JP2002257132A - Dynamic pressure bearing - Google Patents
Dynamic pressure bearingInfo
- Publication number
- JP2002257132A JP2002257132A JP2001053683A JP2001053683A JP2002257132A JP 2002257132 A JP2002257132 A JP 2002257132A JP 2001053683 A JP2001053683 A JP 2001053683A JP 2001053683 A JP2001053683 A JP 2001053683A JP 2002257132 A JP2002257132 A JP 2002257132A
- Authority
- JP
- Japan
- Prior art keywords
- dynamic pressure
- groove
- inner peripheral
- radial
- thrust
- 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.)
- Pending
Links
- 230000002093 peripheral effect Effects 0.000 claims abstract description 120
- 239000010687 lubricating oil Substances 0.000 description 34
- 230000000694 effects Effects 0.000 description 9
- 239000003921 oil Substances 0.000 description 8
- 239000011148 porous material Substances 0.000 description 3
- 238000004513 sizing Methods 0.000 description 3
- 238000000034 method Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 238000000465 moulding Methods 0.000 description 2
- 230000003287 optical effect Effects 0.000 description 2
- 230000002195 synergetic effect Effects 0.000 description 2
- 238000005452 bending Methods 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 230000010485 coping Effects 0.000 description 1
- 238000000605 extraction Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 239000012466 permeate Substances 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
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/02—Parts of sliding-contact bearings
- F16C33/04—Brasses; Bushes; Linings
- F16C33/06—Sliding surface mainly made of metal
- F16C33/10—Construction relative to lubrication
- F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
- F16C33/106—Details of distribution or circulation inside the bearings, e.g. details of the bearing surfaces to affect flow or pressure of the liquid
- F16C33/107—Grooves for generating pressure
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C17/00—Sliding-contact bearings for exclusively rotary movement
- F16C17/02—Sliding-contact bearings for exclusively rotary movement for radial load only
- F16C17/026—Sliding-contact bearings for exclusively rotary movement for radial load only with helical grooves in the bearing surface to generate hydrodynamic pressure, e.g. herringbone grooves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C17/00—Sliding-contact bearings for exclusively rotary movement
- F16C17/10—Sliding-contact bearings for exclusively rotary movement for both radial and axial load
- F16C17/102—Sliding-contact bearings for exclusively rotary movement for both radial and axial load with grooves in the bearing surface to generate hydrodynamic pressure
- F16C17/107—Sliding-contact bearings for exclusively rotary movement for both radial and axial load with grooves in the bearing surface to generate hydrodynamic pressure with at least one surface for radial load and at least one surface for axial load
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/02—Parts of sliding-contact bearings
- F16C33/04—Brasses; Bushes; Linings
- F16C33/06—Sliding surface mainly made of metal
- F16C33/10—Construction relative to lubrication
- F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
- F16C33/103—Construction relative to lubrication with liquid, e.g. oil, as lubricant retained in or near the bearing
- F16C33/104—Construction relative to lubrication with liquid, e.g. oil, as lubricant retained in or near the bearing in a porous body, e.g. oil impregnated sintered sleeve
-
- 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
- F16C17/26—Systems consisting of a plurality of sliding-contact bearings
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Oil, Petroleum & Natural Gas (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Sliding-Contact Bearings (AREA)
- Motor Or Generator Frames (AREA)
- Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
Abstract
Description
【0001】[0001]
【発明の属する技術分野】本発明は、スピンドルモータ
用軸受等の比較的高速で回転する軸を高精度で支持する
際に用いて好適な焼結含油軸受等で作られる動圧軸受に
関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a dynamic pressure bearing made of a sintered oil-impregnated bearing suitable for supporting a shaft rotating at a relatively high speed, such as a spindle motor bearing, with high precision.
【0002】[0002]
【従来の技術】滑り軸受のラジアル荷重を受ける内周面
に溝を設け、回転軸との間に形成される油膜に動圧を生
じさせることにより滑り摩擦を低減させる技術がある。
動圧を生じさせる溝、すなわち動圧溝は、通常、周方向
(回転軸の回転方向)に間隔をおいて複数形成され、そ
の形状は、軸方向と平行あるいは斜めに延びる直線状の
ものや、三角形状のもの、さらには、略V字状でヘリン
グボーン模様に形成されたものがある。三角形状や略V
字状の動圧溝の場合は、周方向に対して対称的な形状と
され、その周方向に沿って1列または2列に形成されて
いる。また、このような動圧溝の深さは、均一であった
り、周方向に変化しているもの等がある。2. Description of the Related Art There is a technique for reducing sliding friction by providing a groove on an inner peripheral surface of a sliding bearing which receives a radial load and generating a dynamic pressure on an oil film formed between the bearing and a rotating shaft.
A plurality of grooves for generating dynamic pressure, that is, dynamic pressure grooves, are usually formed at intervals in the circumferential direction (rotational direction of the rotating shaft), and have a linear shape extending parallel to or oblique to the axial direction. , A triangular shape, and a substantially V-shaped herringbone pattern. Triangular or V
In the case of the U-shaped dynamic pressure grooves, the grooves are symmetrical with respect to the circumferential direction, and are formed in one or two rows along the circumferential direction. In addition, the depth of such a dynamic pressure groove may be uniform or may vary in the circumferential direction.
【0003】また、ラジアル荷重とともにスラスト荷重
を受ける軸受においては、スラスト荷重を受ける端面
に、複数の動圧溝が放射状あるいは渦巻き状に形成され
たものや、複数の略V字状の動圧溝が形成されたものが
ある。これらの動圧溝においても、その深さは均一なも
のや周方向に変化しているもの等があり、さらには、底
面が周方向に波状に形成されて深さが不均一なものもあ
る。[0003] Further, in a bearing which receives a thrust load together with a radial load, a plurality of dynamic pressure grooves are formed radially or spirally on an end face which receives the thrust load, or a plurality of substantially V-shaped dynamic pressure grooves are provided. Is formed. Also in these dynamic pressure grooves, there are those having a uniform depth and those varying in the circumferential direction, and further, those having a bottom surface formed in a wavy shape in the circumferential direction and having an uneven depth. .
【0004】上記のような動圧溝が形成された動圧軸受
は、焼結含油軸受に多く適用されている。焼結含油軸受
の場合、スラスト荷重を受ける端面への動圧溝の形成
は、圧粉体の成形時か、または焼結体へのサイジング時
に金型のパンチで行われる。また、内周面への動圧溝の
形成は、動圧溝が内周面から端面に開放し、かつ、軸方
向に平行な場合には、圧粉体の成形時か、焼結体をサイ
ジングする段階で形成される。また、端面に開放してお
らず内周面内に閉じられた状態の動圧溝を形成するに
は、圧粉体の成形時に、一端側を端面に開放させてお
き、焼結体のサイジング時に開放側の端部を封鎖する方
法が挙げられる。この他には、サイジング時に、軸孔に
挿入されるコアロッドの外周面に形成した凸部を内周面
に刻印して動圧溝を形成し、コアロッドの抜き取りは軸
受のスプリングバックの発生により行う方法がある。こ
のようにして動圧溝が形成された焼結含油は、動圧作用
によって回転軸との摩擦抵抗が小さくなり、また、長期
にわたって機能することから、高速回転するスピンドル
モータの回転軸の軸受として特に好適である。[0004] The dynamic pressure bearing in which the above-mentioned dynamic pressure grooves are formed is widely applied to sintered oil-impregnated bearings. In the case of a sintered oil-impregnated bearing, the formation of the dynamic pressure groove on the end face that receives the thrust load is performed by a punch of a mold at the time of molding the compact or sizing the sintered body. In addition, when the dynamic pressure grooves are formed on the inner peripheral surface, the dynamic pressure grooves are opened from the inner peripheral surface to the end face, and when the dynamic pressure grooves are parallel to the axial direction, when the green compact is molded or when the sintered body is formed. It is formed at the stage of sizing. In order to form a hydrodynamic groove that is not open to the end face but closed in the inner peripheral face, one end side is opened to the end face during molding of the green compact, and the sintered body is sized. Sometimes, a method of closing the open end is used. In addition, at the time of sizing, a convex portion formed on the outer peripheral surface of the core rod inserted into the shaft hole is stamped on the inner peripheral surface to form a dynamic pressure groove, and extraction of the core rod is performed by occurrence of spring back of the bearing. There is a way. The sintered oil impregnated with the dynamic pressure grooves formed in this way has a reduced frictional resistance with the rotating shaft due to the dynamic pressure action, and also functions for a long period of time. Particularly preferred.
