JP3904179B2 - Spindle motor - Google Patents

Spindle motor Download PDF

Info

Publication number
JP3904179B2
JP3904179B2 JP2000120481A JP2000120481A JP3904179B2 JP 3904179 B2 JP3904179 B2 JP 3904179B2 JP 2000120481 A JP2000120481 A JP 2000120481A JP 2000120481 A JP2000120481 A JP 2000120481A JP 3904179 B2 JP3904179 B2 JP 3904179B2
Authority
JP
Japan
Prior art keywords
bearing assembly
rotor
flange
seal
stator
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.)
Expired - Fee Related
Application number
JP2000120481A
Other languages
Japanese (ja)
Other versions
JP2000324746A (en
Inventor
ユルゲン・エールシュ
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.)
Minebea Co Ltd
Original Assignee
Minebea Co 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 Minebea Co Ltd filed Critical Minebea Co Ltd
Publication of JP2000324746A publication Critical patent/JP2000324746A/en
Application granted granted Critical
Publication of JP3904179B2 publication Critical patent/JP3904179B2/en
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

Links

Images

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
    • H02K5/173—Means for supporting bearings, e.g. insulating supports or means for fitting bearings in the bearing-shields using bearings with rolling contact, e.g. ball bearings
    • H02K5/1737—Means for supporting bearings, e.g. insulating supports or means for fitting bearings in the bearing-shields using bearings with rolling contact, e.g. ball 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
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/80—Labyrinth sealings
    • G—PHYSICS
    • G11—INFORMATION STORAGE
    • G11B—INFORMATION STORAGE BASED ON RELATIVE MOVEMENT BETWEEN RECORD CARRIER AND TRANSDUCER
    • G11B19/00—Driving, starting, stopping record carriers not specifically of filamentary or web form, or of supports therefor; Control thereof; Control of operating function ; Driving both disc and head
    • G11B19/20—Driving; Starting; Stopping; Control thereof
    • G11B19/2009—Turntables, hubs and motors for disk drives; Mounting of motors in the drive
    • 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
    • F16C2370/00—Apparatus relating to physics, e.g. instruments
    • F16C2370/12—Hard disk drives or the like

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Power Engineering (AREA)
  • Mechanical Engineering (AREA)
  • Motor Or Generator Frames (AREA)
  • Permanent Magnet Type Synchronous Machine (AREA)

Abstract

The spindle motor is secured from turning which has bearings axially superimpose. The bearings consist of a base plate disk of an internal ring and an outer ring which is connected with an external rotor secured from turning. A labyrinth seal is arranged in the bearing lid which prevents oil from pouring from the bearing.

