JP2000310220A - Dynamic pressure bearing - Google Patents
Dynamic pressure bearingInfo
- Publication number
- JP2000310220A JP2000310220A JP11121652A JP12165299A JP2000310220A JP 2000310220 A JP2000310220 A JP 2000310220A JP 11121652 A JP11121652 A JP 11121652A JP 12165299 A JP12165299 A JP 12165299A JP 2000310220 A JP2000310220 A JP 2000310220A
- Authority
- JP
- Japan
- Prior art keywords
- flange portion
- flange
- dynamic pressure
- shaft
- annular groove
- 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
Landscapes
- Sliding-Contact Bearings (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、シャフト部とフラ
ンジ部とからなるフランジ付シャフトを備える動圧軸受
に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a dynamic pressure bearing provided with a flanged shaft including a shaft portion and a flange portion.
【０００２】[0002]
【従来の技術】従来より、動圧軸受としては、スリーブ
にフランジ付シャフトを回転自在に嵌合したものがあ
る。このフランジ付シャフトは、図３に示すように、シ
ャフト部３２と、このシャフト部３２に嵌合して固定し
たフランジ部３３とからなり、シャフト部３２の外周面
またはスリーブ内周面にラジアル支持用の動圧発生溝４
６を設け、フランジ部３３の端面３３ａ,３３ｂにアキ
シャル支持用の動圧発生溝３５,３６を設けている。2. Description of the Related Art Conventionally, as a dynamic pressure bearing, there is a type in which a flanged shaft is rotatably fitted to a sleeve. As shown in FIG. 3, the flanged shaft includes a shaft portion 32 and a flange portion 33 fitted and fixed to the shaft portion 32, and is radially supported on the outer peripheral surface of the shaft portion 32 or the inner peripheral surface of the sleeve. Pressure generating groove 4 for
6 is provided, and dynamic pressure generating grooves 35 and 36 for axial support are provided on the end faces 33 a and 33 b of the flange portion 33.
【０００３】上記シャフト部３２の外周面には、フラン
ジ部３３の厚さより極く小さい幅で断面矩形の環状溝３
４を設け、上記フランジ付シャフト３１のシャフト部３
２とフランジ部３３との結合は次のように行っている。
すなわち、図４に示すように、その環状溝３４がフラン
ジ部３３の穴の内周面における幅方向の中央に位置する
ように、シャフト部３２にフランジ部３３を外嵌する。
そして、上記フランジ部３３を上金型３７と下金型３８
とで挟みこんでプレス加工して、フランジ部３３の端面
３３ａ,３３ｂに図３に示す動圧発生溝３５,３６を設け
る。そうすると、図３に示すように、上記シャフト部３
２の環状溝３４に対向するフランジ部３３の内周面が半
径方向内側に向かって膨出して、膨出変形部３９が、環
状溝３４に部分的に食い込んで、環状溝３４のエッジ部
３４ａに係合して、フランジ部３３をシャフト部３２に
対して固定する。On the outer peripheral surface of the shaft portion 32, an annular groove 3 having a width much smaller than the thickness of the flange portion 33 and having a rectangular cross section is provided.
4, the shaft portion 3 of the flanged shaft 31
The connection between 2 and the flange portion 33 is performed as follows.
That is, as shown in FIG. 4, the flange portion 33 is externally fitted to the shaft portion 32 such that the annular groove 34 is located at the center in the width direction on the inner peripheral surface of the hole of the flange portion 33.
Then, the flange 33 is connected to the upper mold 37 and the lower mold 38.
And press working to form dynamic pressure generating grooves 35 and 36 shown in FIG. 3 on the end faces 33 a and 33 b of the flange portion 33. Then, as shown in FIG.
The inner peripheral surface of the flange portion 33 facing the second annular groove 34 bulges inward in the radial direction, and the bulging deformation portion 39 partially bites into the annular groove 34 to form an edge portion 34 a of the annular groove 34. To fix the flange 33 to the shaft 32.