【0005】[0005]
【発明が解決しようとする課題】ところで、例えば光デ
ィスク装置のスピンドルモータは、回転数が毎分数千回
転以上と他の回転軸よりもかなり高速であり、これに加
えて、光ディスクの搭載によるアンバランス荷重が加わ
って負荷が周方向に移動する振れ周りを生じる。このた
め、これを支持する動圧軸受にあっては、回転軸との間
に油膜が形成されにくくなることから摩擦抵抗が増大
し、摩耗の進行が速まったり消費電力が増したりする問
題が生じる。つまり、光ディスク装置がより高速回転化
すればするほど、動圧軸受の性能の向上が求められる。By the way, for example, a spindle motor of an optical disk device has a rotational speed of several thousands or more per minute, which is much higher than that of other rotary shafts. When a balance load is applied, the load moves in the circumferential direction, causing a runout. For this reason, in the dynamic pressure bearing that supports this, since an oil film is less likely to be formed between the bearing and the rotating shaft, frictional resistance increases, causing a problem that wear progresses faster and power consumption increases. . That is, the higher the speed of the optical disk device, the higher the performance of the dynamic pressure bearing is required.
【0006】したがって本発明は、動圧作用がより高ま
って回転軸との摩擦抵抗が大幅に低減し、回転軸の高速
回転化に対応可能な動圧軸受を提供することを目的とし
ている。SUMMARY OF THE INVENTION Accordingly, it is an object of the present invention to provide a dynamic pressure bearing capable of coping with a high-speed rotation of a rotary shaft, in which the dynamic pressure action is further increased and the frictional resistance with the rotary shaft is greatly reduced.
【0007】[0007]
【課題を解決するための手段】本発明は、回転軸からラ
ジアル荷重を受ける内周面に、回転軸の回転方向に収束
する複数の略V字状のラジアル動圧溝がヘリングボーン
模様に形成され、このラジアル動圧溝の収束部が、軸方
向一端側に偏っており、かつ、略V字状をなすラジアル
動圧溝の一方および他方の各溝部のうちの前記一端側の
溝部が、反対側の溝部よりも短く形成されていることを
特徴とする。According to the present invention, a plurality of substantially V-shaped radial dynamic pressure grooves converging in the rotation direction of a rotating shaft are formed in a herringbone pattern on an inner peripheral surface receiving a radial load from the rotating shaft. The converging portion of the radial dynamic pressure groove is biased toward one end in the axial direction, and the groove on one end of one and the other grooves of the radial dynamic pressure groove having a substantially V shape is It is characterized by being formed shorter than the groove on the opposite side.
【0008】本発明においては、回転軸からラジアル荷
重を受ける内周面が、軸方向全域にわたって連続して形
成されている場合と、軸方向に間隔をおいて2箇所以上
形成されている場合とを含む。内周面が全域にわたる場
合には、その全域にわたって本発明に係る上記ラジアル
動圧溝が周方向に1列に形成されている構成を基本とす
る。本発明では、上記ラジアル動圧溝が、内周面の全域
ではなく少なくとも軸方向一端側に形成されている構成
を含む。その場合には、収束部は上記構成と同様に軸方
向一端側に偏ることになる。ラジアル動圧溝は、両端に
形成されて計2列とされていてもよい。また、他端側に
はラジアル動圧溝が形成されていないか、もしくは、従
来のラジアル動圧溝が形成されていて両端に異なる種類
のラジアル動圧溝が1列ずつ形成されている形態も含
む。In the present invention, the case where the inner peripheral surface receiving the radial load from the rotating shaft is formed continuously over the entire area in the axial direction, and the case where two or more places are formed at intervals in the axial direction. including. When the inner peripheral surface extends over the entire area, the radial dynamic pressure grooves according to the present invention are basically formed in a single row in the circumferential direction over the entire area. The present invention includes a configuration in which the radial dynamic pressure groove is formed not at the entire area of the inner peripheral surface but at least at one end in the axial direction. In this case, the converging portion is biased toward one end in the axial direction as in the above configuration. The radial dynamic pressure grooves may be formed at both ends to form a total of two rows. Also, there is no radial dynamic pressure groove formed on the other end side, or a conventional radial dynamic pressure groove is formed, and different types of radial dynamic pressure grooves are formed at both ends in a row. Including.
【0009】一方、回転軸からラジアル荷重を受ける内
周面が、軸方向に間隔をおいて2箇所以上形成されてい
る場合は、軸方向の端部側に形成された各内周面の少な
くとも一方に、上記ラジアル動圧溝が形成されているこ
とを特徴とする。この場合、その内周面の軸方向全域に
ラジアル動圧溝が1列に形成されており、他方の内周面
にも同様に本発明のラジアル動圧溝が形成されている形
態を含む。また、他方の内周面には、ラジアル動圧溝が
形成されていないか、もしくは、従来のラジアル動圧溝
が形成されていてもよい。On the other hand, when two or more inner peripheral surfaces receiving a radial load from the rotating shaft are formed at intervals in the axial direction, at least one of the inner peripheral surfaces formed on the axial end portion side. On the other hand, the radial dynamic pressure groove is formed. In this case, a radial dynamic pressure groove is formed in a single row in the entire axial direction of the inner peripheral surface, and the radial dynamic pressure groove of the present invention is similarly formed on the other inner peripheral surface. The other inner peripheral surface may not have a radial dynamic pressure groove formed therein, or may have a conventional radial dynamic pressure groove formed therein.
【0010】上記各形態を包含する本発明においては、
本発明に係るラジアル動圧溝が回転軸の回転方向すなわ
ち周方向に収束する略V字状であって、その収束部が軸
方向一端側に偏っており、かつ、略V字状をなすラジア
ル動圧溝の一方および他方の各溝部のうちの一端側の溝
部が反対側の溝部よりも短いことを特徴としている。本
発明によれば、回転軸の回転によってラジアル動圧溝に
供給された潤滑油は動圧作用を発揮しながら収束部に収
束し、この収束部で最も高い油圧を発生する。この収束
部は、一端側に偏っているので、例えば2つの本発明の
動圧軸受を、収束部がそれぞれ端部側になるように配置
して組み合わせると、油圧が高い収束部間の距離が長く
なる。このため、動圧作用がより高まって回転軸の振れ
や倒れを抑える剛性が向上し、かつ、回転軸との摩擦抵
抗が大幅に低減する。その結果、高速回転仕様の回転軸
の軸受として対応可能である。In the present invention including the above embodiments,
The radial dynamic pressure groove according to the present invention has a substantially V-shape that converges in the rotation direction of the rotating shaft, that is, the circumferential direction, and the converging portion is biased toward one end in the axial direction, and has a substantially V-shape. It is characterized in that one of the grooves of the dynamic pressure groove and the other of the other grooves are shorter than the groove on the opposite side. According to the present invention, the lubricating oil supplied to the radial dynamic pressure groove by the rotation of the rotating shaft converges to the converging portion while exerting the dynamic pressure action, and generates the highest hydraulic pressure in the converging portion. Since the converging portion is biased toward one end, for example, when two hydrodynamic bearings of the present invention are arranged and combined so that the converging portions are located on the end portions, the distance between the converging portions with high hydraulic pressure is reduced. become longer. For this reason, the dynamic pressure action is further increased, the rigidity for suppressing the run-out and fall of the rotary shaft is improved, and the frictional resistance with the rotary shaft is greatly reduced. As a result, it can be used as a bearing for a rotating shaft of a high-speed rotation specification.
