JPS6364647B2 - - Google Patents
Info
- Publication number
- JPS6364647B2 JPS6364647B2 JP57128342A JP12834282A JPS6364647B2 JP S6364647 B2 JPS6364647 B2 JP S6364647B2 JP 57128342 A JP57128342 A JP 57128342A JP 12834282 A JP12834282 A JP 12834282A JP S6364647 B2 JPS6364647 B2 JP S6364647B2
- Authority
- JP
- Japan
- Prior art keywords
- thrust
- shaft body
- thrust bearing
- bearing
- radial
- 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
Links
- 239000000314 lubricant Substances 0.000 claims description 12
- 230000002093 peripheral effect Effects 0.000 description 14
- 238000006073 displacement reaction Methods 0.000 description 4
- 238000000034 method Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 1
- 239000004519 grease Substances 0.000 description 1
- 238000007373 indentation Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000005096 rolling process Methods 0.000 description 1
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
- F16C17/00—Sliding-contact bearings for exclusively rotary movement
- F16C17/04—Sliding-contact bearings for exclusively rotary movement for axial load only
- F16C17/08—Sliding-contact bearings for exclusively rotary movement for axial load only for supporting the end face of a shaft or other member, e.g. footstep bearings
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Sliding-Contact Bearings (AREA)
Description
【発明の詳細な説明】
この発明は回転中のスラスト負荷能力を一定に
保つ動圧形流体軸受装置に関する。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a hydrodynamic bearing device that maintains a constant thrust load capacity during rotation.
従来の動圧形流体軸受装置は第1図に示すよう
に、ハウジング1に設けた円筒状孔2は円筒状の
ラジアル内面3と平面状のスラスト軸受面4とを
有し、前記円筒状孔2に配設した軸体5は動圧発
生用のみぞ6を有する円筒状のラジアル外面7と
凸形円すい状のスラスト端面8とを有している。
前記動圧発生用のみぞ6は軸体5の回転中にラジ
アル内面3とラジアル外面7との間のすきま内の
潤滑剤をスラスト軸受面4の外周部とスラスト端
面8の外周部との間の圧力室11へ流出する作用
を行う。前記ハウジング1には軸体5の回転中に
圧力室11からハウジング1の上面に通ずる循環
穴12が設けられている。 In a conventional hydrodynamic bearing device, as shown in FIG. 1, a cylindrical hole 2 provided in a housing 1 has a cylindrical radial inner surface 3 and a planar thrust bearing surface 4. The shaft body 5 disposed at 2 has a cylindrical radial outer surface 7 having a groove 6 for generating dynamic pressure and a convex conical thrust end surface 8.
The groove 6 for generating dynamic pressure transfers the lubricant in the gap between the radial inner surface 3 and the radial outer surface 7 between the outer periphery of the thrust bearing surface 4 and the outer periphery of the thrust end surface 8 during rotation of the shaft body 5. The effect of flowing out to the pressure chamber 11 is performed. The housing 1 is provided with a circulation hole 12 that communicates from the pressure chamber 11 to the upper surface of the housing 1 during rotation of the shaft body 5.
従つて軸体5が回転して浮上すると、圧力室1
1内の潤滑剤が循環穴12を通つて軸体5の外周
面に流出し、軸体5の浮上量はほぼ一定に保たれ
る。 Therefore, when the shaft body 5 rotates and floats, the pressure chamber 1
The lubricant in the shaft body 1 flows out to the outer peripheral surface of the shaft body 5 through the circulation hole 12, and the flying height of the shaft body 5 is kept almost constant.
このような軸受をフラツト・モータ等に使用す
る場合は、軸体5に固定したロータとハウジング
1に固定したステータとが軸方向の微小すきまを
介して平面で対向しているのでロータとステータ
との相対変位を小さくすることが望まれる。しか
し循環穴12をラジアル外面とスラスト端面との
境介部13の近傍に精度良く設けることは加工上
むずかしいので軸体5の浮上量即ちロータとステ
ータとの相対変位を小さくおさえることは困難で
ある。 When such a bearing is used in a flat motor, etc., the rotor fixed to the shaft body 5 and the stator fixed to the housing 1 face each other on a plane with a small gap in the axial direction, so that the rotor and stator are It is desirable to reduce the relative displacement of However, since it is difficult to form the circulation hole 12 with high accuracy near the interface 13 between the radial outer surface and the thrust end surface, it is difficult to suppress the flying height of the shaft body 5, that is, the relative displacement between the rotor and the stator. .