【０００４】[0004]
【発明が解決しようとする課題】ところが、上記従来の
動圧軸受のシャフト部３２とフランジ部３３との結合構
造では、フランジ部３３の極く一部が環状溝３４のエッ
ジ部３４ａに係合しているだけであるから、フランジ部
３３とシャフト部３２との結合が弱いという問題があ
る。However, in the conventional coupling structure of the shaft portion 32 and the flange portion 33 of the dynamic pressure bearing, only a part of the flange portion 33 is engaged with the edge portion 34a of the annular groove 34. However, there is a problem that the connection between the flange portion 33 and the shaft portion 32 is weak.
【０００５】そこで、本発明の目的は、シャフト部にフ
ランジ部を簡単に強固に固定できるフランジ付シャフト
を有する動圧軸受を提供することにある。An object of the present invention is to provide a dynamic pressure bearing having a flanged shaft which can easily and firmly fix the flange to the shaft.
【０００６】[0006]
【課題を解決するための手段】上記目的を達成するた
め、請求項１の動圧軸受は、シャフト部と、上記シャフ
ト部に嵌合して固定したフランジ部とからなるフランジ
付シャフトを備える動圧軸受において、上記シャフト部
の外周面に、上記フランジ部の厚さに略等しい幅で断面
円弧状の環状溝を設け、上記環状溝と上記フランジ部の
内周面とが上記フランジ部の厚み方向の略全幅にわたっ
て互いに押圧していることを特徴としている。According to a first aspect of the present invention, there is provided a dynamic pressure bearing having a flanged shaft comprising a shaft portion and a flange portion fitted and fixed to the shaft portion. In the pressure bearing, on the outer peripheral surface of the shaft portion, an annular groove having an arc-shaped cross section having a width substantially equal to the thickness of the flange portion is provided, and the annular groove and the inner peripheral surface of the flange portion have a thickness of the flange portion. It is characterized in that they are pressed against each other over substantially the entire width in the direction.
【０００７】上記請求項１の動圧軸受によれば、上記シ
ャフト部の外周面に、上記フランジ部の厚さに略等しい
幅で断面円弧状の環状溝が設けられ、断面円弧状の環状
溝とフランジ部の内周面とがフランジ部の厚み方向の全
幅にわたって互いに押圧し、かつ、係合している。した
がって、上記シャフト部とフランジ部との連結は強固で
あって、フランジ部に対してシャフト部が空回りするこ
とはない。According to the dynamic pressure bearing of the first aspect, an annular groove having an arc-shaped cross section with a width substantially equal to the thickness of the flange portion is provided on the outer peripheral surface of the shaft portion. And the inner peripheral surface of the flange portion press and engage with each other over the entire width in the thickness direction of the flange portion. Accordingly, the connection between the shaft portion and the flange portion is strong, and the shaft portion does not idle with respect to the flange portion.
【０００８】また、請求項２の動圧軸受は、請求項１の
動圧軸受において、上記環状溝の深さが５〜３０μｍに
設定されていることを特徴としている。The dynamic pressure bearing of claim 2 is characterized in that, in the dynamic pressure bearing of claim 1, the depth of the annular groove is set to 5 to 30 μm.
【０００９】上記請求項２の動圧軸受によれば、フラン
ジ部の端面に動圧発生溝を設けるためにフランジ部にプ
レス加工を施した場合に、断面円弧状の環状溝の深さが
５〜３０μｍに設定されているから、フランジ部の内周
面は、半径方向内側に向かって膨出して、シャフト部の
断面円弧状の環状溝に全面わたって強く押圧する。した
がって、上記シャフト部の環状溝とフランジ部の内周面
とがフランジ部の厚み方向の全幅にわたって互いに押圧
し、かつ、係合しているので、シャフト部とフランジ部
との連結は強固で、それらが相対回転することはない。According to the second aspect of the present invention, when the flange is press-worked to provide a dynamic pressure generating groove on the end face of the flange, the annular groove having an arc-shaped cross section has a depth of 5 mm. Since the thickness is set to ３０30 μm, the inner peripheral surface of the flange portion bulges inward in the radial direction, and strongly presses the entire surface of the circular groove having an arc-shaped cross section of the shaft portion. Therefore, the annular groove of the shaft portion and the inner peripheral surface of the flange portion press against each other over the entire width in the thickness direction of the flange portion, and are engaged, so that the connection between the shaft portion and the flange portion is strong, They do not rotate relative to each other.
