparatus including the same |
| US8508883B2 (en) | 2011-09-30 | 2013-08-13 | Nidec Corporation | Motor including hydrodynamic bearing and disk drive apparatus including same |
| US8514515B2 (en) | 2011-09-30 | 2013-08-20 | Nidec Corporation | Motor and disk drive apparatus |
| US8582233B2 (en) | 2012-02-01 | 2013-11-12 | Nidec Corporation | Motor and disk drive apparatus |
| US8587895B1 (en) | 2012-05-30 | 2013-11-19 | Nidec Corporation | Bearing mechanism, motor and disk drive apparatus |
| US8599513B1 (en) | 2012-05-30 | 2013-12-03 | Nidec Corporation | Bearing mechanism, motor, and disk drive apparatus |
| US8630063B2 (en) | 2012-05-30 | 2014-01-14 | Nidec Corporation | Bearing mechanism, motor, and disk drive apparatus |
| US8670209B2 (en) | 2012-07-13 | 2014-03-11 | Nidec Corporation | Spindle motor including a fluid dynamic bearing and disk drive apparatus with same |
| JP2014060910A (en) * | 2012-09-14 | 2014-04-03 | Samsung Electro-Mechanics Co Ltd | Spindle motor and hard disc drive including the same |
| US8690435B2 (en) | 2009-11-25 | 2014-04-08 | Nidec Corporation | Dynamic pressure bearing and spindle motor using the same |
| US8711514B2 (en) | 2011-09-30 | 2014-04-29 | Nidec Corporation | Motor and disk drive apparatus |
| US8724256B2 (en) | 2012-09-18 | 2014-05-13 | Nidec Corporation | Bearing apparatus, spindle motor, and disk drive apparatus |
| US8724257B2 (en) | 2012-09-18 | 2014-05-13 | Nidec Corporation | Hydrodynamic bearing apparatus and spindle motor and disk drive apparatus including the same |
| US8773816B1 (en) | 2013-03-13 | 2014-07-08 | Nidec Corporation | Spindle motor with hydrodynamic bearing structure having capillary seal and disk drive apparatus including same |
| US8797678B1 (en) | 2013-03-14 | 2014-08-05 | Nidec Corporation | Spindle motor and disk drive apparatus |
| US8794839B2 (en) | 2009-06-12 | 2014-08-05 | Nidec Corporation | Bearing apparatus, spindle motor, and disk drive apparatus |
| US8941946B2 (en) | 2013-03-14 | 2015-01-27 | Nidec Corporation | Motor including dynamic bearing with seal portion and disk drive apparatus including the same |
| US9001460B2 (en) | 2013-08-21 | 2015-04-07 | Nidec Corporation | Spindle motor, and disk drive apparatus |
| CN104810960A (en) * | 2014-01-27 | 2015-07-29 | 建准电机工业股份有限公司 | Motor with Thrust Bearing |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH08130852A (en) * | 1994-11-02 | 1996-05-21 | Nippon Densan Corp | Spindle motor |
| JP2000197309A (en) * | 1998-08-08 | 2000-07-14 | Nippon Densan Corp | Motor fitted with fluid pressure bearing and recording disc driver fitted with the motor |
| JP2001056023A (en) * | 1999-08-18 | 2001-02-27 | Seiko Instruments Inc | Spindle motor |
-
2001
- 2001-09-20 JP JP2001286294A patent/JP4959078B2/en not_active Expired - Fee Related
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH08130852A (en) * | 1994-11-02 | 1996-05-21 | Nippon Densan Corp | Spindle motor |
| JP2000197309A (en) * | 1998-08-08 | 2000-07-14 | Nippon Densan Corp | Motor fitted with fluid pressure bearing and recording disc driver fitted with the motor |
| JP2001056023A (en) * | 1999-08-18 | 2001-02-27 | Seiko Instruments Inc | Spindle motor |
Cited By (33)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US7021829B2 (en) | 2003-07-22 | 2006-04-04 | Nidec Corporation | Fluid-dynamic-pressure bearing, spindle motor furnished with the fluid-dynamic-pressure bearing, method of manufacturing rotor assembly applied in the spindle motor, and recording-disk drive furnished with the spindle motor |
| CN1321276C (en) * | 2003-07-22 | 2007-06-13 | 日本电产株式会社 | Liquid hydrodynamic bearing, main shaft motor , method for producing rotor assembly recording disc driving apparatus |
| US7345392B2 (en) * | 2004-04-08 | 2008-03-18 | Minebea Co., Ltd. | Spindle motor having a hydrodynamic bearing system |
| US7866047B2 (en) | 2005-03-18 | 2011-01-11 | Nidec Corporation | Sleeve-unit manufacturing method |