またロータとステータとの間に働く吸引力はス
ラスト荷重として働くのでスラスト荷重はかなり
厳しい。しかし軸体5の停止時にはスラスト端面
8とスラスト軸受面4とが点接触するので最大接
触面圧が大きく、スラスト軸受面4に圧こんが生
ずるおそれがある。 Also, the suction force acting between the rotor and stator acts as a thrust load, so the thrust load is quite severe. However, when the shaft body 5 is stopped, the thrust end face 8 and the thrust bearing surface 4 come into point contact, so the maximum contact surface pressure is large, and there is a possibility that an indentation may occur in the thrust bearing surface 4.
この発明は前述の各欠点を除去することを目的
とする。 The invention aims to eliminate each of the aforementioned drawbacks.
次にこの発明の実施例を図面に基いて説明す
る。第2図において、ハウジング21は一つの部
材から構成され、このハウジング21には円筒状
孔22が設けられている。前記円筒状孔22の開
口部は円筒状孔22より大径の大径孔23となつ
ており、また円筒状孔22の内周面には円筒状の
ラジアル内面24が設けられている。前記円筒状
孔22の底面には平面状のスラスト軸受面25が
設けられ、また円筒状孔22には軸体26が配設
されている。前記軸体26の外周面にはラジアル
内面24と対向して共働する円筒状のラジアル外
面27が設けられ、このラジアル外面27には第
3図に示すようにスパイラル状の動圧発生用のみ
ぞ28が設けられている。前記軸体26の一方の
端面にはスラスト軸受面25と対向して共働する
截頭円すい面状のスラスト端面31が設けられ、
このスラスト端面31の外周部とスラスト軸受面
25の外周部との間は圧力室32となつている。 Next, embodiments of the present invention will be described based on the drawings. In FIG. 2, a housing 21 is constructed from one member, and a cylindrical hole 22 is provided in the housing 21. The opening of the cylindrical hole 22 is a large diameter hole 23 having a larger diameter than the cylindrical hole 22, and a cylindrical radial inner surface 24 is provided on the inner peripheral surface of the cylindrical hole 22. A planar thrust bearing surface 25 is provided on the bottom surface of the cylindrical hole 22, and a shaft body 26 is provided in the cylindrical hole 22. A cylindrical radial outer surface 27 that faces and cooperates with the radial inner surface 24 is provided on the outer circumferential surface of the shaft body 26, and as shown in FIG. A groove 28 is provided. A truncated conical thrust end face 31 is provided on one end face of the shaft body 26 and faces and cooperates with the thrust bearing surface 25.
A pressure chamber 32 is formed between the outer periphery of the thrust end face 31 and the outer periphery of the thrust bearing surface 25.
前記動圧発生用のみぞ28は軸受の作動中即ち
軸体26とハウジング21との少なくとも一方の
回転中にラジアル内面24とラジアル外面27と
の間のすきま内の潤滑剤を圧力室32へ流出する
作用を行う。前記スラスト端面31の中央部には
軸方向に循環穴33が設けられ、また軸体26に
は軸体26の作動中に循環穴33から大径孔23
に通ずる連通穴34が設けられている。従つて循
環穴33は軸体26の外周面に通じている。前記
スラスト端面31は軸体26の静止時にスラスト
軸受面25と直接に接触する環状の接触面35を
循環穴33の周囲に有しており、また円筒状孔2
2には油、グリース、又は空気等の潤滑剤が存在
している。 The groove 28 for generating dynamic pressure allows the lubricant in the gap between the radial inner surface 24 and the radial outer surface 27 to flow out into the pressure chamber 32 during the operation of the bearing, that is, during rotation of at least one of the shaft body 26 and the housing 21. perform the action of A circulation hole 33 is provided in the central part of the thrust end face 31 in the axial direction, and the large diameter hole 23 is formed in the shaft body 26 from the circulation hole 33 during operation of the shaft body 26.
A communication hole 34 communicating with is provided. Therefore, the circulation hole 33 communicates with the outer peripheral surface of the shaft body 26. The thrust end face 31 has an annular contact surface 35 around the circulation hole 33 that directly contacts the thrust bearing surface 25 when the shaft body 26 is at rest, and also has an annular contact surface 35 around the circulation hole 33.
2, a lubricant such as oil, grease, or air is present.