Description

【０００１】
【発明の属する技術分野】
本発明は、ラビリンスシール構造のスピンドルモータに関する。
【０００２】
【従来の技術】
磁気ディスクドライブに使用されるスピンドルモータは、軸受アセンブリーを介して固定中心軸を中心にして回転するロータを有しており、軸受アセンブリーからグリース（以下、当業界の用法に従い「オイル」ということにする）がロータの外側へ漏れて磁気ディスクを汚染することがないように、ロータの両端部を別体のオイルシール部材で覆っている。そして、ロータの内周面と固定中心軸の外周面との間の間隔は軸受アセンブリーからオイルの漏れが生じない程度に例えば０．０１ｍｍ程度離間して、いわゆるラビリンスシール構造になるように設計されている。
【０００３】
ところで、従来のスピンドルモータにおいては、オイルシール部材は中心穴の直径が固定中心軸の半径の間隔、即ち、０．０１ｍｍ程度大きな環状部材で構成して、これらのオイルシール部材をロータの対応端部に取り付けるように設計されている。
【０００４】
ところが、このようなオイルシール部材をロータ及びロータを軸受アセンブリーに固定する接続部材に取り付ける場合は、必然的に取り付け誤差が生じること、及び、オイルシール部材がロータや接続部材に傾斜して取り付けられる場合もあることから、オイルシール部材の中心壁面の一部が固定中心軸の外周面に接触してしまうと不具合が生じる。このことはスピンドルモータの生産性を低下させる。
【０００５】
【発明が解決しようとする課題】
本発明の課題は、軸受アセンブリーの両端部から外部へ潤滑油漏れのないようにシール構造を改良したスピンドルモータを提供することにある。
【０００６】
【課題を解決するための手段】
以上の課題を解決するために、本発明に基づくラビリンスシール形スピンドルモータは、ステータを担持する基板と、該ステータと共軸に一端が該基板に接続された中心軸と、該ステータから軸方向にずれて形成された胴部を有し該中心軸を共軸に囲繞して配設されたロータと、該ロータの該胴部内に該ロータ及び該中心軸に共軸に配設された軸受アセンブリーと、該ロータの該胴部と該軸受アセンブリーとの間に設けられ該ロータを該軸受アセンブリーに接続する有底円筒接続部材とを具備するスピンドルモータであって、前記有底円筒接続部材は、その一部分である第１有底部として、前記軸受アセンブリーの一端部の軸方向外側に、かつ、当該有底円筒接続部材の一端部に半径方向内向きに、当該有底円筒接続部材と一体的に形成された第１フランジ状シール部を備え、
前記第１フランジ状シール部は、前記中心軸の半径よりも所定のラビリンスシール間隔だけ大きな半径を有し該中心軸に共軸に該中心軸を貫通させる第１シール穴を有し、前記ロータは、その一部分である第２有底部として、前記軸受アセンブリーの他端部の軸方向外側に、かつ、当該ロータの、前記有底円筒接続部材の前記一端部と反対側の端部に半径方向内向きに、当該ロータと一体的に形成された第２フランジ状シール部を備え、前記第２フランジ状シール部は、前記中心軸の半径よりも所定のラビリンスシール間隔だけ大きな半径を有し該中心軸に共軸に該中心軸を貫通させる第２シール穴を有し、前記第１シール穴の壁面と前記中心軸の外周面との間及び前記第２シール穴の壁面と該中心軸の外周面との間に全周にわたって均一な前記ラビリンスシール間隔を有するラビリンスシールを形成して成り、前記有底円筒接続部材における前記第１有底部を除く円筒部の半径方向外側の壁は、前記ロータの前記第２有底部に接続する壁部の半径方向内側の壁に隣接しており、前記軸受アセンブリーは、前記第１フランジ状シール部である前記第１有底部、前記円筒部及び前記第２フランジ状シール部である前記第２有底部によって囲まれている。
また、本発明では、前記有底円筒接続部材は、その前記第１フランジ状シール部である前記第１有底部が前記軸受アセンブリーに接するように配置されていると共に、前記円筒部もまた当該軸受アセンブリーに接するように配置されており、かつ、前記ロータは、その前記第２フランジ状シール部である前記第２有底部が前記軸受アセンブリーに接するように配置されていると共に、前記壁部もまた当該軸受アセンブリーに接するように配置されているように構成することが望ましい。
【０００７】
軸受アセンブリーの前記一端部を、第１フランジ状シール部がステータ側に位置するようにステータ側に形成され、軸受アセンブリーの前記他端部は、第２フランジ状シール部が軸受アセンブリーに関してステータの反対側に位置するように、軸受アセンブリーに関してステータの反対側に形成されることが望ましい。
【０００８】
また、軸受アセンブリーの他端部は、第２フランジ状シール部がステータ側に位置するようにステータ側に形成され、軸受アセンブリーの前記一端部は、第１フランジ状シール部が軸受アセンブリーに関してステータの反対側に位置するように、軸受アセンブリーに関してステータの反対側に形成されることも望ましい。
【０００９】
軸受アセンブリーは、中心軸の外周面に固定される内輪と円筒接続部の内周面に固定される外輪と、内輪と外輪との間に配設されて内外輪に保持される転動体を含み、外輪の、軸受アセンブリーの前記一端側から軸方向外側に離間するロータの胴部に半径方向内側に向く円筒支持部を形成し、円筒支持部と外輪との間に円筒支持部と外輪とに圧接するＯリングを設けることも望ましい。
【００１０】
円筒形接続部材は、スリーブと第１フランジ状シール部で軸断面でＵ字形になっていることが望ましく、また、第１及び第２ラビリンスシールの間隔は０．００５ｍｍ乃至０．０２ｍｍ、特に、実質的に０．０１ｍｍであることが望ましい。
【００１１】
【発明の実施の形態】
以下、図面を参照して本発明を実施形態に基づいて説明する。
【００１２】
図１は、本発明のスピンドルモータの第１実施形態である。図１に示すように、スピンドルモータは基板１を有し、これに図中上方へ延びる中心軸２が下端で固定されている。１９はステータであり、積層コア（鉄心）２０とそれの歯部に巻きかけられたコイル２１とから成り、中心軸２に共軸になるように基板１に固定されている。コイル２１は対応の接続ピン２２を介して導出されている。
【００１３】
ロータ１０は、環状の胴部２３と、図１において胴部２３の下方にスカート状に増径した薄肉の円筒部２４とを有する。この円筒部２４の内周面にステータ１９を囲繞する環状の永久磁石２５が設けられている。
【００１４】
ロータ１０の胴部２３の内周面２６は円柱状の孔（中央孔）を形成する。ロータ１０は胴部２３で後述の円筒接続部材６を介して中心軸２を中心にして回転するように設けられている。
【００１５】
中心軸２に、環状スペーサ１２を間において１対の軸受４，５が嵌装されている。図示の場合は、これら軸受４，５は玉軸受で、それぞれ内輪４ａ，５ａと、外輪４ｂ，５ｂと、内外輪間の玉４ｃ，５ｃとを含む。内輪４ａ，５ａは内周面で中心軸２の外周面に固定されている。ここで、両軸受４，５及びスペーサ１２の組み合わせを軸受アセンブリー２７と呼ぶことにする。
【００１６】
軸断面Ｕ字形（即ちコップ状）の円筒接続部材６は、円筒形のスリーブ部７とその一端（図１では下端、即ち、ステータ１９側端）にこれと一体に設けられた半径方向内側へ向く環状のフランジ状シール部（以下「第１フランジ状シール部」という）８とから成る。軸受４，５の外輪４ｂ，５ｂの外周面がスリーブ部７の内周面に接するように、軸受アセンブリー２７がスリーブ部７に圧入されている。また、第１フランジ状シール部８は、その上面（ステータ１９と反対側）が下側（即ち、ステータ１９側）の軸受４の外輪４ｂの下側（即ち、ステータ１９側）の端面に接している。従って、軸受アセンブリー２７は円筒接続部材６に嵌入されている。中心軸２の外径、軸受アセンブリー２７の内外径、円筒接続部材６のスリーブ部の内外径の公差を所望のラビリンスシール間隔（例えば、０．０１ｍｍ程度）の２倍の数分の１から１／１０（例えば、０．００１ｍｍ乃至０．００５ｍｍ）程度に形成する。
【００１７】
第１フランジ状シール部８は円柱形の中心シール穴（以下、「第１中心シール穴」という）２８を有する。この第１中心シール穴２８は中心軸２に対して上記の公差程度で共軸になるように形成され、その半径は中心軸２の外形よりも実質的に所望のラビリンスシール間隔（例えば、０．００５ｍｍ乃至０．０２ｍｍ、（一般には０．０１ｍｍ又はその近傍 ））に形成されている。
【００１８】
従って、円筒接続部材６を、中心軸２に取り付けられた軸受アセンブリー２７に組み付けると、中心軸２を囲繞する第１フランジ状シール部８の第１中心シール穴２８と中心軸２との間にそれらの全円周にわたって実質的に等しい隙間が生じる。この隙間の大きさは上記のラビリンス隙間に相当し、例えば、０．００５ｍｍ乃至０．０２ｍｍ（一般には０．０１ｍｍ又はその近傍 ））である。従って、中心軸２と第１フランジ状シール部８との間に全円周にわたって実質的に均一な隙間を形成する第１ラビリンスシール９（図１では、理解をよくするために隙間を誇張して大きく示している）が形成される。このため、第１ラビリンスシール９はオイルが軸受アセンブリー２７から下方（ステータ１９側）へ漏れたり飛散したりするのを防止する。また、この第１ラビリンスシール９は、円筒接続部材６の第１フランジ状シール部８の第１中心シール穴２８の壁面と中心軸２の外周面とが接触するのを防止する。
【００１９】
ロータ１０は、胴部２３の内周面２６で円筒接続部材６のスリーブ部７の外周面に嵌装されている。この内周面の直径も上記の公差と同等の公差を有するように形成されている。胴部２３の上端部（ステータ１９と反対側の端部）に胴部２３と一体に半径方向内側へ向く環状のフランジ状シール部（以下「第２フランジ状シール部」という）１３が形成されている。第２フランジ状シール部１３の下面（ステータ１９側の面）は上方（ステータ１９と反対側）の軸受５の内外輪５ａ，５ｂの上方（ステータ１９と反対側）の端面に圧接している。
【００２０】
第２フランジ状シール部１３は、第１フランジ状シール部８と同様に、円柱形の中心シール穴（以下「第２シール穴」という）２９を有する。この第２中心シール穴２９も中心軸２に対して上記の公差程度で共軸になるように形成され、その半径は中心軸２の外形よりも実質的に所望のラビリンスシール間隔（例えば、０．００５ｍｍ乃至０．０２ｍｍ（一般には０．０１ｍｍ又はその近傍 ））に形成されている。
【００２１】
従って、ロータ１０及び円筒接続部材６が中心軸２に組み付けられると、中心軸２を囲繞する第２フランジ状シール部１３の第２中心シール穴２９と中心軸２との間にそれらの全円周にわたって実質的に等しい隙間が生じる。この隙間の大きさは上記のラビリンス隙間に相当し、例えば、０．００５ｍｍ乃至０．０２ｍｍ（一般には０．０１ｍｍ又はその近傍 ））である。従って、中心軸２と第１フランジ状シール部８との間に全円周にわたって実質的に均一な隙間を形成する第２ラビリンスシール１１（図１では、これも理解をよくするために隙間を誇張して大きく示している）が形成される。このため、第２ラビリンスシール１１はオイルが軸受アセンブリー２７から上方（ステータ１９と反対側）へ漏れたり飛散したりするのを防止する。また、この第２ラビリンスシール１１はロータ１０の第２フランジ状シール部１３の第２中央シール穴２９の壁面と中心軸２の外周面とが接触するのを防止する。
【００２２】
図２は、本発明のスピンドルモータの第２実施形態を示す。この実施形態では、第１実施形態の第１フランジ状シール部８と第２フランジ状シール部１３とが交代して、即ち、第１ラビリンスシール９と第２ラビリンスシール１１とが交代して配置されている。
【００２３】
第２フランジ状シール部１３は、ロータ１０の胴部２３の下端面（ステータ１９側）にロータ１０と一体に形成される。また、円筒接続部材６は、第１フランジ状シール部８を上にして（即ち、ステータ１９と反対側に向けて）スリーブ部７がロータ１０の内周面２６と軸受アセンブリー２７の外周面との間に圧入される。こうすることによって、第１フランジ状シール部８の第１中心シール穴２８の壁面と中心軸２の外周面との間、及び、第２フランジ状シール部１３の第２中心シール穴２９の壁面と中心軸２との間に、それぞれ、全周にわたって均一な所望の隙間を有する第１ラビリンスシール９及び第２ラビリンスシール１１が形成される。これによって、第１実施形態同様、オイル漏れや飛散及びロータ１０などの回転部に中心軸２への当たりや接触を防止する。第２実施形態は、その他の部分や構造が第１実施形態の場合と同じであるから、 同一部品には同一参照番号を付して示し、それらの説明は省略する。
【００２４】