【0011】上記の作用をより効果的に得るためには、
ラジアル動圧溝の収束部はできるだけ一端側に配するこ
とが好ましい。また、ラジアル動圧溝の収束部から一端
側に延びる短い方の溝部の端部は内周面において閉じて
いる形態でもよいが、端面または軸孔の端縁に形成され
た面取り部に開放する形態でもよい。その場合には、回
転軸と端部との間に溜まる潤滑油が収束部に搬送される
作用が生じ、回転軸の回転による潤滑油の漏洩が抑制さ
れる。In order to obtain the above-mentioned effects more effectively,
It is preferable that the converging portion of the radial dynamic pressure groove is disposed at one end as much as possible. Further, the end of the shorter groove extending from the converging portion of the radial dynamic pressure groove to one end may be closed on the inner peripheral surface, but is opened to the chamfer formed on the end surface or the edge of the shaft hole. It may be in a form. In this case, the lubricating oil accumulated between the rotating shaft and the end portion is conveyed to the converging portion, and the leakage of the lubricating oil due to the rotation of the rotating shaft is suppressed.
【0012】V字状のラジアル動圧溝の形状は、V字状
をなす各溝部が直線的であっても曲線的であってもよ
い。また、ラジアル動圧溝の深さは、潤滑油のダム効果
を期待して回転軸の回転方向側を深くしたり、逆に、潤
滑油のくさび効果を向上させるために回転軸の回転方向
側に向かうにしたがって浅くしたりすることができる。The shape of the V-shaped radial dynamic pressure groove may be such that each V-shaped groove is linear or curved. In addition, the depth of the radial dynamic pressure groove should be increased in the rotational direction of the rotating shaft in order to expect the dam effect of the lubricating oil, or conversely, in order to improve the wedge effect of the lubricating oil, It can be made shallower toward.
【0013】次に、本発明は、回転軸からラジアル荷重
とともにスラスト荷重も受ける動圧軸受において、スラ
スト荷重を受ける一方の端面に、回転軸の回転方向に向
かうにしたがって外周側から内周側に延びる複数のスラ
スト動圧溝が略放射状に形成されているとともに、ラジ
アル荷重を受ける内周面に、回転軸の回転方向に収束す
る複数の略V字状のラジアル動圧溝がヘリングボーン模
様に形成されていることを特徴とする。Next, the present invention relates to a dynamic pressure bearing which receives a thrust load as well as a radial load from a rotary shaft. A plurality of extending thrust dynamic pressure grooves are formed substantially radially, and a plurality of substantially V-shaped radial dynamic pressure grooves converging in the rotation direction of the rotating shaft are formed in a herringbone pattern on an inner peripheral surface receiving a radial load. It is characterized by being formed.
【0014】本発明においては、さらに、ラジアル動圧
溝の収束部がスラスト動圧溝が形成された端面側に偏っ
ており、かつ、略V字状をなすラジアル動圧溝の一方お
よび他方の各溝部のうちのスラスト動圧溝が形成された
端面側の溝部が反対側の溝部よりも短く形成されている
ことを特徴とする。In the present invention, further, the converging portion of the radial dynamic pressure groove is biased toward the end face side where the thrust dynamic pressure groove is formed, and one and the other of the substantially V-shaped radial dynamic pressure grooves are formed. The groove on the end face side of the groove on which the thrust dynamic pressure groove is formed is shorter than the groove on the opposite side.
【0015】これら発明においては、先の発明と同様
に、回転軸からラジアル荷重を受ける内周面が、軸方向
全域にわたって連続して形成されている場合と、軸方向
に間隔をおいて2箇所以上形成されている場合とを含
む。内周面が全域にわたる場合には、その全域にわたっ
て本発明に係る上記ラジアル動圧溝が周方向に1列に形
成されている構成を基本とする。本発明では、上記ラジ
アル動圧溝が、内周面の全域ではなく少なくとも軸方向
一端側に形成されている構成を含む。その場合には、収
束部は上記構成と同様に軸方向一端側に偏ることにな
る。ラジアル動圧溝は、両端に形成されて計2列とされ
ていてもよい。また、他端側にはラジアル動圧溝が形成
されていないか、もしくは、従来のラジアル動圧溝が形
成されていて両端に異なる種類のラジアル動圧溝が1列
ずつ形成されている形態も含む。[0015] In these inventions, similarly to the above invention, the inner peripheral surface receiving a radial load from the rotating shaft is formed continuously over the entire area in the axial direction, and at two places at intervals in the axial direction. The above case is also included. When the inner peripheral surface extends over the entire area, the radial dynamic pressure grooves according to the present invention are basically formed in a single row in the circumferential direction over the entire area. The present invention includes a configuration in which the radial dynamic pressure groove is formed not at the entire area of the inner peripheral surface but at least at one end in the axial direction. In this case, the converging portion is biased toward one end in the axial direction as in the above configuration. The radial dynamic pressure grooves may be formed at both ends to form a total of two rows. Also, there is no radial dynamic pressure groove formed on the other end side, or a conventional radial dynamic pressure groove is formed, and different types of radial dynamic pressure grooves are formed at both ends in a row. Including.
【0016】一方、回転軸からラジアル荷重を受ける内
周面が軸方向に間隔をおいて2箇所以上形成されている
場合は、スラスト動圧溝が形成された側の端部に上記ラ
ジアル動圧溝が形成されていることを特徴とする。この
場合、その内周面の軸方向全域にラジアル動圧溝が1列
に形成されており、これとは反対側の端部の内周面にも
同様に本発明のラジアル動圧溝が形成されている形態を
含む。また、その反対側の端部の内周面にはラジアル動
圧溝が形成されていないか、もしくは、従来のラジアル
動圧溝が形成されていてもよい。On the other hand, when two or more inner peripheral surfaces receiving a radial load from the rotating shaft are formed at intervals in the axial direction, the radial dynamic pressure is formed at the end on the side where the thrust dynamic pressure groove is formed. It is characterized in that a groove is formed. In this case, a radial dynamic pressure groove is formed in a row in the entire axial direction of the inner peripheral surface, and the radial dynamic pressure groove of the present invention is similarly formed on the inner peripheral surface at the opposite end. Including the form that has been. Further, no radial dynamic pressure groove may be formed on the inner peripheral surface at the opposite end, or a conventional radial dynamic pressure groove may be formed.
【0017】上記スラスト動圧溝は、形成される端面の
面積に応じて配置が容易な形状とされ、例えば、線状、
楕円状、三角形状、流線形状等の形状が適用される。ま
た、スラスト動圧溝は、内周側の端部が端面内において
閉じているか、あるいは内周面もしくは軸孔の端縁に形
成した面取り部に開放しているかのいずれであってもよ
い。さらに、スラスト動圧溝の外周側の端部も、端面内
において閉じているか、あるいは外周側に開放している
かのいずれかであってもよい。The thrust dynamic pressure groove has a shape which can be easily arranged according to the area of the end face to be formed.
Shapes such as an elliptical shape, a triangular shape, and a streamline shape are applied. Further, the thrust dynamic pressure groove may have either an inner peripheral end closed in the end face or an open end in a chamfer formed in the inner peripheral face or the edge of the shaft hole. Furthermore, the end on the outer peripheral side of the thrust dynamic pressure groove may be either closed in the end face or open to the outer peripheral side.
