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 |
| JPWO2006098389A1 (en) * | 2005-03-16 | 2008-08-28 | 有限会社鈴木プレス工業所 | Flywheel power supply |
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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