図３は本発明の第３実施形態を示す。この実施形態では、軸受アセンブリー３０は、基板１に固定された中心軸２の上端部の減径部３１に嵌合固定された内輪３２と、中心軸２の下側の外周面に形成された環状溝３３と、中心軸２を囲繞する１個の外輪３４と、内輪３２と外輪３４との間に保持されている転動体（図では玉）３５と、環状溝３３と外輪３４との間に保持されている転動体（図では玉）３６とを含む。
【００２５】
円筒接続部材６は、第１実施形態同様、スリーブ部７とその下端部に形成された第１フランジ状シール部８とから成る。スリーブ部７の外周面はロータ１０の胴部２３の内周面２６と嵌合しており、スリーブ部７の内周面の内下端部１７が外輪３４の外周面と嵌合している。この場合も、第１フランジ状シール部８の第１中心シール穴２８の壁面と中心軸２の外周面との間に第１実施形態の場合と同様の第１ラビリンスシール９が形成される。
【００２６】
ロータ１０に、胴部２３の上方に胴部２３から半径方向内側へ突出する円筒支持部３７を設けている。この円筒支持部３７の内壁に、半径方向内側へ突出してロータ１０を外輪３４に嵌合させる環状係止部１８が形成されている。また、円筒支持部３７の上端部にこれから半径方向内側に延びる第２フランジ状シール部１３を第１実施形態同様に設けている。この場合も、第２フランジ状シール部８の第１中心シール穴２８の壁面と中心軸２の減径部３１の外周面との間に第１実施形態の場合と同様の第２ラビリンスシール１１が形成される。
【００２７】
ロータ１０の円筒支持部３７の下面と円筒接続部材６のスリーブ部７の上端面との間に形成された環状空間１５に円筒支持部３７の下面とスリーブ部７の上端面とに圧接するＯリング１４が設けられている。このＯリング１４によって、外輪３４を迂回して生じる恐れのある軸受アセンブリー３０からのロータ１０の半径方向外側へオイルの漏れ又は飛散を防止することができる。他の部分や部材は、第１及び第２実施形態と実質的に同じであるから、これらの部分や部材には第１及び第２実施形態の場合と同じ番号を付けて示し、説明は省略する。
【００２８】
この第３実施形態においても、第１ラビリンスシール９及び第２ラビリンスシール１１は、全周にわたって均等にかつ所定のラビリンスシール間隔で形成されるから第１及び第２実施形態のラビリンスシールと同様の作用効果を有する。これにＯリングのシーリング効果が加重されることになる。
【００２９】
【発明の効果】
本発明は、軸受アセンブリーの両端部に設けられ中心軸との間にラビリンスシールを形成するシール部をロータ及びロータを軸受アセンブリーに保持する円筒接続部材に一体に形成し、これらのシール部に中心軸と精度が高く半径が所定のラビリンス間隔だけ大きな中心シール穴を形成したから、軸受アセンブリーからのオイルの漏れや飛散がなくかつロータなどの回転部材が中心軸に当たったり接触することがないという効果がある。
【図面の簡単な説明】
【図１】本発明のスピンドルモータの第１実施形態の縦断面図である。
【図２】本発明のスピンドルモータの第２実施形態の縦断面図である。
【図３】本発明のスピンドルモータの第３実施形態の左半分の縦断面図である。
【符号の説明】
１ 基板
２ 中心軸
４ 軸受
５ 軸受
６ 円筒接続部材
７ スリーブ部
８ 第１フランジ状シール部
９ 第１ラビリンスシール
１０ ロータ
１１ 第２ラビリンスシール
１３ 第２フランジ状シール部
１４ Ｏリング
１８ 環状係止部
１９ ステータ
２３ 胴部
２４ 円筒部
２６ 内周面
２７ 軸受アセンブリー
２８ 第１中心シール穴
２９ 第２中心シール穴
３０ 軸受アセンブリー
３７ 円筒支持部[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a spindle motor having a labyrinth seal structure.
[0002]
[Prior art]
A spindle motor used in a magnetic disk drive has a rotor that rotates about a fixed central axis via a bearing assembly. From the bearing assembly, grease (hereinafter referred to as “oil” in accordance with usage in the industry). However, both ends of the rotor are covered with separate oil seal members so that they do not leak to the outside of the rotor and contaminate the magnetic disk. The distance between the inner peripheral surface of the rotor and the outer peripheral surface of the fixed central shaft is designed to be a so-called labyrinth seal structure with a distance of, for example, about 0.01 mm so that no oil leaks from the bearing assembly. ing.
[0003]
By the way, in the conventional spindle motor, the oil seal member is composed of an annular member having a diameter of the center hole which is larger than the radius of the fixed central axis, that is, about 0.01 mm, and these oil seal members are arranged at the corresponding ends of the rotor. Designed to be attached to the part.
[0004]
However, when such an oil seal member is attached to the rotor and the connection member that fixes the rotor to the bearing assembly, an installation error inevitably occurs, and the oil seal member is attached to the rotor or the connection member at an inclination. In some cases, when a part of the central wall surface of the oil seal member comes into contact with the outer peripheral surface of the fixed central shaft, a problem occurs. This reduces the productivity of the spindle motor.
[0005]
[Problems to be solved by the invention]
An object of the present invention is to provide a spindle motor having an improved seal structure so that there is no leakage of lubricating oil from both ends of the bearing assembly to the outside.
[0006]
[Means for Solving the Problems]
In order to solve the above-described problems, a labyrinth seal type spindle motor according to the present invention includes a substrate carrying a stator, a central axis coaxially connected to the stator and one end connected to the substrate, and an axial direction from the stator. A rotor having a trunk portion formed so as to be offset from the central axis and surrounding the central axis with the coaxial axis, and a rotor and a bearing coaxially arranged with the central axis in the trunk portion of the rotor and assembly, the rotor is provided between the body portion and the bearing assembly of the rotor to a spindle motor having a bottomed cylindrical connecting member for connecting to the bearing assembly, the bottomed cylindrical connecting member , as a first bottom portion is a portion thereof, in the axially outer end portion of the bearing assembly, and radially inward at one end of the bottomed cylindrical connecting member, the bottomed cylindrical connecting member integrally to be formed Includes a first flange-like seal portion,
Wherein the first flange-like seal portion has a first sheet Lumpur hole through which the central axis in coaxially to the central axis has only large radius given labyrinth seal gap than the radius of said central axis, the rotor, as a second bottom portion is a portion, axially outwardly of the other end of the bearing assembly and of the rotor, the opposite end portion and the end portion of the bottomed cylindrical connecting member the radially inward, with the rotor and a second flange-like seal portion is integrally formed, said second flange-like seal portion is larger by a predetermined labyrinth seal gap than the radius the radius of the central axis having a second sheet Lumpur hole through which the central axis in coaxially to the central axis, and between wall surfaces of the second seal hole of the outer peripheral surface of the wall and the central axis of the first seal bore Between the outer periphery of the central axis and the entire circumference Serial Ri formed by forming a labyrinth seal having a labyrinth seal gap, the radially outer wall of the cylindrical portion except the first bottom portion of the bottomed cylindrical connecting member is connected to said second bottom portion of the rotor Adjacent to a radially inner wall of the wall portion, the bearing assembly is the first bottomed portion that is the first flange-shaped seal portion, the cylindrical portion, and the second flange-shaped seal portion. Surrounded by a bottom.