【0018】このようなスラスト動圧溝には、回転軸が
端面に摺動することによって潤滑油が供給され、動圧作
用によって摩擦が低減される。スラスト動圧溝は、回転
軸の回転方向に向かうにしたがって外周側から内周側に
延びており、これらが略放射状に配列されているので、
供給された潤滑油は回転軸の回転によって内周側に積極
的に流動していく。これによって、外周側への潤滑油の
漏洩が抑えられるとともに、内周側の油圧が高くなって
内周面の端部への潤滑油の供給が促され、内周面の摩擦
低減が図られる。スラスト動圧溝の外周側の端部が端面
内において閉じていれば、遠心力による潤滑油の漏洩が
より抑えられるので好ましい。In such a thrust dynamic pressure groove, lubricating oil is supplied by the rotation shaft sliding on the end face, and the friction is reduced by the dynamic pressure action. The thrust dynamic pressure grooves extend from the outer peripheral side to the inner peripheral side as going in the rotation direction of the rotating shaft, and since these are arranged in a substantially radial manner,
The supplied lubricating oil positively flows toward the inner peripheral side by the rotation of the rotating shaft. As a result, the leakage of the lubricating oil to the outer peripheral side is suppressed, and the hydraulic pressure on the inner peripheral side is increased to promote the supply of the lubricating oil to the end of the inner peripheral surface, thereby reducing the friction of the inner peripheral surface. . It is preferable that the end on the outer peripheral side of the thrust dynamic pressure groove is closed in the end face, because leakage of lubricating oil due to centrifugal force can be further suppressed.
【0019】スラスト動圧溝の内周側の端部が閉じてい
る形態が焼結含油軸受に適用されると、潤滑油は油圧の
高い部分から気孔内に浸透して内周面あるいは端面へと
循環する。一方、スラスト動圧溝の内周側の端部が内周
面もしくは軸孔の端縁に形成した面取り部に開放してい
る形態の場合には、潤滑油は内周面のV字状のラジアル
動圧溝における端部側の溝部に流入することが可能で、
その溝部および収束部の油圧が高くなる。ラジアル動圧
溝の端部側の溝部の長さが、反対側の溝部よりも短く形
成されていると、その作用を顕著に得ることができる。When a form in which the inner peripheral end of the thrust dynamic pressure groove is closed is applied to the sintered oil-impregnated bearing, the lubricating oil permeates into the pores from a high oil pressure portion to the inner peripheral surface or the end surface. And circulate. On the other hand, in the case where the inner peripheral end of the thrust dynamic pressure groove is open to the inner peripheral surface or the chamfer formed at the edge of the shaft hole, the lubricating oil is V-shaped on the inner peripheral surface. It is possible to flow into the groove on the end side of the radial dynamic pressure groove,
The oil pressure in the groove and the converging portion increases. When the length of the groove portion on the end portion side of the radial dynamic pressure groove is formed shorter than the groove portion on the opposite side, the effect can be obtained remarkably.
【0020】本発明では、先の発明と同様にラジアル動
圧溝の収束部をできるだけ端部側に配することにより、
その収束部とスラスト動圧溝とが近接して両者の間の部
分の油圧が高まり、回転軸に浮力を与えることになって
摩擦が低減する。また、内周面の両端にラジアル動圧溝
を形成すれば、前述したように油圧の高い部分の距離が
長くなるので、回転軸の振れや倒れを抑える剛性が向上
し、かつ、回転軸との摩擦抵抗が大幅に低減する。ラジ
アル動圧溝の端部側の短い溝部は内周面において閉じて
いる状態でもよいが、端面に開放する形態であれば、ス
ラスト動圧溝の潤滑油の流通性が良好となり、動圧作用
がより顕著に得られる。In the present invention, by arranging the converging portion of the radial dynamic pressure groove as close to the end as possible in the same manner as in the previous invention,
The convergence portion and the thrust dynamic pressure groove are close to each other, and the hydraulic pressure in the portion between the two is increased, and buoyancy is applied to the rotating shaft, thereby reducing friction. Also, if radial dynamic pressure grooves are formed at both ends of the inner peripheral surface, the distance of the high oil pressure part is increased as described above, so that the rigidity for suppressing the runout and falling of the rotary shaft is improved, and Frictional resistance is greatly reduced. The short groove portion on the end side of the radial dynamic pressure groove may be closed on the inner peripheral surface, but if it is open to the end surface, the flowability of the lubricating oil in the thrust dynamic pressure groove becomes good, and the dynamic pressure action Is more remarkably obtained.
【0021】ラジアル動圧溝とスラスト動圧溝の潤滑油
の流通性をより良好にしたい場合には、両者の向かい合
う端部どうしを直接連通させるか、それぞれの端部を軸
孔の端縁に形成した面取り部に開放すればよい。また、
焼結含油軸受の場合に比較的流通性を低めて気孔を利用
した潤滑油の循環作用を得たい場合には、双方の動圧溝
を閉じた状態とし、かつ、向かい合う端部を互い違いに
配置すればよい。When it is desired to improve the flowability of the lubricating oil between the radial dynamic pressure groove and the thrust dynamic pressure groove, the opposite ends of the two grooves may be directly communicated with each other, or each end may be connected to the edge of the shaft hole. What is necessary is just to open to the formed chamfer. Also,
In the case of a sintered oil-impregnated bearing, if it is desired to obtain a lubricating oil circulating effect using pores with relatively low flowability, both hydrodynamic grooves are closed and the opposite ends are staggered. do it.
【0022】なお、上記本発明に係る動圧軸受は、多孔
性で潤滑油が含浸された焼結含油軸受に好適に適用され
る。焼結含油軸受は、潤滑油が気孔を流通することによ
り、回転軸との摺動面、すなわちラジアル荷重を受ける
内周面やスラスト荷重を受ける端面に対して潤滑油が供
給および吸引されて循環する。本発明は、このような潤
滑油の循環と、潤滑油の動圧発生をより効果的に発生さ
せて、摩擦低減に伴う長寿命化や高回転仕様への対応を
可能ならしめる。The hydrodynamic bearing according to the present invention is suitably applied to a sintered oil-impregnated bearing that is porous and impregnated with lubricating oil. In the sintered oil-impregnated bearing, the lubricating oil is supplied and sucked and circulated to the sliding surface with the rotating shaft, that is, the inner peripheral surface receiving the radial load and the end surface receiving the thrust load, by the lubricating oil flowing through the pores. I do. The present invention enables the circulation of the lubricating oil and the generation of the dynamic pressure of the lubricating oil to be more effectively generated, thereby making it possible to extend the service life associated with the reduction of friction and to cope with high-speed specifications.
【0023】[0023]
【発明の実施の形態】以下、図面を参照して本発明の実
施形態を説明する。図8〜図11は、一般的な軸受の構
造を示している。図8に示す軸受1Aは、円筒状の金属
製ハウジング2に、円筒状の焼結含油軸受体3が圧入さ
れ、軸受体3に挿入された回転軸4を支持している。図
9に示す軸受1Bは、ハウジング2に圧入した2つの軸
受体3を、互いに間隔をおいてハウジング2の両端部に
配置し、双方の軸受体3で回転軸4を支持している。図
10に示す軸受1Cは、ハウジング2に1つの軸受体3
が圧入され、軸受体3によって支持される回転軸4は円
盤状のフランジ4aを有しており、そのフランジ4aが
軸受体3の一方の端面に摺動する。図11に示す軸受1
Dはスピンドルモータ用軸受に好適なもので、有底円筒
状のハウジング2内に、間隔をおいて2つの軸受体3が
圧入され、球面に形成された回転軸4の先端をハウジン
グ2の底部のスラスト受板2aで受けるとともに、フラ
ンジ4aが開口側の軸受体3の端面に摺動して潤滑油の
漏洩防止をなしている。以下に、これら軸受1A〜1D
に適用される本発明に係る軸受体の実施形態を説明す
る。Embodiments of the present invention will be described below with reference to the drawings. 8 to 11 show the structure of a general bearing. In a bearing 1A shown in FIG. 8, a cylindrical sintered oil-impregnated bearing body 3 is press-fitted into a cylindrical metal housing 2, and supports a rotating shaft 4 inserted into the bearing body 3. In a bearing 1B shown in FIG. 9, two bearing bodies 3 press-fitted into a housing 2 are arranged at both ends of the housing 2 at an interval from each other, and a rotating shaft 4 is supported by both bearing bodies 3. A bearing 1C shown in FIG.