【００１０】また、上記環状溝の深さが５μｍ未満に設
定された場合、プレス加工されたフランジ部の内周面が
断面円弧状の環状溝の深さより遥かにつまり過度に半径
方向内側に向かって膨出する。その結果、上記フランジ
部の内周面と環状溝との押圧力が過度になって、フラン
ジ部およびシャフト部に歪みが生じることが分かった。When the depth of the annular groove is set to less than 5 μm, the inner peripheral surface of the pressed flange portion is far more than the depth of the circular groove having an arc-shaped cross section, that is, excessively inward in the radial direction. Bulge out. As a result, it was found that the pressing force between the inner peripheral surface of the flange portion and the annular groove was excessive, and the flange portion and the shaft portion were distorted.
【００１１】また、上記環状溝の深さが３０μｍを越え
るように設定された場合、フランジ部の内周面と環状溝
との間に隙間が生じるから、あるいはそれらの押圧力が
小さくなって、フランジ部をシャフト部に対して確実に
固定できないことが分かった。If the depth of the annular groove is set to exceed 30 μm, a gap is formed between the inner peripheral surface of the flange portion and the annular groove, or the pressing force thereof is reduced. It was found that the flange could not be securely fixed to the shaft.
【００１２】また、請求項３の動圧軸受は、請求項１ま
たは２の動圧軸受において、上記フランジ部の端面にプ
レスにより動圧発生溝が形成されていることを特徴とし
ている。A dynamic pressure bearing according to a third aspect of the present invention is the dynamic pressure bearing according to the first or second aspect, wherein a dynamic pressure generating groove is formed on an end face of the flange portion by pressing.
【００１３】上記請求項３の動圧軸受よれば、請求項１
または２の動圧軸受において、上記フランジ部の端面に
プレスにより動圧発生溝を形成すると、フランジ部の内
周面が半径方向内側に向かって膨出して、断面円弧状の
環状溝とフランジ部の内周面とがフランジ部の厚み方向
の全幅にわたって互いに押圧し、かつ、係合する。した
がって、上記シャフト部にフランジ部を簡単に強固に固
定できる。[0013] According to the dynamic pressure bearing of the third aspect, the first aspect.
In the dynamic pressure bearing of the second aspect, when the dynamic pressure generating groove is formed by pressing on the end face of the flange, the inner peripheral surface of the flange bulges inward in the radial direction, and the annular groove having an arc-shaped cross section and the flange are formed. Are pressed against and engaged with each other over the entire width of the flange portion in the thickness direction. Therefore, the flange portion can be easily and firmly fixed to the shaft portion.
【００１４】[0014]
【発明の実施の形態】以下、本発明の動圧軸受を図示の
実施の形態により詳細に説明する。BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a perspective view of a hydrodynamic bearing according to the present invention.
【００１５】図１,２は本発明の実施の一形態の動圧軸
受が有するフランジ付シャフトの断面図である。このフ
ランジ付シャフトは、図１に示すように、シャフト部２
と、このシャフト部２に嵌合して固定したフランジ部３
とからなる。なお、上記シャフト部２はステンレス鋼で
製作し、フランジ部３は鋼合金で製作したものである。FIGS. 1 and 2 are cross-sectional views of a flanged shaft included in a dynamic pressure bearing according to an embodiment of the present invention. As shown in FIG.
And a flange portion 3 fitted and fixed to the shaft portion 2
Consists of The shaft 2 is made of stainless steel, and the flange 3 is made of a steel alloy.