In the present invention, the bottomed cylindrical connecting member is disposed such that the first bottomed portion which is the first flange-shaped seal portion is in contact with the bearing assembly, and the cylindrical portion is also the bearing. The rotor is disposed so as to contact the assembly, and the rotor is disposed such that the second bottomed portion which is the second flange-shaped seal portion is in contact with the bearing assembly, and the wall portion is also configured. Desirably, the bearing assembly is arranged so as to be in contact with the bearing assembly.
[0007]
The one end portion of the bearing assembly is formed on the stator side such that the first flange-like seal portion is located on the stator side, and the other end portion of the bearing assembly is opposite to the stator with respect to the bearing assembly. Preferably, it is formed on the opposite side of the stator with respect to the bearing assembly so as to be located on the side.
[0008]
The other end portion of the bearing assembly is formed on the stator side so that the second flange-shaped seal portion is positioned on the stator side, and the one end portion of the bearing assembly has the first flange-shaped seal portion of the stator with respect to the bearing assembly. It is also desirable to be formed on the opposite side of the stator with respect to the bearing assembly so that it is located on the opposite side.
[0009]
The bearing assembly includes an inner ring fixed to the outer peripheral surface of the central shaft, an outer ring fixed to the inner peripheral surface of the cylindrical connecting portion, and a rolling element disposed between the inner ring and the outer ring and held by the inner and outer rings. A cylindrical support portion that is radially inwardly formed on the body of the rotor that is spaced axially outward from the one end side of the bearing assembly of the outer ring, and the cylindrical support portion and the outer ring are provided between the cylindrical support portion and the outer ring. It is also desirable to provide an O-ring that is in pressure contact.
[0010]
The cylindrical connecting member is preferably U-shaped in the axial cross section between the sleeve and the first flange-like seal portion, and the distance between the first and second labyrinth seals is 0.005 mm to 0.02 mm. It is desirable that it is substantially 0.01 mm.
[0011]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, the present invention will be described based on embodiments with reference to the drawings.
[0012]
FIG. 1 is a first embodiment of a spindle motor of the present invention. As shown in FIG. 1, the spindle motor has a substrate 1, and a central shaft 2 extending upward in the figure is fixed to the substrate 1 at its lower end. Reference numeral 19 denotes a stator, which is composed of a laminated core (iron core) 20 and a coil 21 wound around its teeth, and is fixed to the substrate 1 so as to be coaxial with the central axis 2. The coil 21 is led out through a corresponding connection pin 22.
[0013]
The rotor 10 includes an annular body portion 23 and a thin cylindrical portion 24 whose diameter is increased in a skirt shape below the body portion 23 in FIG. An annular permanent magnet 25 surrounding the stator 19 is provided on the inner peripheral surface of the cylindrical portion 24.
[0014]
The inner peripheral surface 26 of the body portion 23 of the rotor 10 forms a cylindrical hole (center hole). The rotor 10 is provided at the body portion 23 so as to rotate around the central axis 2 via a cylindrical connecting member 6 described later.
[0015]
A pair of bearings 4 and 5 are fitted on the central shaft 2 with an annular spacer 12 interposed therebetween. In the case of illustration, these bearings 4 and 5 are ball bearings and include inner rings 4a and 5a, outer rings 4b and 5b, and balls 4c and 5c between the inner and outer rings, respectively. The inner rings 4a and 5a are fixed to the outer peripheral surface of the central shaft 2 on the inner peripheral surface. Here, the combination of the bearings 4 and 5 and the spacer 12 is referred to as a bearing assembly 27.
[0016]
A cylindrical connecting member 6 having a U-shaped axial section (that is, a cup shape) has a cylindrical sleeve portion 7 and one end thereof (the lower end in FIG. 1, ie, the end on the side of the stator 19) radially inwardly provided integrally therewith. And an annular flange-shaped seal portion (hereinafter referred to as “first flange-shaped seal portion”) 8. The bearing assembly 27 is press-fitted into the sleeve portion 7 so that the outer peripheral surfaces of the outer rings 4 b and 5 b of the bearings 4 and 5 are in contact with the inner peripheral surface of the sleeve portion 7. The first flange-shaped seal portion 8 has an upper surface (on the side opposite to the stator 19) in contact with an end surface on the lower side (that is, the stator 19 side) of the outer ring 4b of the bearing 4 on the lower side (that is, the stator 19 side). ing. Therefore, the bearing assembly 27 is fitted into the cylindrical connecting member 6. The tolerances of the outer diameter of the central shaft 2, the inner and outer diameters of the bearing assembly 27, and the inner and outer diameters of the sleeve portion of the cylindrical connecting member 6 are reduced to a fraction of one to one that is twice the desired labyrinth seal interval (for example, about 0.01 mm). / 10 (for example, 0.001 mm to 0.005 mm).