以上のような構成の動圧形流体軸受装置は軸体
26の静止時にスラスト軸受面25とスラスト端
面31とが接触しているが、軸体26が回転する
と動圧発生用のみぞ28のポンピング作用によつ
て大径孔23内の潤滑剤が圧力室32に流入し、
軸体26が浮上する。前記軸体26が浮上すると
循環穴33が圧力室32に開口し、圧力室32内
の潤滑剤は循環穴33および連通穴34を通つて
大径孔23に流出する。この場合圧力室32内の
潤滑剤の圧力は軸体26の浮上量の変化によつて
調整されてほぼ一定であり、一定のスラスト負荷
能力が得られると共に軸体26の浮上量を小さく
おさえることができる。 In the hydrodynamic bearing device configured as described above, the thrust bearing surface 25 and the thrust end face 31 are in contact when the shaft body 26 is stationary, but when the shaft body 26 rotates, the groove 28 for generating dynamic pressure is pumped. Due to this action, the lubricant in the large diameter hole 23 flows into the pressure chamber 32,
The shaft body 26 floats up. When the shaft body 26 floats up, the circulation hole 33 opens into the pressure chamber 32, and the lubricant in the pressure chamber 32 flows out into the large diameter hole 23 through the circulation hole 33 and the communication hole 34. In this case, the pressure of the lubricant in the pressure chamber 32 is adjusted by changes in the flying height of the shaft body 26 and is approximately constant, so that a constant thrust load capacity can be obtained and the flying height of the shaft body 26 can be kept small. I can do it.
第4図および第5図はハウジングが外筒と球と
から構成されている実施例であつて、ハウジング
21は外筒121と外筒121の内周面の底部に
圧入等の方法によつて嵌合して固定した球221
とから構成されている。前記外筒121の内周面
がラジアル内面24となつており、このラジアル
内面24に内周みぞ36が設けられている。前記
球221がスラスト軸受面25となつており、ま
たスラスト端面31は平面状になつている。また
ラジアル外面27には内周みぞ36と対向する位
置に外周みぞ37が設けられ、この外周みぞ37
は軸体26に設けた連通穴34を介して循環穴3
3と連通している。従つて循環穴33は軸体26
の外周面のラジアル外面27に通じている。なお
外筒121の内周面に球221の代りに円筒コロ
を嵌合して固定しても良い。 4 and 5 show an embodiment in which the housing is composed of an outer cylinder and a sphere, and the housing 21 is fitted into the outer cylinder 121 and the bottom of the inner peripheral surface of the outer cylinder 121 by a method such as press fitting. Ball 221 fitted and fixed
It is composed of. The inner circumferential surface of the outer cylinder 121 is a radial inner surface 24, and an inner circumferential groove 36 is provided in the radial inner surface 24. The ball 221 serves as the thrust bearing surface 25, and the thrust end surface 31 has a planar shape. Further, an outer circumferential groove 37 is provided on the radial outer surface 27 at a position facing the inner circumferential groove 36, and this outer circumferential groove 37
is connected to the circulation hole 3 through the communication hole 34 provided in the shaft body 26.
It communicates with 3. Therefore, the circulation hole 33 is connected to the shaft body 26.
It communicates with the radial outer surface 27 of the outer peripheral surface of. Note that instead of the balls 221, cylindrical rollers may be fitted and fixed to the inner peripheral surface of the outer cylinder 121.
第6図はハウジングが外筒とスリーブと円筒コ
ロとから構成されている実施例であつて、ハウジ
ング21は外筒121と外筒121の内周面に圧
入等の方法によつて嵌合して固定したスリーブ3
21とスリーブ321の内周面の底部に嵌合して
固定した円筒コロ421とから構成されている。
前記スリーブ321の内周面がラジアル内面24
となつており、円筒コロ421が凹球面状のスラ
スト軸受面25となつている。またスラスト端面
31は凸形球面状になつており、スラスト端面3
1とスラスト軸受面25とは断面が円弧状にクラ
ウニングされているので軸体26の起動トルクが
減少すると共にスラスト軸受面25とスラスト端
面の接触面35との摩耗が少ない。なおスラスト
端面31のみを凸形球面状にクラウニングしてス
ラスト軸受面25を平面状にしても良く、円筒コ
ロ421のスラスト軸受面25のみをクラウニン
グしても良い。またスリーブ321の内周面に円
筒コロ421の代りに球を嵌合して固定しても良
い。 FIG. 6 shows an embodiment in which the housing is composed of an outer cylinder, a sleeve, and a cylindrical roller, and the housing 21 is fitted into the outer cylinder 121 and the inner peripheral surface of the outer cylinder 121 by a method such as press fitting. Sleeve 3 fixed with
21 and a cylindrical roller 421 fitted and fixed to the bottom of the inner peripheral surface of the sleeve 321.