【００１６】また、上記シャフト部２の外周面には、ラ
ジアル方向支持用の動圧発生溝１６を形成すると共に、
フランジ部３の厚さに等しい幅で断面円弧状の環状溝４
を形成している。この環状溝４の深さｄを５〜３０μｍ
例えば１５μｍに設定している。また、上記フランジ部
３の中心の断面つつみ形状の穴２０を上記シャフト部２
の断面円弧状の環状溝４に密に嵌合している。つまり、
上記断面円弧状の環状溝４の周面と上記穴２０の内周面
とが略全面にわたって互いに押圧し、かつ、係合して、
上記シャフト部２とフランジ部４とを強固に固定してい
る。また、上記フランジ部３の端面３ａ,３ｂにアキシ
ャル方向支持用の動圧発生溝５,６を形成している。In addition, a dynamic pressure generating groove 16 for supporting in the radial direction is formed on the outer peripheral surface of the shaft portion 2.
An annular groove 4 having a width equal to the thickness of the flange portion 3 and having an arc-shaped cross section.
Is formed. The depth d of the annular groove 4 is 5 to 30 μm
For example, it is set to 15 μm. Further, a hole 20 having a cross section at the center of the flange portion 3 is inserted into the shaft portion 2.
Are closely fitted in the annular groove 4 having an arc-shaped cross section. That is,
The peripheral surface of the annular groove 4 having an arc-shaped cross section and the inner peripheral surface of the hole 20 press and engage with each other over substantially the entire surface,
The shaft portion 2 and the flange portion 4 are firmly fixed. Further, dynamic pressure generating grooves 5 and 6 for supporting in the axial direction are formed on the end surfaces 3a and 3b of the flange portion 3.
【００１７】上記フランジ付シャフトのシャフト部２と
フランジ部３との結合は以下のように行っている。ま
ず、図２に示すように、フランジ部３の素材である円板
２５の中心の円形穴２６の内周面と断面円弧状の環状溝
４とがフランジ部３の厚み方向の全幅にわたって対向す
るように、シャフト部２に円板２５を外嵌する。そし
て、上記円板２５を図４に示す上金型３７および下金型
３８と同じ上金型,下金型(図示せず)で挟んでプレス加
工して、円板２５を図１に示すフランジ部３に加工す
る。このフランジ部３の端面３ａ,３ｂには、動圧発生
溝５,６が形成されると共に、上記シャフト部２の断面
円弧状の環状溝４に対向するフランジ部３の内周面が半
径方向内側に向かって膨出して、フランジ部３の膨出変
形部７とシャフト部２の環状溝４とがフランジ部３の厚
み方向の全幅にわたって互いに押圧している。The connection between the shaft portion 2 and the flange portion 3 of the flanged shaft is performed as follows. First, as shown in FIG. 2, the inner peripheral surface of the circular hole 26 at the center of the disk 25, which is the material of the flange portion 3, and the annular groove 4 having an arc-shaped cross section are opposed to each other over the entire width of the flange portion 3 in the thickness direction. The disk 25 is externally fitted to the shaft portion 2 as described above. Then, the disk 25 is sandwiched between the same upper and lower dies (not shown) as the upper die 37 and the lower die 38 shown in FIG. 4 and pressed to form the disk 25 shown in FIG. The flange 3 is processed. Dynamic pressure generating grooves 5 and 6 are formed on the end faces 3 a and 3 b of the flange portion 3, and the inner peripheral surface of the flange portion 3 that faces the annular groove 4 having a circular cross section of the shaft portion 2 is formed in a radial direction. The flange portion 3 swells inward, and the swelling deformation portion 7 of the flange portion 3 and the annular groove 4 of the shaft portion 2 press each other over the entire width of the flange portion 3 in the thickness direction.