Is press-fitted, and the rotating shaft 4 supported by the bearing body 3 has a disk-shaped flange 4 a, and the flange 4 a slides on one end surface of the bearing body 3. Bearing 1 shown in FIG.
D is suitable for a spindle motor bearing. Two bearings 3 are press-fitted into a bottomed cylindrical housing 2 at an interval, and the tip of a spherically-shaped rotating shaft 4 is attached to the bottom of the housing 2. And the flange 4a slides on the end face of the bearing body 3 on the opening side to prevent leakage of lubricating oil. Below, these bearings 1A-1D
An embodiment of the bearing body according to the present invention applied to the present invention will be described.
【0024】(1)第1実施形態 図1(a)の軸受体11は円筒状で、内周面21が回転
軸からラジアル荷重を受ける。この軸受体11の軸孔の
両端縁には内周面取り部22が形成され、両端の外周縁
には外周面取り部23が形成されている。そして内周面
21には、周方向に等間隔をおいて複数のラジアル動圧
溝31が全周にわたって形成されている。これらラジア
ル動圧溝31は、矢印Rで示す回転軸の回転方向に収束
する略V字状であって、全体としてヘリングボーン模様
をなしている。ラジアル動圧溝31は、内周面21の全
長にわたって形成されており、その両端部は内周面取り
部22に開放している。この場合のラジアル動圧溝31
の頂点である収束部32は軸方向一端側(図1(a)で
上端側)に偏っており、これによって、V字状をなす2
つの溝部31a,31bのうちの収束部32の一端側の
溝部31aの長さが他方の溝部31bよりも短く形成さ
れている。図示例では、ラジアル動圧溝31は直線的で
あるが、外側あるいは内側に反った湾曲状に形成するこ
ともできる。(1) First Embodiment The bearing 11 shown in FIG. 1A is cylindrical, and the inner peripheral surface 21 receives a radial load from a rotating shaft. Inner peripheral chamfers 22 are formed at both end edges of the shaft hole of the bearing body 11, and outer peripheral chamfers 23 are formed at outer peripheral edges at both ends. A plurality of radial dynamic pressure grooves 31 are formed on the inner peripheral surface 21 at equal intervals in the circumferential direction over the entire circumference. These radial dynamic pressure grooves 31 have a substantially V-shape that converges in the rotation direction of the rotation shaft indicated by the arrow R, and have a herringbone pattern as a whole. The radial dynamic pressure groove 31 is formed over the entire length of the inner peripheral surface 21, and both ends thereof are open to the inner peripheral chamfered portion 22. Radial dynamic pressure groove 31 in this case
The convergence portion 32, which is the vertex, is biased toward one end in the axial direction (the upper end in FIG. 1A), thereby forming a V-shaped 2.
The length of the groove 31a at one end of the converging portion 32 of the two grooves 31a and 31b is shorter than the length of the other groove 31b. In the illustrated example, the radial dynamic pressure groove 31 is linear, but may be formed in a curved shape that is curved outward or inward.
【0025】図1(b)の軸受体11は、図1(a)の
変形例で、ラジアル動圧溝31は全長にわたって形成さ
れておらず、一端側に偏って形成されている。この場
合、長い溝部31bは軸方向中間部からやや他端側(図
1(b)で下端側)までしか延びておらず、その先端か
ら他端までの内周面21は平滑な円筒面である。また、
短い溝部31aは内周面取り部22には開放しておら
ず、したがってラジアル動圧溝31は内周面21におい
て閉じている。The bearing body 11 of FIG. 1B is a modification of FIG. 1A, in which the radial dynamic pressure groove 31 is not formed over the entire length, but is formed to be biased toward one end. In this case, the long groove portion 31b extends only slightly from the axial middle portion to the other end (the lower end in FIG. 1B), and the inner peripheral surface 21 from the tip to the other end is a smooth cylindrical surface. is there. Also,
The short groove portion 31a is not open to the inner peripheral chamfered portion 22, so that the radial dynamic pressure groove 31 is closed on the inner peripheral surface 21.
【0026】第1実施形態の軸受体11は、図1(a)
の形態を基本としており、図1(b)のような変形例が
考えられる。この他の変形例としては、図1(a)のラ
ジアル動圧溝31の両端部が内周面取り部22に開放し
ておらず内周面21において閉じている形態や、図1
(b)に示すラジアル動圧溝31が、他端側(図1
(b)で下端側)に形成されている形態が挙げられる。
また、このように一端側にラジアル動圧溝31を形成
し、他端側には本発明に係らない従来公知のラジアル動
圧溝が形成されていてもよい。The bearing body 11 of the first embodiment is shown in FIG.
1B, and a modified example as shown in FIG. 1B can be considered. As another modified example, both ends of the radial dynamic pressure groove 31 of FIG. 1A are not opened to the inner peripheral chamfered portion 22 but are closed at the inner peripheral surface 21, and FIG.
The radial dynamic pressure groove 31 shown in FIG.
(B) at the lower end).
Further, the radial dynamic pressure groove 31 may be formed on one end side, and a conventionally known radial dynamic pressure groove not related to the present invention may be formed on the other end side.
【0027】上記の第1実施形態に係る軸受体11は、
図8あるいは図9に示した軸受1A,1Bの軸受体3と
して適用される。図2は、図9の軸受1Bに適用した例
を示している。この場合は、2つの軸受体11を、間隔
をおいてハウジング2の端部にそれぞれ圧入しており、
各軸受体11のラジアル動圧溝31の収束部32は図示
せぬ回転軸の回転方向(矢印R方向)に収束しており、
かつ、収束部32はそれぞれ端部側に偏っている。な
お、この場合のラジアル動圧溝31の両端は内周面取り
部22には開放しておらず、内周面21において閉じて
いる。このような軸受11Aによれば、2つの軸受体1
1のラジアル動圧溝31の収束部32が端部側に偏って
いるので、油圧が高い収束部32間の距離が長くなり、
換言すると、回転軸を動圧作用によって主に支持する2
点間の距離を長くとることができる。このため、動圧作
用がより高まって回転軸の振れや倒れを抑える剛性が向
上し、かつ、回転軸との摩擦抵抗が大幅に低減する。ま
た、端面に湧出する潤滑油がラジアル動圧溝31の端部
側の溝部31aを経て収束部32に流動させられ、これ
によって回転軸の回転による端面側への潤滑油の漏洩が
抑えられる。The bearing body 11 according to the first embodiment is
It is applied as the bearing body 3 of the bearings 1A and 1B shown in FIG. 8 or FIG. FIG. 2 shows an example applied to the bearing 1B of FIG. In this case, the two bearing bodies 11 are press-fitted into the ends of the housing 2 at intervals.