The inner peripheral surface of the sleeve 321 is the radial inner surface 24
The cylindrical rollers 421 serve as a concave spherical thrust bearing surface 25. The thrust end surface 31 has a convex spherical shape, and the thrust end surface 31 has a convex spherical shape.
1 and the thrust bearing surface 25 are crowned in a circular arc shape in cross section, so that the starting torque of the shaft body 26 is reduced and there is little wear between the thrust bearing surface 25 and the contact surface 35 of the thrust end surface. Note that only the thrust end face 31 may be crowned into a convex spherical shape to make the thrust bearing surface 25 planar, or only the thrust bearing surface 25 of the cylindrical roller 421 may be crowned. Further, instead of the cylindrical roller 421, a ball may be fitted and fixed to the inner peripheral surface of the sleeve 321.
第8図はスラスト軸受面とスラスト端面とが間
接に接触している実施例であつて、ハウジング2
1は外筒121と外筒121の内周面の底部に嵌
合して固定した円筒コロ421とから構成されて
いる。前記外筒121の内周面がラジアル内面2
4となつており、円筒コロ421がスラスト軸受
面25となつている。前記スラスト軸受面25に
球体41が配設され、この球体41はハウジング
21に固定したリテーナ42によつて回転可能に
保持されている。前記スラスト端面31は中央部
が凹形円すい面となつており、このスラスト軸受
面25とスラスト端面31に設けた環状の接触面
35とは軸受の静止時に球体41を介して間接に
接触している。 FIG. 8 shows an embodiment in which the thrust bearing surface and the thrust end surface are in indirect contact with each other, and the housing 2
1 is composed of an outer cylinder 121 and a cylindrical roller 421 fitted and fixed to the bottom of the inner peripheral surface of the outer cylinder 121. The inner peripheral surface of the outer cylinder 121 is the radial inner surface 2
4, and the cylindrical rollers 421 serve as the thrust bearing surface 25. A spherical body 41 is disposed on the thrust bearing surface 25, and this spherical body 41 is rotatably held by a retainer 42 fixed to the housing 21. The thrust end surface 31 has a concave conical surface at its center, and the thrust bearing surface 25 and the annular contact surface 35 provided on the thrust end surface 31 come into indirect contact via the sphere 41 when the bearing is at rest. There is.
このようにすると、軸体26の起動時に球体4
1がスラスト底面25に対してすべるので軸体2
6の起動トルクが低い。なお軸体26が浮上する
と循環穴33内の潤滑剤の圧力が負圧になつて球
体41を吸い込もうとするのでリテーナ42によ
つて球体41の飛び上りを防止している。なおス
ラスト端面31の中央部を凹球面としても良い。 In this way, when the shaft body 26 is started, the sphere 4
1 slides against the thrust bottom surface 25, so the shaft body 2
6's starting torque is low. Note that when the shaft body 26 floats up, the pressure of the lubricant in the circulation hole 33 becomes negative and tries to suck in the sphere 41, so the retainer 42 prevents the sphere 41 from flying up. Note that the center portion of the thrust end face 31 may be formed into a concave spherical surface.
なお図示の実施例ではラジアル外面27に動圧
発生用のみぞ28を設けたが、ラジアル外面27
とラジアル内面24との少なくとも一方に動圧発
生用のみぞ28を設けても良い。 In the illustrated embodiment, the groove 28 for generating dynamic pressure is provided on the radial outer surface 27.
A groove 28 for generating dynamic pressure may be provided in at least one of the radial inner surface 24 and the radial inner surface 24.
また軸体26の回転ではなくハウジング21の
回転としても良く、相対回転としても良い。 Further, instead of the rotation of the shaft body 26, the rotation of the housing 21 may be used, or a relative rotation may be used.
さらに動圧形流体軸受装置を縦型ではなく横型
又は倒置型に用いても良い。 Furthermore, the hydrodynamic bearing device may be used in a horizontal or inverted type instead of a vertical type.
なお転がり軸受で多量生産されている精度の良
い球および円筒コロをこの考案の実施例の球22
1、円筒コロ421、および球体41として用い
ると、低コストで量産に適する。 In addition, ball 22 of the embodiment of this invention is a high-precision ball and cylindrical roller that are mass-produced in rolling bearings.