【００１８】このように、上記フランジ部３の端面３
ａ,３ｂにプレス加工により動圧発生溝５,６を形成する
ことによって、フランジ部３の膨出変形部７とシャフト
部２の環状溝４とがフランジ部３の厚み方向の全幅にわ
たって食い込み、つまり、全幅にわたって互いに押圧
し、かつ、係合するので、フランジ部３をシャフト部２
に対してしっかり連結できる。したがって、上記フラン
ジ部３に対してシャフト部２が空回りすることもない。
また、このように、上記フランジ部３のアキシャル支持
用の動圧発生溝５,６をプレス加工で形成するだけで、
フランジ部３の内周面が膨出して断面円弧状の溝４の全
幅にわたって食い込むので、フランジ部３をシャフト部
２に簡単に強固に固定できる。As described above, the end face 3 of the flange 3
By forming the dynamic pressure generating grooves 5 and 6 in the a and 3b by press working, the bulging deformation portion 7 of the flange portion 3 and the annular groove 4 of the shaft portion 2 bite over the entire width of the flange portion 3 in the thickness direction, That is, the flange 3 is pressed and engaged with each other over the entire width, so that the flange 3 is
Can be securely connected to Therefore, the shaft portion 2 does not idle with respect to the flange portion 3.
Further, in this manner, the dynamic pressure generating grooves 5 and 6 for axial support of the flange portion 3 are simply formed by press working.
Since the inner peripheral surface of the flange portion 3 bulges and bites over the entire width of the groove 4 having an arc-shaped cross section, the flange portion 3 can be easily and firmly fixed to the shaft portion 2.
【００１９】また、上記環状溝４の深さｄを５〜３０μ
ｍに設定しているので、シャフト部２の環状溝４とフラ
ンジ部３の変形膨出部７とがフランジ部３の厚み方向の
全幅にわたって互いに強く押圧し、かつ、係合し、しか
も、フランジ部３の端面３ａ,３ｂが反ったり、湾曲し
たりすることがない。The annular groove 4 has a depth d of 5 to 30 μm.
m, the annular groove 4 of the shaft portion 2 and the deformed bulging portion 7 of the flange portion 3 strongly press each other over the entire width of the flange portion 3 in the thickness direction, and engage with each other. The end faces 3a and 3b of the portion 3 do not warp or curve.
【００２０】もし、上記環状溝４の深さｄを５μｍ未満
に設定すると、プレス加工されたフランジ部３の内周面
が断面円弧状の環状溝４の深さｄより過度に半径方向内
側に向かって膨出するため、上記フランジ部３の内周面
と環状溝４との押圧力が過度になって、フランジ部３お
よびシャフト部２に反りや湾曲が生じることが分かっ
た。If the depth d of the annular groove 4 is set to less than 5 μm, the inner peripheral surface of the pressed flange portion 3 is excessively radially inward of the depth d of the annular groove 4 having an arc-shaped cross section. It has been found that the bulges toward the flange portion 3 and the shaft portion 2 due to excessive pressing force between the inner peripheral surface of the flange portion 3 and the annular groove 4.
【００２１】また、もし、上記環状溝の深さを３０μｍ
を越えるように設定すると、フランジ部３の内周面と環
状溝４との間に隙間が生じるか、あるいはそれらの押圧
力が小さくなって、フランジ部３をシャフト部２に対し
て確実に固定できないことが分かった。If the annular groove has a depth of 30 μm
When it is set to exceed, a gap is formed between the inner peripheral surface of the flange portion 3 and the annular groove 4 or the pressing force thereof is reduced, and the flange portion 3 is securely fixed to the shaft portion 2. I knew I couldn't.
【００２２】上記実施の形態では、シャフト部４をステ
ンレス鋼で製作したが、工具鋼で製作してもよい。In the above embodiment, the shaft portion 4 is made of stainless steel, but may be made of tool steel.