[0017]
The first flange-shaped seal portion 8 has a cylindrical center seal hole (hereinafter referred to as “first center seal hole”) 28. The first center seal hole 28 is formed so as to be coaxial with the center axis 2 with the above-mentioned tolerance, and its radius is substantially larger than the outer shape of the center axis 2 by a desired labyrinth seal interval (for example, 0 0.005 mm to 0.02 mm (generally 0.01 mm or the vicinity thereof).
[0018]
Accordingly, when the cylindrical connecting member 6 is assembled to the bearing assembly 27 attached to the central shaft 2, the first central seal hole 28 of the first flange-shaped seal portion 8 surrounding the central shaft 2 is interposed between the central shaft 2. A substantially equal gap is created over their entire circumference. The size of the gap corresponds to the labyrinth gap, and is, for example, 0.005 mm to 0.02 mm (generally 0.01 mm or the vicinity thereof). Accordingly, the first labyrinth seal 9 (a gap is exaggerated for better understanding in FIG. 1) that forms a substantially uniform gap between the central shaft 2 and the first flange-shaped seal portion 8 over the entire circumference. Are shown). For this reason, the first labyrinth seal 9 prevents oil from leaking or scattering downward from the bearing assembly 27 (on the side of the stator 19). The first labyrinth seal 9 prevents the wall surface of the first center seal hole 28 of the first flange-shaped seal portion 8 of the cylindrical connecting member 6 from contacting the outer peripheral surface of the center shaft 2.
[0019]
The rotor 10 is fitted on the outer peripheral surface of the sleeve portion 7 of the cylindrical connecting member 6 on the inner peripheral surface 26 of the body portion 23. The diameter of the inner peripheral surface is also formed to have a tolerance equivalent to the above tolerance. An annular flange-like seal portion (hereinafter referred to as a “second flange-like seal portion”) 13 is formed at the upper end portion (the end portion opposite to the stator 19) of the trunk portion 23 so as to be integral with the trunk portion 23 in the radial direction. ing. The lower surface of the second flange-shaped seal portion 13 (the surface on the side of the stator 19) is in pressure contact with the upper end surface (the side opposite to the stator 19) of the bearing 5 on the upper side (the side opposite to the stator 19). .
[0020]
Similar to the first flange-shaped seal portion 8, the second flange-shaped seal portion 13 has a cylindrical center seal hole (hereinafter referred to as “second seal hole”) 29. The second center seal hole 29 is also formed so as to be coaxial with the center axis 2 with the above-mentioned tolerance, and its radius is substantially larger than the outer shape of the center axis 2 by a desired labyrinth seal interval (for example, 0 0.005 mm to 0.02 mm (generally 0.01 mm or the vicinity thereof).
[0021]
Accordingly, when the rotor 10 and the cylindrical connecting member 6 are assembled to the central shaft 2, the entire circle between the second central seal hole 29 of the second flange-shaped seal portion 13 surrounding the central shaft 2 and the central shaft 2. There are substantially equal gaps around the circumference. The size of the gap corresponds to the labyrinth gap, and is, for example, 0.005 mm to 0.02 mm (generally 0.01 mm or the vicinity thereof). Therefore, the second labyrinth seal 11 (in FIG. 1, for the sake of better understanding, the gap is formed between the central shaft 2 and the first flange-shaped seal portion 8 to form a substantially uniform gap over the entire circumference. Exaggerated and large) is formed. For this reason, the second labyrinth seal 11 prevents oil from leaking or scattering upward from the bearing assembly 27 (on the side opposite to the stator 19). The second labyrinth seal 11 prevents the wall surface of the second central seal hole 29 of the second flange-shaped seal portion 13 of the rotor 10 from contacting the outer peripheral surface of the central shaft 2.
[0022]
FIG. 2 shows a second embodiment of the spindle motor of the present invention. In this embodiment, the first flange-like seal portion 8 and the second flange-like seal portion 13 of the first embodiment are alternately arranged, that is, the first labyrinth seal 9 and the second labyrinth seal 11 are alternately arranged. Has been.
[0023]