The converging portion 32 of the radial dynamic pressure groove 31 of each bearing body 11 converges in the rotation direction (the direction of arrow R) of the rotating shaft (not shown),
In addition, the converging portions 32 are each biased toward the end. In this case, both ends of the radial dynamic pressure groove 31 are not open to the inner peripheral chamfered portion 22 but are closed on the inner peripheral surface 21. According to such a bearing 11A, the two bearing bodies 1
Since the converging portion 32 of the radial dynamic pressure groove 31 is biased toward the end, the distance between the converging portions 32 with high hydraulic pressure becomes longer,
In other words, 2 which mainly supports the rotating shaft by the dynamic pressure action
The distance between points can be increased. For this reason, the dynamic pressure action is further increased, the rigidity for suppressing the run-out and fall of the rotary shaft is improved, and the frictional resistance with the rotary shaft is greatly reduced. Further, the lubricating oil flowing out to the end face is caused to flow to the converging portion 32 through the groove 31a on the end side of the radial dynamic pressure groove 31, thereby suppressing leakage of the lubricating oil to the end face side due to rotation of the rotating shaft.
【0028】また、図8の軸受1Aに軸受体11を適用
する場合は、両端部にラジアル動圧溝31が形成されて
いるか、あるいは一端側にラジアル動圧溝31が形成さ
れ、他端側には従来公知のラジアル動圧溝が形成されて
いる形態が適用される。この適用例では、1つの軸受体
11の両端側の油圧の高い部分の間の距離が、本発明に
係るラジアル動圧溝31の収束部32が端部側に形成さ
れていることにより従来よりも長くなる。したがって、
上記と同様に回転軸の振れや倒れを抑える剛性が向上
し、かつ、回転軸との摩擦抵抗が大幅に低減する。When the bearing body 11 is applied to the bearing 1A shown in FIG. 8, the radial dynamic pressure grooves 31 are formed at both ends, or the radial dynamic pressure grooves 31 are formed at one end and the other end is formed. In this case, a conventionally known form in which a radial dynamic pressure groove is formed is applied. In this application example, the distance between the high oil pressure portions on both ends of one bearing body 11 is smaller than that of the conventional one because the converging portion 32 of the radial dynamic pressure groove 31 according to the present invention is formed on the end side. Is also longer. Therefore,
As described above, the rigidity for suppressing the run-out and fall of the rotary shaft is improved, and the frictional resistance with the rotary shaft is greatly reduced.
【0029】(2)第2実施形態 次に、内周面にラジアル荷重を受けるとともに、一端面
にスラスト荷重を受ける軸受の実施形態を説明する。図
3(a)に示す軸受体12の内周面21には、周方向に
等間隔をおいて複数のラジアル動圧溝31が形成されて
いる。これらラジアル動圧溝31は、矢印Rで示す図示
せぬ回転軸の回転方向に収束する略V字状であって、全
体としてヘリングボーン模様をなしている。ラジアル動
圧溝31は、内周面21の全長にわたって形成されてお
り、その両端部は内周面取り部22に開放している。こ
の場合のラジアル動圧溝31の収束部32は軸方向の中
間部に位置しており、ラジアル動圧溝31は周方向に対
して対称的に形成されている。(2) Second Embodiment Next, an embodiment of a bearing which receives a radial load on the inner peripheral surface and a thrust load on one end surface will be described. A plurality of radial dynamic pressure grooves 31 are formed at equal intervals in the circumferential direction on the inner peripheral surface 21 of the bearing body 12 shown in FIG. These radial dynamic pressure grooves 31 have a substantially V-shape converging in the direction of rotation of a rotating shaft (not shown) indicated by an arrow R, and have a herringbone pattern as a whole. The radial dynamic pressure groove 31 is formed over the entire length of the inner peripheral surface 21, and both ends thereof are open to the inner peripheral chamfered portion 22. In this case, the converging portion 32 of the radial dynamic pressure groove 31 is located at an intermediate portion in the axial direction, and the radial dynamic pressure groove 31 is formed symmetrically with respect to the circumferential direction.
【0030】一方、軸受体12の一端側(図3(a)の
上端側)の端面24には、複数のスラスト動圧溝35
が、周方向に等間隔をおいて放射状に形成されている。
これらスラスト動圧溝35は、図4(a)に示すよう
に、回転軸の回転方向Rに向かうにしたがって外周側か
ら内周側にやや湾曲しながら延びている。図4(a)の
場合のスラスト動圧溝35は端面24内において閉じて
いるが、図4(b)に示すように、内周側の端部が内周
面21(あるいは内周面取り部22)に開放しており、
かつ、外周側の端部が外周面25(あるいは外周面取り
部23)に開放している形態であってもよい。図3
(a)のスラスト動圧溝35は、外周側の端部は端面2
4内において閉じている一方、内周側の端部は内周面取
り部22に開放しており、スラスト動圧溝35は内周面
取り部22を介してラジアル動圧溝31に連通してい
る。On the other hand, a plurality of thrust dynamic pressure grooves 35 are provided on the end face 24 on one end side (upper end side in FIG. 3A) of the bearing body 12.
Are radially formed at equal intervals in the circumferential direction.
As shown in FIG. 4A, the thrust dynamic pressure grooves 35 extend while slightly bending from the outer peripheral side to the inner peripheral side in the rotation direction R of the rotating shaft. The thrust dynamic pressure groove 35 in the case of FIG. 4A is closed in the end face 24, but as shown in FIG. 4B, the end on the inner circumferential side is the inner circumferential face 21 (or the inner circumferential chamfered portion). 22)
Further, the outer peripheral side end may be open to the outer peripheral surface 25 (or the outer peripheral chamfered portion 23). FIG.
The outer peripheral end of the thrust dynamic pressure groove 35 in FIG.
4, the inner peripheral end is open to the inner peripheral chamfer 22, and the thrust dynamic pressure groove 35 communicates with the radial dynamic pressure groove 31 via the inner peripheral chamfer 22. .
【0031】図3(b)および図3(c)に示す軸受体
12は、第2実施形態の変形例である。図3(b)の軸
受体12は、図1(a)で示したようにラジアル動圧溝
31の収束部32が一端側(図3(b)で上端側)に偏
っており、これによって、V字状をなす2つの溝部31
a,31bのうちのスラスト動圧溝35が形成された端
面24側の溝部31aの長さが他方の溝部31bよりも
短く形成されている。図3(c)の軸受体12は、図1
(b)で示したようなラジアル動圧溝31がスラスト動
圧溝35が形成された一端側(図3(c)で上端側)に
偏っており、スラスト動圧溝35は内周面取り部22を
介してラジアル動圧溝31と連通している。The bearing body 12 shown in FIGS. 3B and 3C is a modification of the second embodiment. In the bearing body 12 of FIG. 3B, the converging portion 32 of the radial dynamic pressure groove 31 is biased toward one end (the upper end in FIG. 3B) as shown in FIG. , Two V-shaped grooves 31
The length of the groove 31a on the end face 24 side where the thrust dynamic pressure groove 35 is formed is shorter than the other groove 31b. The bearing body 12 shown in FIG.
3B, the radial dynamic pressure groove 31 is biased toward one end (the upper end in FIG. 3C) where the thrust dynamic pressure groove 35 is formed, and the thrust dynamic pressure groove 35 is an inner peripheral chamfer. It is in communication with the radial dynamic pressure groove 31 via 22.