【００２３】[0023]
【発明の効果】以上より明らかなように、請求項１の発
明の動圧軸受は、シャフト部の外周面に、フランジ部の
厚さに略等しい幅で断面円弧状の環状溝を設けて、断面
円弧状の環状溝とフランジ部の内周面とをフランジ部の
厚み方向の略全幅にわたって互いに押圧し、かつ、係合
しているので、シャフト部とフランジ部との連結を強固
にできる。As is apparent from the above, the dynamic pressure bearing according to the first aspect of the present invention is provided with an annular groove having a width substantially equal to the thickness of the flange portion and an arc-shaped cross section on the outer peripheral surface of the shaft portion. Since the annular groove having an arcuate cross section and the inner peripheral surface of the flange portion are pressed against and engaged with each other over substantially the entire width in the thickness direction of the flange portion, the connection between the shaft portion and the flange portion can be strengthened.
【００２４】また、請求項２の発明の動圧軸受は、請求
項１の動圧軸受において、上記環状溝の深さを５〜３０
μｍに設定しているので、フランジ部の内周面は、シャ
フト部の断面円弧状の環状溝に全面にわたって食い込
み、シャフト部にフランジ部を確実に強固に固定でき、
しかも、フランジ部の端面に反りや湾曲が生じることは
ない。According to a second aspect of the present invention, in the hydrodynamic bearing of the first aspect, the annular groove has a depth of 5 to 30.
μm, the inner peripheral surface of the flange part bites into the annular groove of the cross section of the shaft part over the entire surface, and the flange part can be securely fixed firmly to the shaft part.
In addition, the end face of the flange does not warp or curve.
【００２５】また、請求項３の発明の動圧軸受は、請求
項１または２の動圧軸受において、上記フランジ部の端
面にプレスにより動圧発生溝を形成しているので、フラ
ンジ部の端面に動圧発生溝を形成する加工を行うと同時
にシャフト部の断面円弧状の溝にフランジ部の内周面を
膨出させて食い込ませる加工を行うことができる。According to a third aspect of the present invention, there is provided the dynamic pressure bearing according to the first or second aspect, wherein the dynamic pressure generating groove is formed on the end face of the flange by pressing. At the same time as forming the dynamic pressure generating groove at the same time, the inner peripheral surface of the flange portion can be bulged into the groove having an arc-shaped cross section of the shaft portion.
【図面の簡単な説明】[Brief description of the drawings]
【図１】 図１は本発明の実施の一形態の動圧軸受のフ
ランジ付シャフトの断面図である。FIG. 1 is a sectional view of a flanged shaft of a dynamic pressure bearing according to an embodiment of the present invention.
【図２】 図２は上記フランジ付シャフトのフランジ部
にアキシャル方向支持用の動圧発生溝を形成する前の状
態を示す図である。FIG. 2 is a view showing a state before a dynamic pressure generating groove for supporting in an axial direction is formed in a flange portion of the flanged shaft.
【図３】 図３は従来の動圧軸受のフランジ付シャフト
の断面図である。FIG. 3 is a sectional view of a flanged shaft of a conventional dynamic pressure bearing.
【図４】 図４は上記フランジ付シャフトのフランジ部
にアキシャル方向支持用の動圧発生環状溝を形成する前
の状態を示す図である。FIG. 4 is a view showing a state before a dynamic pressure generating annular groove for supporting in an axial direction is formed on a flange portion of the flanged shaft.
２ シャフト部 ３ フランジ部 ４ 環状溝 ５,６ 動圧発生溝 ｄ 環状溝の深さ 2 Shaft 3 Flange 4 Annular groove 5, 6 Dynamic pressure generating groove d Depth of annular groove
Claims (3)
て固定したフランジ部とからなるフランジ付シャフトを
備える動圧軸受において、 上記シャフト部の外周面に、上記フランジ部の厚さに略
等しい幅で断面円弧状の環状溝を設け、 上記環状溝と上記フランジ部の内周面とが上記フランジ
部の厚み方向の略全幅にわたって互いに押圧しているこ
とを特徴とする動圧軸受。1. A dynamic pressure bearing provided with a flanged shaft including a shaft portion and a flange portion fitted and fixed to the shaft portion, wherein a thickness of the flange portion is substantially equal to an outer peripheral surface of the shaft portion. An annular groove having an equal width and an arcuate cross section is provided, and the annular groove and the inner peripheral surface of the flange portion are pressed against each other over substantially the entire width in the thickness direction of the flange portion.