1. When used as the cylindrical roller 421 and the sphere 41, it is suitable for mass production at low cost.
この発明の動圧形流体軸受装置によると、スラ
スト端面31に設けた循環穴33が軸体26の外
周面に通じているので軸体26がハウジング21
に対して軸方向に変位すると圧力室32内の潤滑
剤が循環穴33を通つて軸体26の外周面に流出
し、圧力室32内の潤滑剤の圧力は軸体26のハ
ウジング21に対する変位によつて調整されてほ
ぼ一定であり、一定のスラスト負荷能力が得られ
ると共に軸体26のハウジング21に対する軸方
向の変位を小さくおさえることができる。またス
ラスト端面31は軸受の静止時にスラスト軸受面
25と直接又は間接に接触する環状の接触面35
を循環穴33の周囲に有しているので軸受の静止
時にスラスト軸受面25とスラスト端面31との
接触面圧を小さくでき、スラスト軸受面25とス
ラスト端面31との損傷を防止できるという効果
を有する。 According to the hydrodynamic bearing device of the present invention, the circulation hole 33 provided in the thrust end face 31 communicates with the outer peripheral surface of the shaft body 26, so that the shaft body 26 is connected to the housing 21.
When the lubricant in the pressure chamber 32 is displaced in the axial direction relative to the housing 21, the lubricant in the pressure chamber 32 flows out to the outer peripheral surface of the shaft body 26 through the circulation hole 33, and the pressure of the lubricant in the pressure chamber 32 is increased by the displacement of the shaft body 26 with respect to the housing 21. The thrust load is adjusted to be substantially constant, so that a constant thrust load capacity can be obtained and the displacement of the shaft body 26 with respect to the housing 21 in the axial direction can be kept small. Further, the thrust end surface 31 is an annular contact surface 35 that directly or indirectly contacts the thrust bearing surface 25 when the bearing is at rest.
around the circulation hole 33, the contact pressure between the thrust bearing surface 25 and the thrust end surface 31 can be reduced when the bearing is stationary, and damage to the thrust bearing surface 25 and the thrust end surface 31 can be prevented. have
第1図は従来の動圧形流体軸受装置の断面図、
第2図はこの発明の一実施例を示す動圧形流体軸
受装置の断面図、第3図は第2図に示す軸体の正
面図、第4図、第6図、および第8図はこの発明
の他の実施例を示す動圧形流体軸受装置の断面
図、第5図は第4図に示す軸体の正面図、第7図
は第6図に示す軸体の正面図、第9図は第8図に
示す軸体の正面図である。
図中、21はハウジング、22は円筒状孔、2
4はラジアル内面、25はスラスト軸受面、26
は軸体、27はラジアル外面、28は動圧発生用
のみぞ、31はスラスト端面、32は圧力室、3
3は循環穴、35は接触面である。
Figure 1 is a cross-sectional view of a conventional hydrodynamic bearing device.
FIG. 2 is a sectional view of a hydrodynamic bearing device showing an embodiment of the present invention, FIG. 3 is a front view of the shaft body shown in FIG. 2, and FIGS. 4, 6, and 8 are 5 is a front view of the shaft shown in FIG. 4, FIG. 7 is a front view of the shaft shown in FIG. 6, and FIG. FIG. 9 is a front view of the shaft shown in FIG. 8. In the figure, 21 is a housing, 22 is a cylindrical hole, 2
4 is the radial inner surface, 25 is the thrust bearing surface, 26
27 is a shaft body, 27 is a radial outer surface, 28 is a groove for generating dynamic pressure, 31 is a thrust end surface, 32 is a pressure chamber, 3
3 is a circulation hole, and 35 is a contact surface.