【0032】上記の第2実施形態に係る軸受体12は、
図10あるいは図11に示した軸受1C,1Dの軸受体
3として適用される。図5は、図3(c)に示した軸受
体12を図10の軸受1Cに適用した例を示している。
この軸受12Aは、軸受体12に挿入された図示せぬ回
転軸のフランジは、スラスト動圧溝35が形成された端
面24に摺動し、これによってスラスト動圧溝35には
潤滑油が供給されて動圧作用が起こり、摩擦が低減され
る。スラスト動圧溝35は、矢印Rで示す回転軸の回転
方向に向かうにしたがって外周側から内周側に延びてお
り、これらが略放射状に配列されているので、供給され
た潤滑油は回転軸の回転によって内周側に積極的に流動
していく。これによって、外周側への潤滑油の漏洩が抑
えられるとともに、内周側の油圧が高くなって内周面2
1の端部への潤滑油の供給が促され、内周面21の摩擦
低減が図られる。特に、ラジアル動圧溝31の収束部3
2はスラスト動圧溝35が形成された端部側に偏ってお
り、かつ、スラスト動圧溝35は内周面取り部22を介
してラジアル動圧溝31に連通しているので、スラスト
動圧溝35が形成された端面からラジアル動圧溝31に
わたる軸孔端部の内周面の油圧が高くなりやすく、ラジ
アル側の摺動特性が一層向上する。The bearing body 12 according to the second embodiment is
It is applied as the bearing body 3 of the bearings 1C and 1D shown in FIG. 10 or FIG. FIG. 5 shows an example in which the bearing body 12 shown in FIG. 3C is applied to the bearing 1C of FIG.
In this bearing 12A, a flange of a rotating shaft (not shown) inserted into the bearing body 12 slides on the end face 24 on which the thrust dynamic pressure groove 35 is formed, whereby lubricating oil is supplied to the thrust dynamic pressure groove 35. As a result, a dynamic pressure action occurs, and friction is reduced. The thrust dynamic pressure grooves 35 extend from the outer peripheral side to the inner peripheral side in the direction of rotation of the rotating shaft indicated by the arrow R. Since these are arranged in a substantially radial manner, the supplied lubricating oil is rotated by the rotating shaft. With the rotation of, it flows positively toward the inner circumference. As a result, the leakage of the lubricating oil to the outer peripheral side is suppressed, and the hydraulic pressure on the inner peripheral side is increased to increase the inner peripheral surface 2.
The supply of the lubricating oil to the end portion 1 is promoted, and the friction of the inner peripheral surface 21 is reduced. In particular, the converging portion 3 of the radial dynamic pressure groove 31
2 is biased toward the end where the thrust dynamic pressure groove 35 is formed, and since the thrust dynamic pressure groove 35 communicates with the radial dynamic pressure groove 31 via the inner peripheral chamfered portion 22, the thrust dynamic pressure The hydraulic pressure on the inner peripheral surface at the end of the shaft hole extending from the end face where the groove 35 is formed to the radial dynamic pressure groove 31 is likely to be increased, and the sliding characteristics on the radial side are further improved.
【0033】図6(a)は図3(a)に示した軸受体1
2を図11の軸受1Dに適用した例を示し、図6(b)
は図3(b)に示した軸受体12を図11の軸受1Dに
適用した例を示している。図6(a)の軸受12Bは、
図3(a)に示した軸受体12がハウジング2の一端部
(図6(a)で上端部)に圧入して配置され、他端部に
は図3(a)に示した軸受体12において端面24にス
ラスト動圧溝35が形成されていない一般的な軸受体5
が圧入して配置されている。この例では、スラスト動圧
溝35を有する軸受体12として、図3(b)あるいは
図3(c)に示した軸受体12を適用してもよい。ま
た、他端側のスラスト動圧溝35が無い軸受体5として
は、図1(a)あるいは図1(b)に示した軸受体11
を適用してもよい。FIG. 6A shows the bearing 1 shown in FIG.
FIG. 6B shows an example in which No. 2 is applied to the bearing 1D of FIG.
Shows an example in which the bearing body 12 shown in FIG. 3B is applied to the bearing 1D of FIG. The bearing 12B of FIG.
The bearing body 12 shown in FIG. 3A is press-fitted into one end of the housing 2 (the upper end in FIG. 6A), and the other end is provided with the bearing body 12 shown in FIG. , A general bearing body 5 in which the thrust dynamic pressure groove 35 is not formed on the end face 24
Are press-fitted and arranged. In this example, as the bearing body 12 having the thrust dynamic pressure groove 35, the bearing body 12 shown in FIG. 3B or 3C may be applied. Further, as the bearing body 5 having no thrust dynamic pressure groove 35 on the other end side, the bearing body 11 shown in FIG. 1A or FIG.
May be applied.
【0034】図6(b)の軸受12Cは、スラスト動圧
溝35を有する軸受体12がハウジング2の一端部(図
6(b)で上端部)に圧入して配置され、他端部には、
ラジアル動圧溝31もスラスト動圧溝35も形成されて
いない内周面21が平滑な円筒状の軸受体6が圧入して
配置されている。スラスト動圧溝35を有する軸受体1
2は、図3(b)の軸受体12の変形例であって、ラジ
アル動圧溝31における内部側(図6(b)で下端側)
の端部が内周面取り部22に開放しておらず、内周面2
1において閉じている。In the bearing 12C of FIG. 6B, the bearing body 12 having the thrust dynamic pressure groove 35 is press-fitted into one end (the upper end in FIG. 6B) of the housing 2, and is arranged at the other end. Is
A cylindrical bearing body 6 having a smooth inner peripheral surface 21 on which neither the radial dynamic pressure groove 31 nor the thrust dynamic pressure groove 35 is formed is press-fitted. Bearing body 1 having thrust dynamic pressure groove 35
Reference numeral 2 denotes a modified example of the bearing body 12 shown in FIG. 3B, and the inner side of the radial dynamic pressure groove 31 (the lower end side in FIG. 6B).
Is not open to the inner peripheral chamfered portion 22, and the inner peripheral surface 2
Closed at 1.
【0035】図6(a),(b)に示す軸受12A,1
2Cにおいても、スラスト動圧溝35とラジアル動圧溝
31とによる相乗的な効果によって、回転軸の回転によ
る動圧作用やスラスト動圧溝35が形成された端面24
における潤滑油の漏洩抑制効果を上記軸受12Aと同様
に得ることができる。The bearings 12A, 12 shown in FIGS.
Also in 2C, due to a synergistic effect of the thrust dynamic pressure groove 35 and the radial dynamic pressure groove 31, the end face 24 on which the thrust dynamic pressure groove 35 is formed and the dynamic pressure action by the rotation of the rotating shaft is formed.
Can be obtained in the same manner as in the bearing 12A.
【0036】(3)第3実施形態 次に、図7を参照して本発明に係る第3実施形態を説明
する。図7に示す軸受体13は、矢印R方向に回転する
回転軸からラジアル荷重を受ける内周面21が軸方向両
端部に形成されており、これら内周面21の間に、内周
面21よりも大径で回転軸が接触しない中逃げ部41が
形成されている。図7で下側の内周面21に対応する外
径は他の部分よりも小径であり、この軸受体13は小径
部42と大径部43とを有している。中逃げ部41は、
外径が均一で、かつ、内径が、小径部42に対応する部
分の内径が中逃げ部41と同径であった軸受素材の小径
部42に対応する部分の外周を、金型で縮径させること
によって形成することができる。軸受体13の2つの内
周面21には、図2で示したものと同様のラジアル動圧
溝31が形成されている。また、大径部43側の端面2
4には、内周面取り部22に開放するスラスト動圧溝3
5が形成されている。(3) Third Embodiment Next, a third embodiment according to the present invention will be described with reference to FIG. The bearing body 13 shown in FIG. 7 has inner peripheral surfaces 21 that receive a radial load from a rotating shaft rotating in the direction of arrow R formed at both axial ends, and an inner peripheral surface 21 between these inner peripheral surfaces 21. A middle escape portion 41 having a larger diameter than the rotary shaft does not contact is formed. The outer diameter corresponding to the lower inner peripheral surface 21 in FIG. 7 is smaller than the other parts, and this bearing body 13 has a small diameter part 42 and a large diameter part 43. The middle escape part 41 is
The outer circumference of the portion corresponding to the small diameter portion 42 of the bearing material, in which the outer diameter is uniform and the inner diameter of the portion corresponding to the small diameter portion 42 is the same as the middle relief portion 41, is reduced in diameter by a mold. And can be formed. A radial dynamic pressure groove 31 similar to that shown in FIG. 2 is formed on the two inner peripheral surfaces 21 of the bearing body 13. Also, the end face 2 on the large diameter portion 43 side
4 includes a thrust dynamic pressure groove 3 which is open to the inner peripheral chamfered portion 22.