を特徴とする動圧軸受。2. The dynamic pressure bearing according to claim 1, wherein a depth of the annular groove is set to 5 to 30 μm.
いて、 上記フランジ部の端面にプレスにより動圧発生溝が形成
されていることを特徴とする動圧軸受。3. The dynamic pressure bearing according to claim 1, wherein a dynamic pressure generating groove is formed on an end surface of the flange portion by pressing.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP12165299A JP3961151B2 (en) | 1999-04-28 | 1999-04-28 | Hydrodynamic bearing |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP12165299A JP3961151B2 (en) | 1999-04-28 | 1999-04-28 | Hydrodynamic bearing |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JP2000310220A true JP2000310220A (en) | 2000-11-07 |
| JP3961151B2 JP3961151B2 (en) | 2007-08-22 |
Family
ID=14816559
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP12165299A Expired - Fee Related JP3961151B2 (en) | 1999-04-28 | 1999-04-28 | Hydrodynamic bearing |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3961151B2 (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1251626A2 (en) * | 2001-04-17 | 2002-10-23 | Minebea Co., Ltd. | Bearing device and spindle motor provided with the bearing device |
| DE20211203U1 (en) * | 2002-07-24 | 2003-07-31 | Minebea Co.,Ltd., Kitasaku, Nagano | Hydrodynamic thrust bearing |
| DE20211064U1 (en) * | 2002-07-22 | 2003-08-07 | Minebea Co.,Ltd., Kitasaku, Nagano | Hydrodynamic thrust bearing |
| DE20211066U1 (en) * | 2002-07-22 | 2003-09-18 | Minebea Co.,Ltd., Kitasaku, Nagano | Hydrodynamic thrust bearing |
| DE20211065U1 (en) * | 2002-07-22 | 2003-12-04 | Minebea Co., Ltd., Kitasaku | Hydrodynamic thrust bearing |
-
1999
- 1999-04-28 JP JP12165299A patent/JP3961151B2/en not_active Expired - Fee Related
Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1251626A2 (en) * | 2001-04-17 | 2002-10-23 | Minebea Co., Ltd. | Bearing device and spindle motor provided with the bearing device |
| EP1251626A3 (en) * | 2001-04-17 | 2005-11-16 | Minebea Co., Ltd. | Bearing device and spindle motor provided with the bearing device |
| US7176594B2 (en) | 2001-04-17 | 2007-02-13 | Minebea Co., Ltd. | Motor |
| DE20211064U1 (en) * | 2002-07-22 | 2003-08-07 | Minebea Co.,Ltd., Kitasaku, Nagano | Hydrodynamic thrust bearing |
| DE20211066U1 (en) * | 2002-07-22 | 2003-09-18 | Minebea Co.,Ltd., Kitasaku, Nagano | Hydrodynamic thrust bearing |
| DE20211065U1 (en) * | 2002-07-22 | 2003-12-04 | Minebea Co., Ltd., Kitasaku | Hydrodynamic thrust bearing |
| US6851860B2 (en) | 2002-07-22 | 2005-02-08 | Minebea Co., Ltd. | Hydrodynamic thrust bearing |
| US6945696B2 (en) | 2002-07-22 | 2005-09-20 | Minebea Co., Ltd. | Hydrodynamic thrust bearing |
| US6984069B2 (en) | 2002-07-22 | 2006-01-10 | Mineabea Co., Ltd. | Hydrodynamic thrust bearing |
| DE20211203U1 (en) * | 2002-07-24 | 2003-07-31 | Minebea Co.,Ltd., Kitasaku, Nagano | Hydrodynamic thrust bearing |
| US6939048B2 (en) | 2002-07-24 | 2005-09-06 | Minebea Co., Ltd | Hydrodynamic thrust bearing |
Also Published As
| Publication number | Publication date |
|---|---|
| JP3961151B2 (en) | 2007-08-22 |
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