Claims (1)
状のラジアル内面24とスラスト軸受面25とを
有し、前記円筒状孔22に配設した軸体26はラ
ジアル内面24と対向して共働する円筒状のラジ
アル外面27と、スラスト軸受面25と対向して
共働するスラスト端面31とを有し、該スラスト
端面31の外周部とスラスト軸受面25の外周部
との間に圧力室32が設けられ、前記ラジアル内
面24とラジアル外面27との少なくとも一方に
は軸受の作動中にラジアル内面24とラジアル外
面27との間のすきま内の潤滑剤を圧力室32へ
流出する作用を行う動圧発生用のみぞ28が設け
られている動圧形流体軸受装置において、前記ス
ラスト端面31の中央部に設けた循環穴33が軸
体26の外周面に通じ、前記スラスト端面31は
軸受の静止時にスラスト軸受面25と直接又は間
接に接触する環状の接触面35を循環穴33の周
囲に有していることを特徴とする動圧形流体軸受
装置。 2 スラスト軸受面25とスラスト端面31との
間に球体41が配設され、該球体41を保持する
リテーナ42がハウジング21に固定され、前記
スラスト軸受面25とスラスト端面の接触面35
とが軸受の静止時に球体41を介して間接に接触
している特許請求の範囲第1項記載の動圧形流体
軸受装置。[Claims] 1. A cylindrical hole 22 provided in the housing 21 has a cylindrical radial inner surface 24 and a thrust bearing surface 25, and a shaft body 26 provided in the cylindrical hole 22 has a radial inner surface 24 and a thrust bearing surface 25. It has a cylindrical radial outer surface 27 that faces and works together, and a thrust end face 31 that faces and works together with the thrust bearing surface 25. A pressure chamber 32 is provided between the radial inner surface 24 and the radial outer surface 27, and at least one of the radial inner surface 24 and the radial outer surface 27 is provided with lubricant in the gap between the radial inner surface 24 and the radial outer surface 27 to flow out into the pressure chamber 32 during operation of the bearing. In a hydrodynamic bearing device in which a groove 28 for generating dynamic pressure is provided, a circulation hole 33 provided in the center of the thrust end face 31 communicates with the outer circumferential surface of the shaft body 26, and Reference numeral 31 denotes a hydrodynamic bearing device characterized in that it has an annular contact surface 35 around the circulation hole 33 that directly or indirectly contacts the thrust bearing surface 25 when the bearing is at rest. 2 A sphere 41 is disposed between the thrust bearing surface 25 and the thrust end surface 31, a retainer 42 holding the sphere 41 is fixed to the housing 21, and a contact surface 35 between the thrust bearing surface 25 and the thrust end surface
2. The hydrodynamic bearing device according to claim 1, wherein the spherical bodies and the spherical bodies are in indirect contact with each other through the spheres 41 when the bearing is at rest.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP12834282A JPS5824616A (en) | 1982-07-24 | 1982-07-24 | Dynamic pressure fluid bearing device |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP12834282A JPS5824616A (en) | 1982-07-24 | 1982-07-24 | Dynamic pressure fluid bearing device |
Publications (2)
Publication Number | Publication Date |
---|---|
JPS5824616A JPS5824616A (en) | 1983-02-14 |
JPS6364647B2 true JPS6364647B2 (en) | 1988-12-13 |
Family
ID=14982426
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP12834282A Granted JPS5824616A (en) | 1982-07-24 | 1982-07-24 | Dynamic pressure fluid bearing device |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPS5824616A (en) |
Families Citing this family (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS6384419U (en) * | 1986-11-20 | 1988-06-02 | ||
JPH0814285B2 (en) * | 1988-06-29 | 1996-02-14 | 松下電器産業株式会社 | Fan motor |
JP2689331B2 (en) * | 1988-03-25 | 1997-12-10 | 宇宙開発事業団 | Pre-combustion air-breathing rocket engine |
US4934836A (en) * | 1988-08-18 | 1990-06-19 | Nippon Seiko Kabushiki Kaisha | Dynamic pressure type fluid bearing device |
US7011450B2 (en) | 2002-12-02 | 2006-03-14 | Matsushita Electric Industrial Co., Ltd. | Fluid dynamic bearing device and motor including the device |
JP2006029565A (en) | 2004-07-21 | 2006-02-02 | Matsushita Electric Ind Co Ltd | Fluid bearing device, spindle motor having the same, and hard disk drive device |
WO2006098389A1 (en) * | 2005-03-16 | 2006-09-21 | Suzuki Press Kogyosho, Co. Ltd. | Flywheel power supply device |
Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS54102445A (en) * | 1978-01-27 | 1979-08-11 | Matsushita Electric Ind Co Ltd | Fluid bearing revolving apparatus |
-
1982
- 1982-07-24 JP JP12834282A patent/JPS5824616A/en active Granted
Patent Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS54102445A (en) * | 1978-01-27 | 1979-08-11 | Matsushita Electric Ind Co Ltd | Fluid bearing revolving apparatus |
Also Published As
Publication number | Publication date |
---|---|
JPS5824616A (en) | 1983-02-14 |
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