| US7622837B2 (en) | 2005-04-21 | 2009-11-24 | Panasonic Corporation | Hydrodynamic bearing device and spindle motor having the bearing device, and recording and/or reproducing apparatus using the spindle motor |
| US7988810B2 (en) | 2006-09-20 | 2011-08-02 | Nidec Corporation | Sleeve unit, method of manufacturing thereof, and motor using the sleeve unit |
| US8472132B2 (en) | 2008-05-26 | 2013-06-25 | Nidec Corporation | Fluid dynamic bearing apparatus arranged to discharge air bubbles generated therein and a spindle motor and a disk drive apparatus including the same |
| US8517611B2 (en) | 2009-06-12 | 2013-08-27 | Nidec Corporation | Bearing apparatus, spindle motor, and disk drive apparatus |
| US8568033B2 (en) | 2009-06-12 | 2013-10-29 | Nidec Corporation | Bearing apparatus, spindle motor, and disk drive apparatus |
| US8277125B2 (en) | 2009-06-12 | 2012-10-02 | Nidec Corporation | Bearing apparatus, spindle motor, and disk drive apparatus |
| US8967865B2 (en) | 2009-06-12 | 2015-03-03 | Nidec Corporation | Bearing apparatus, spindle motor, and disk drive apparatus |
| US8794839B2 (en) | 2009-06-12 | 2014-08-05 | Nidec Corporation | Bearing apparatus, spindle motor, and disk drive apparatus |
| US8337086B2 (en) | 2009-06-18 | 2012-12-25 | Nidec Corporation | Bearing apparatus, spindle motor, and disk drive apparatus |
| US8690435B2 (en) | 2009-11-25 | 2014-04-08 | Nidec Corporation | Dynamic pressure bearing and spindle motor using the same |
| US8514515B2 (en) | 2011-09-30 | 2013-08-20 | Nidec Corporation | Motor and disk drive apparatus |
| US8711514B2 (en) | 2011-09-30 | 2014-04-29 | Nidec Corporation | Motor and disk drive apparatus |
| US8508883B2 (en) | 2011-09-30 | 2013-08-13 | Nidec Corporation | Motor including hydrodynamic bearing and disk drive apparatus including same |
| US8582233B2 (en) | 2012-02-01 | 2013-11-12 | Nidec Corporation | Motor and disk drive apparatus |
| US8587895B1 (en) | 2012-05-30 | 2013-11-19 | Nidec Corporation | Bearing mechanism, motor and disk drive apparatus |
| US8599513B1 (en) | 2012-05-30 | 2013-12-03 | Nidec Corporation | Bearing mechanism, motor, and disk drive apparatus |
| US8630063B2 (en) | 2012-05-30 | 2014-01-14 | Nidec Corporation | Bearing mechanism, motor, and disk drive apparatus |
| US8670209B2 (en) | 2012-07-13 | 2014-03-11 | Nidec Corporation | Spindle motor including a fluid dynamic bearing and disk drive apparatus with same |
| JP2014060910A (en) * | 2012-09-14 | 2014-04-03 | Samsung Electro-Mechanics Co Ltd | Spindle motor and hard disc drive including the same |
| US8724256B2 (en) | 2012-09-18 | 2014-05-13 | Nidec Corporation | Bearing apparatus, spindle motor, and disk drive apparatus |
| US8724257B2 (en) | 2012-09-18 | 2014-05-13 | Nidec Corporation | Hydrodynamic bearing apparatus and spindle motor and disk drive apparatus including the same |
| CN102938599A (en) * | 2012-11-21 | 2013-02-20 | 中国船舶重工集团公司第七0七研究所 | Permanent magnet gyro motor with double stators and through-hole bearing |
| CN102938599B (en) * | 2012-11-21 | 2016-04-27 | 中国船舶重工集团公司第七0七研究所 | A kind of bimorph transducer through hole bearing permanent magnet gyro motor |
| US8773816B1 (en) | 2013-03-13 | 2014-07-08 | Nidec Corporation | Spindle motor with hydrodynamic bearing structure having capillary seal and disk drive apparatus including same |
| US8797678B1 (en) | 2013-03-14 | 2014-08-05 | Nidec Corporation | Spindle motor and disk drive apparatus |
| US8941946B2 (en) | 2013-03-14 | 2015-01-27 | Nidec Corporation | Motor including dynamic bearing with seal portion and disk drive apparatus including the same |
| US9001460B2 (en) | 2013-08-21 | 2015-04-07 | Nidec Corporation | Spindle motor, and disk drive apparatus |
| CN104810960A (en) * | 2014-01-27 | 2015-07-29 | 建准电机工业股份有限公司 | Motor with Thrust Bearing |
| US20150214809A1 (en) * | 2014-01-27 | 2015-07-30 | Sunonwealth Electric Machine Industry Co., Ltd. | Motor with Thrust Bearing |
Also Published As
| Publication number | Publication date |
|---|---|
| JP4959078B2 (en) | 2012-06-20 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| JP2003092867A (en) | Dynamic pressure bearing spindle motor | |