The second flange-shaped seal portion 13 is formed integrally with the rotor 10 on the lower end surface (the stator 19 side) of the body portion 23 of the rotor 10. Also, the cylindrical connecting member 6 has the sleeve portion 7 with the inner peripheral surface 26 of the rotor 10 and the outer peripheral surface of the bearing assembly 27 with the first flange-shaped seal portion 8 facing upward (that is, facing the opposite side of the stator 19). It is press-fitted between. By doing so, the wall surface of the first central seal hole 28 of the first flange-shaped seal portion 8 and the outer peripheral surface of the central shaft 2 and the wall surface of the second central seal hole 29 of the second flange-shaped seal portion 13 are obtained. A first labyrinth seal 9 and a second labyrinth seal 11 having a desired gap that is uniform over the entire circumference are formed between the first labyrinth seal 11 and the central axis 2. As a result, as in the first embodiment, oil leakage and scattering, and contact with the rotating shaft such as the rotor 10 and contact with the central shaft 2 are prevented. In the second embodiment, the other parts and structures are the same as those in the first embodiment, and therefore, the same parts are denoted by the same reference numerals, and description thereof is omitted.
[0024]
FIG. 3 shows a third embodiment of the present invention. In this embodiment, the bearing assembly 30 is formed on the inner ring 32 fitted and fixed to the reduced diameter portion 31 at the upper end portion of the central shaft 2 fixed to the substrate 1, and the lower outer peripheral surface of the central shaft 2. Between the annular groove 33, one outer ring 34 surrounding the central shaft 2, rolling elements (balls in the figure) 35 held between the inner ring 32 and the outer ring 34, and between the annular groove 33 and the outer ring 34 Rolling elements (balls in the figure) 36 held by the.
[0025]
As in the first embodiment, the cylindrical connecting member 6 includes a sleeve portion 7 and a first flange-like seal portion 8 formed at the lower end portion thereof. The outer peripheral surface of the sleeve portion 7 is fitted with the inner peripheral surface 26 of the body portion 23 of the rotor 10, and the inner lower end portion 17 of the inner peripheral surface of the sleeve portion 7 is fitted with the outer peripheral surface of the outer ring 34. Also in this case, the same first labyrinth seal 9 as that in the first embodiment is formed between the wall surface of the first center seal hole 28 of the first flange-shaped seal portion 8 and the outer peripheral surface of the center shaft 2.
[0026]
The rotor 10 is provided with a cylindrical support portion 37 that protrudes radially inward from the trunk portion 23 above the trunk portion 23. An annular locking portion 18 is formed on the inner wall of the cylindrical support portion 37 so as to protrude inward in the radial direction and to fit the rotor 10 to the outer ring 34. Moreover, the 2nd flange-shaped seal part 13 extended in radial direction from now on the upper end part of the cylindrical support part 37 is provided similarly to 1st Embodiment. Also in this case, the second labyrinth seal 11 similar to that in the first embodiment is provided between the wall surface of the first center seal hole 28 of the second flange-shaped seal portion 8 and the outer peripheral surface of the reduced diameter portion 31 of the center shaft 2. Is formed.
[0027]
An O that presses against the lower surface of the cylindrical support portion 37 and the upper end surface of the sleeve portion 7 in an annular space 15 formed between the lower surface of the cylindrical support portion 37 of the rotor 10 and the upper end surface of the sleeve portion 7 of the cylindrical connecting member 6. A ring 14 is provided. This O-ring 14 can prevent oil leakage or scattering from the bearing assembly 30 to the outer side in the radial direction of the rotor 10 that may occur around the outer ring 34. Since other parts and members are substantially the same as those in the first and second embodiments, these parts and members are denoted by the same numbers as those in the first and second embodiments, and description thereof is omitted. To do.
[0028]
Also in the third embodiment, the first labyrinth seal 9 and the second labyrinth seal 11 are formed evenly over the entire circumference and at a predetermined labyrinth seal interval, and thus are the same as the labyrinth seals of the first and second embodiments. Has a working effect. This is weighted by the sealing effect of the O-ring.
[0029]
【The invention's effect】
In the present invention, a seal portion provided at both ends of a bearing assembly and forming a labyrinth seal with a central shaft is formed integrally with a rotor and a cylindrical connecting member that holds the rotor in the bearing assembly. The center seal hole with high accuracy and the radius that is large by the predetermined labyrinth interval is formed, so there is no oil leakage or scattering from the bearing assembly, and the rotating member such as the rotor does not hit or contact the center shaft effective.
[Brief description of the drawings]
FIG. 1 is a longitudinal sectional view of a first embodiment of a spindle motor of the present invention.
FIG. 2 is a longitudinal sectional view of a second embodiment of the spindle motor of the present invention.
FIG. 3 is a longitudinal sectional view of the left half of a third embodiment of the spindle motor of the present invention.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 Board | substrate 2 Center axis | shaft 4 Bearing 5 Bearing 6 Cylindrical connection member 7 Sleeve part 8 1st flange-like seal part 9 1st labyrinth seal 10 Rotor 11 2nd labyrinth seal 13 2nd flange-like seal part 14 O-ring 18 Annular locking part 19 Stator 23 Body 24 Cylindrical part 26 Inner peripheral surface 27 Bearing assembly 28 First center seal hole 29 Second center seal hole 30 Bearing assembly 37 Cylindrical support part

Claims (7)

ステータを担持する基板と、該ステータと共軸に一端が該基板に接続された中心軸と、該ステータから軸方向にずれて形成された胴部を有し該中心軸を共軸に囲繞して配設されたロータと、該ロータの該胴部内に該ロータ及び該中心軸に共軸に配設された軸受アセンブリーと、
該ロータの該胴部と該軸受アセンブリーとの間に設けられ該ロータを該軸受アセンブリーに接続する有底円筒接続部材とを具備するスピンドルモータであって、
前記有底円筒接続部材は、その一部分である第１有底部として、
前記軸受アセンブリーの一端部の軸方向外側に、かつ、当該有底円筒接続部材の一端部に半径方向内向きに、当該有底円筒接続部材と一体的に形成された第１フランジ状シール部を備え、
前記第１フランジ状シール部は、
前記中心軸の半径よりも所定のラビリンスシール間隔だけ大きな半径を有し該中心軸に共軸に該中心軸を貫通させる第１シール穴を有し、
前記ロータは、その一部分である第２有底部として、
前記軸受アセンブリーの他端部の軸方向外側に、かつ、当該ロータの、前記有底円筒接続部材の前記一端部と反対側の端部に半径方向内向きに、当該ロータと一体的に形成された第２フランジ状シール部を備え、
前記第２フランジ状シール部は、
前記中心軸の半径よりも所定のラビリンスシール間隔だけ大きな半径を有し該中心軸に共軸に該中心軸を貫通させる第２シール穴を有し、
前記第１シール穴の壁面と前記中心軸の外周面との間及び前記第２シール穴の壁面と該中心軸の外周面との間に全周にわたって均一な前記ラビリンスシール間隔を有するラビリンスシールを形成して成り、
前記有底円筒接続部材における前記第１有底部を除く円筒部の半径方向外側の壁は、前記ロータの前記第２有底部に接続する壁部の半径方向内側の壁に隣接しており、
前記軸受アセンブリーは、
前記第１フランジ状シール部である前記第１有底部、前記円筒部及び前記第２フランジ状シール部である前記第２有底部によって囲まれている、
ことを特徴とするスピンドルモータ。A substrate carrying the stator; a central axis coaxially connected to the stator; a central axis having one end connected to the substrate; and a trunk formed offset from the stator in the axial direction. And a rotor assembly disposed coaxially with the rotor and the central axis in the body of the rotor;
The rotor is provided between the body portion and the bearing assembly of the rotor to a spindle motor having a bottomed cylindrical connecting member for connecting to the bearing assembly,
The bottomed cylindrical connecting member is a first bottomed portion which is a part thereof,
The axially outer end portion of the bearing assembly, and radially inward at one end of the bottomed cylindrical connecting member, the bottomed cylindrical connecting member and the first flange-like seal portion that is integrally formed With
The first flange-shaped seal portion is
Has a first sheet Lumpur hole through which the central axis in coaxially to the central axis has a larger radius by a predetermined labyrinth seal gap than the radius of said central axis,
The rotor is a second bottomed portion that is a part of the rotor,
Axially outwardly of the other end of the bearing assembly and of the rotor, the radially inward at an end opposite said one end portion of the bottomed cylindrical connecting member, the rotor and integrally formed a second flange-like seal portion that is,
The second flange-shaped seal portion is
A second sheet Lumpur hole through which the central axis in coaxially to the central axis has a larger radius by a predetermined labyrinth seal gap than the radius of said central axis,
A labyrinth seal having a uniform labyrinth seal interval over the entire circumference between the wall surface of the first seal hole and the outer peripheral surface of the central shaft and between the wall surface of the second seal hole and the outer peripheral surface of the central shaft. formed and Ri formed,
The radially outer wall of the cylindrical portion excluding the first bottomed portion in the bottomed cylindrical connecting member is adjacent to the radially inner wall of the wall portion connected to the second bottomed portion of the rotor,
The bearing assembly includes:
Surrounded by the first bottomed portion that is the first flange-shaped seal portion, the cylindrical portion, and the second bottomed portion that is the second flange-shaped seal portion,
A spindle motor characterized by that. 前記有底円筒接続部材は、The bottomed cylindrical connecting member is
その前記第１フランジ状シール部である前記第１有底部が前記軸受アセンブリーに接するように配置されていると共に、前記円筒部もまた当該軸受アセンブリーに接するように配置されており、  The first bottomed portion that is the first flange-shaped seal portion is disposed so as to contact the bearing assembly, and the cylindrical portion is also disposed so as to contact the bearing assembly,
かつ、  And,
前記ロータは、  The rotor is
その前記第２フランジ状シール部である前記第２有底部が前記軸受アセンブリーに接するように配置されていると共に、前記壁部もまた当該軸受アセンブリーに接するように配置されていることを特徴とする請求項１に記載のスピンドルモータ。  The second bottomed portion that is the second flange-shaped seal portion is disposed so as to contact the bearing assembly, and the wall portion is also disposed so as to contact the bearing assembly. The spindle motor according to claim 1. 前記軸受アセンブリーの前記一端部は、前記第１フランジ状シール部が前記ステータ側に位置するように該ステータ側に形成され、
該軸受アセンブリーの前記他端部は、前記第２フランジ状シール部が該軸受アセンブリーに関して該ステータの反対側に位置するように、該軸受アセンブリーに関して該ステータの反対側に形成されることを特徴とする請求項１又は２に記載のスピンドルモータ。The one end portion of the bearing assembly is formed on the stator side such that the first flange-shaped seal portion is located on the stator side,
The other end of the bearing assembly is formed on the opposite side of the stator with respect to the bearing assembly such that the second flange-like seal is located on the opposite side of the stator with respect to the bearing assembly. The spindle motor according to claim 1 or 2 . 前記軸受アセンブリーの前記他端部は、前記第２フランジ状シール部が前記ステータ側に位置するように該ステータ側に形成され、
該軸受アセンブリーの前記一端部は、前記第１フランジ状シール部が該軸受アセンブリーに関して該ステータの反対側に位置するように、該軸受アセンブリーに関して該ステータの反対側に形成されることを特徴とする請求項１又は２に記載のスピンドルモータ。The other end portion of the bearing assembly is formed on the stator side such that the second flange-shaped seal portion is located on the stator side,
The one end of the bearing assembly is formed on the opposite side of the stator with respect to the bearing assembly such that the first flange-like seal is located on the opposite side of the stator with respect to the bearing assembly. The spindle motor according to claim 1 or 2 . 前記軸受アセンブリーは、前記中心軸の外周面に固定される内輪と前記円筒接続部の内周面に固定される外輪と、該内輪と該外輪との間に配設されて該内外輪に保持される転動体を含み、
該外輪の、該軸受アセンブリーの前記一端側から軸方向外側に離間する前記ロータの前記胴部の部分に半径方向内側に向く円筒支持部を形成し、該円筒支持部と該外輪との間に該円筒支持部と該外輪とに圧接するＯリングを設けたことを特徴とする請求項３に記載のスピンドルモータ。The bearing assembly is disposed between the inner ring fixed to the outer peripheral surface of the central shaft, the outer ring fixed to the inner peripheral surface of the cylindrical connecting portion, and the inner ring and the outer ring, and is held by the inner and outer rings. Including rolling elements,
A cylindrical support portion facing radially inward is formed at a portion of the body portion of the rotor that is spaced axially outward from the one end side of the bearing assembly of the outer ring, and between the cylindrical support portion and the outer ring. The spindle motor according to claim 3 , wherein an O-ring is provided in pressure contact with the cylindrical support portion and the outer ring. 前記第１及び第２ラビリンスシールの間隔は０．００５ｍｍ乃至０．０２ｍｍであることを特徴とする請求項１乃至５のいずれかの１に記載のスピンドルモータ。 6. The spindle motor according to claim 1, wherein an interval between the first and second labyrinth seals is 0.005 mm to 0.02 mm. 前記第１及び第２ラビリンスシールの間隔は実質的に０．０１ｍｍであることを特徴とする請求項１乃至５のいずれかの１に記載のスピンドルモータ。 The spindle motor according to claim 1, wherein a distance between the first and second labyrinth seals is substantially 0.01 mm.
JP2000120481A 1999-04-23 2000-04-21 Spindle motor Expired - Fee Related JP3904179B2 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE1999118468 DE19918468C2 (en) 1999-04-23 1999-04-23 Spindle motor with labyrinth seal and sleeve for tension-free mounting of the bearings
DE19918468.2 1999-04-23