| US7391139B2 (en) | Spindle motor and rotation apparatus | |
| US7654744B2 (en) | Fluid dynamic bearing mechanism for a motor | |
| US6211592B1 (en) | Motor for driving storage disks | |
| JP2006097894A (en) | Fluid dynamic bearing device | |
| JP2000186717A (en) | Fluid dynamic pressure bearing, spindle motor, and rotor device | |
| US7699527B2 (en) | Fluid bearing device | |
| US20080063332A1 (en) | Hydrodynamic bearing device and motor and recording and reproducing apparatus using the same | |
| JP2007107641A (en) | Spindle motor and turning device | |
| JP2001020945A (en) | Dynamic pressure bearing | |
| JP2001056023A (en) | Spindle motor | |
| JP3996436B2 (en) | Hydrodynamic bearing motor | |
| JP3991215B2 (en) | Hydrodynamic bearing device | |
| JP2004190855A (en) | Spindle motor | |
| JP2006158015A (en) | Method of manufacturing spindle motor | |
| JP2007060731A (en) | Spindle motor and rotary device | |
| JP2000215589A (en) | Motor for driving recording disk and recording disk drive device provided with the same | |
| JP4661014B2 (en) | DYNAMIC PRESSURE BEARING DEVICE AND SPINDLE MOTOR HAVING THE DYNAMIC PRESSURE BEARING DEVICE | |
| JPH10259820A (en) | Hydrodynamic fluid bearing | |
| JPH11155254A (en) | Dynamic-pressure bearing motor | |
| JP3892995B2 (en) | Hydrodynamic bearing unit | |
| JP2004108549A (en) | Hydrodynamic bearing device | |
| JP2011074951A (en) | Fluid dynamic bearing device | |
| JP3013969B2 (en) | Dynamic pressure bearing device | |
| JP2002168250A (en) | Fluid dynamic-pressure bearing |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| RD01 | Notification of change of attorney |
Free format text: JAPANESE INTERMEDIATE CODE: A7421 Effective date: 20040303 |
|
| A621 | Written request for application examination |
Free format text: JAPANESE INTERMEDIATE CODE: A621 Effective date: 20080516 |
|
| RD01 | Notification of change of attorney |
Free format text: JAPANESE INTERMEDIATE CODE: A7421 Effective date: 20091113 |
|
| A977 | Report on retrieval |
Free format text: JAPANESE INTERMEDIATE CODE: A971007 Effective date: 20100616 |
|
| A131 | Notification of reasons for refusal |
Free format text: JAPANESE INTERMEDIATE CODE: A131 Effective date: 20100622 |
|
| A601 | Written request for extension of time |
Free format text: JAPANESE INTERMEDIATE CODE: A601 Effective date: 20100820 |
|
| A711 | Notification of change in applicant |
Free format text: JAPANESE INTERMEDIATE CODE: A711 Effective date: 20100820 |
|
| A521 | Written amendment |
Free format text: JAPANESE INTERMEDIATE CODE: A523 Effective date: 20100823 |
|
| A521 | Written amendment |
Free format text: JAPANESE INTERMEDIATE CODE: A821 Effective date: 20100820 |
|
| A602 | Written permission of extension of time |
Free format text: JAPANESE INTERMEDIATE CODE: A602 Effective date: 20100913 |
|
| A521 | Written amendment |
Free format text: JAPANESE INTERMEDIATE CODE: A523 Effective date: 20100921 |
|
| A072 | Dismissal of procedure |
Free format text: JAPANESE INTERMEDIATE CODE: A072 Effective date: 20110419 |
|
| A131 | Notification of reasons for refusal |
Free format text: JAPANESE INTERMEDIATE CODE: A131 Effective date: 20110524 |
|
| TRDD | Decision of grant or rejection written | ||
| A01 | Written decision to grant a patent or to grant a registration (utility model) |
Free format text: JAPANESE INTERMEDIATE CODE: A01 Effective date: 20120313 |
|
| A01 | Written decision to grant a patent or to grant a registration (utility model) |
Free format text: JAPANESE INTERMEDIATE CODE: A01 |
|
| A61 | First payment of annual fees (during grant procedure) |
Free format text: JAPANESE INTERMEDIATE CODE: A61 Effective date: 20120321 |
|
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20150330 Year of fee payment: 3 |
|
| R150 | Certificate of patent or registration of utility model |
Free format text: JAPANESE INTERMEDIATE CODE: R150 |
|
| R250 | Receipt of annual fees |
Free format text: JAPANESE INTERMEDIATE CODE: R250 |
|
| LAPS | Cancellation because of no payment of annual fees |