Publications (2)

Publication Number Publication Date
JP2000324746A JP2000324746A (en) 2000-11-24
JP3904179B2 true JP3904179B2 (en) 2007-04-11

Family

ID=7905621

Family Applications (1)

Application Number Title Priority Date Filing Date
JP2000120481A Expired - Fee Related JP3904179B2 (en) 1999-04-23 2000-04-21 Spindle motor

Country Status (2)

Country Link
JP (1) JP3904179B2 (en)
DE (1) DE19918468C2 (en)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE20119716U1 (en) 2001-12-05 2003-01-30 Minebea Kk Spindle motor for hard drives
DE102013105964B4 (en) * 2013-06-07 2021-12-02 Minebea Mitsumi Inc. Rotor with bearing device

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3613899B2 (en) * 1996-09-04 2005-01-26 日本精工株式会社 Method for reducing shaft runout of rolling bearing device and rolling bearing device with reduced shaft runout
DE19733566B4 (en) * 1997-08-02 2005-10-13 Minebea Co., Ltd. Spindle motor with sleeve

Also Published As

Publication number Publication date
JP2000324746A (en) 2000-11-24
DE19918468C2 (en) 2002-03-21
DE19918468A1 (en) 2000-11-02

Similar Documents

Publication Publication Date Title
US7391139B2 (en) Spindle motor and rotation apparatus
JP4959078B2 (en) Hydrodynamic bearing spindle motor
US7654744B2 (en) Fluid dynamic bearing mechanism for a motor
US6538354B2 (en) Spindle motor with toroidal sealing plates
TW200403397A (en) A bearing housing and seal assembly in such a bearing housing
JP2004248492A (en) Seal construction for motor, motor, and motor for automatic transmission of automobile
US20070206890A1 (en) Spindle motor having plurality of sealing portions
US20080063332A1 (en) Hydrodynamic bearing device and motor and recording and reproducing apparatus using the same
JP2960040B2 (en) Sealing device
JP3904179B2 (en) Spindle motor
JP3652732B2 (en) motor
JP2018119681A (en) Seal structure of rotary machine, rotary machine, and seal member
KR20130107506A (en) Fluid hydrodynamic bearing and spindle motor having the same
JP2000074052A (en) Compound bearing device, spindle motor provided with the same and swing arm assembly for hard disc drive device
JP3602707B2 (en) Hydrodynamic bearing motor
JP2003097725A (en) Sealing device
JP2007511194A (en) Fluid dynamic bearing motor
JP3386965B2 (en) Bearing structure of spindle motor
JP2001086691A (en) Spindle motor
JP2004108549A (en) Hydrodynamic bearing device
JP3984464B2 (en) Rotation drive
JPH075325Y2 (en) Sealing device
JP3201862B2 (en) Spindle motor
JPH0440044Y2 (en)
JP2002058201A (en) Spindle motor

Legal Events

Date Code Title Description
A621 Written request for application examination

Free format text: JAPANESE INTERMEDIATE CODE: A621

Effective date: 20040726

A977 Report on retrieval

Free format text: JAPANESE INTERMEDIATE CODE: A971007

Effective date: 20060830

A131 Notification of reasons for refusal

Free format text: JAPANESE INTERMEDIATE CODE: A131

Effective date: 20060905

A521 Written amendment

Free format text: JAPANESE INTERMEDIATE CODE: A523

Effective date: 20061027

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: 20070104

A61 First payment of annual fees (during grant procedure)

Free format text: JAPANESE INTERMEDIATE CODE: A61

Effective date: 20070105

R150 Certificate of patent or registration of utility model

Free format text: JAPANESE INTERMEDIATE CODE: R150

LAPS Cancellation because of no payment of annual fees