5 are formed.
【0037】第3実施形態の軸受体13は、例えば図1
0に示した軸受1Cに適用され、その場合は、スラスト
動圧溝35が形成された大径部43側の端面24に回転
軸のフランジが摺動する形態で用いられる。この軸受体
13によれば、内周面21の両端部側に、各ラジアル動
圧溝31の収束部32が偏っていることから回転軸を動
圧作用によって主に支持する2点間の距離を長くなり、
動圧作用がより高まって回転軸の振れや倒れを抑える剛
性が向上し、かつ、回転軸との摩擦抵抗が大幅に低減す
る。また、スラスト動圧溝35とラジアル動圧溝31と
による相乗的な効果によって、回転軸の回転による動圧
作用やスラスト動圧溝35が形成された端面24におけ
る潤滑油の漏洩抑制効果を、上記第2実施形態と同様に
得ることができる。さらに、小径部42側の内周面21
においては、内周面取り部22近傍に溜まる潤滑油がラ
ジアル動圧溝31の短い溝部31aに吸引される作用が
生じ、潤滑油の飛散が抑えられて動圧作用を効果的に得
ることができる。The bearing body 13 of the third embodiment is, for example, shown in FIG.
This is applied to the bearing 1C shown in FIG. 0, in which case the flange of the rotary shaft slides on the end face 24 on the large diameter portion 43 side where the thrust dynamic pressure groove 35 is formed. According to the bearing body 13, since the converging portions 32 of the radial dynamic pressure grooves 31 are biased toward both ends of the inner peripheral surface 21, the distance between two points that mainly support the rotating shaft by dynamic pressure action. Become longer,
The dynamic pressure action is further enhanced, the rigidity for suppressing the runout and fall of the rotary shaft is improved, and the frictional resistance with the rotary shaft is greatly reduced. Further, the synergistic effect of the thrust dynamic pressure groove 35 and the radial dynamic pressure groove 31 reduces the dynamic pressure effect due to the rotation of the rotating shaft and the lubricating oil leakage suppressing effect on the end face 24 where the thrust dynamic pressure groove 35 is formed. It can be obtained in the same manner as in the second embodiment. Furthermore, the inner peripheral surface 21 on the small diameter portion 42 side
In this case, the lubricating oil accumulated near the inner peripheral chamfered portion 22 is sucked into the short groove portion 31a of the radial dynamic pressure groove 31, so that the scattering of the lubricating oil is suppressed and the dynamic pressure effect can be obtained effectively. .
【0038】また、この軸受体13は、図11に示した
スピンドルモータ用軸受1Dとしても好適に用いられ
る。その場合、回転軸の回転によって両端部のラジアル
動圧溝31の収束部32付近の油圧が最も高くなる。ラ
ジアル動圧溝31はラジアル荷重を受ける内周面21全
周にわたって形成されているので、回転軸が振れ周りし
ても潤滑油はその内周面21に対し絶えることなく一様
に供給され、動圧作用が常に生じながら回転軸はスムー
ズに回転することができる。回転軸が回転すると、フラ
ンジが摺動する側の端面24ではスラスト動圧溝35に
より動圧作用が生じ、スラスト荷重を受けてもスムーズ
な摺動がなされるとともに、潤滑油はラジアル動圧溝3
1に流動して内周面21のラジアル動圧溝31の油圧が
より高まる。一方、小径部42側の内周面21において
は、スラスト受板と軸受体との間の空間に潤滑油が存在
すると、その潤滑油はラジアル動圧溝31によって内周
面21に吸引され、これによって動圧作用が効果的に発
生する。The bearing 13 is also suitably used as the spindle motor bearing 1D shown in FIG. In this case, the oil pressure near the converging portion 32 of the radial dynamic pressure groove 31 at both ends becomes highest due to the rotation of the rotating shaft. Since the radial dynamic pressure groove 31 is formed over the entire circumference of the inner peripheral surface 21 that receives the radial load, even if the rotating shaft oscillates, the lubricating oil is constantly and uniformly supplied to the inner peripheral surface 21. The rotating shaft can rotate smoothly while the dynamic pressure action always occurs. When the rotating shaft rotates, a dynamic pressure action is generated by the thrust dynamic pressure groove 35 on the end surface 24 on which the flange slides, and smooth sliding is performed even when a thrust load is received, and the lubricating oil is moved in the radial dynamic pressure groove. 3
1 and the hydraulic pressure in the radial dynamic pressure groove 31 of the inner peripheral surface 21 is further increased. On the other hand, when lubricating oil is present in the space between the thrust receiving plate and the bearing body on the inner peripheral surface 21 on the small diameter portion 42 side, the lubricating oil is sucked into the inner peripheral surface 21 by the radial dynamic pressure groove 31, This effectively produces a dynamic pressure effect.
【0039】[0039]
【発明の効果】以上説明したように、本発明の動圧軸受
によれば、動圧作用がより高まって回転軸との摩擦抵抗
が大幅に低減する動圧溝を効果的に形成しているので、
回転軸の高速回転化に対応可能な動圧軸受としてきわめ
て有望である。As described above, according to the dynamic pressure bearing of the present invention, the dynamic pressure groove in which the dynamic pressure action is further enhanced and the frictional resistance with the rotating shaft is greatly reduced is effectively formed. So
It is very promising as a dynamic pressure bearing that can cope with high-speed rotation of a rotating shaft.
【図1】 (a),(b)は本発明の第1実施形態に係
る軸受体の縦割り断面図である。FIGS. 1A and 1B are longitudinal sectional views of a bearing body according to a first embodiment of the present invention.
【図2】 本発明の第1実施形態に係る軸受の断面図で
ある。FIG. 2 is a sectional view of the bearing according to the first embodiment of the present invention.
【図3】 (a),(b),(c)は本発明の第2実施
形態に係る軸受体の縦割り断面図である。FIGS. 3 (a), (b) and (c) are longitudinal sectional views of a bearing body according to a second embodiment of the present invention.
【図4】 本発明に係るスラスト動圧溝を示す軸受体の
上面図である。FIG. 4 is a top view of a bearing body showing a thrust dynamic pressure groove according to the present invention.
【図5】 本発明の第2実施形態に係る軸受の断面図で
ある。FIG. 5 is a sectional view of a bearing according to a second embodiment of the present invention.
【図6】 (a),(b)は本発明の第2実施形態に係
る別形態の軸受の断面図である。FIGS. 6A and 6B are cross-sectional views of another type of bearing according to the second embodiment of the present invention.
【図7】 本発明の第3実施形態に係る軸受体の断面図
である。FIG. 7 is a sectional view of a bearing according to a third embodiment of the present invention.
【図8】 一般的な軸受の構造例を示す縦割り断面図で
ある。FIG. 8 is a longitudinal sectional view showing a structural example of a general bearing.
【図9】 一般的な軸受の構造の他の例を示す縦割り断
面図である。FIG. 9 is a vertical sectional view showing another example of the structure of a general bearing.
【図10】 一般的な軸受の構造の他の例を示す縦割り
断面図である。FIG. 10 is a longitudinal sectional view showing another example of a general bearing structure.
【図11】 一般的な軸受の構造の他の例を示す縦割り
断面図である。FIG. 11 is a vertical sectional view showing another example of the structure of a general bearing.
4…回転軸 11,12,13…軸受体 11A,12A,12B,12C…軸受 21…内周面 22…内周面取り部 31…ラジアル動圧溝 31a,31b…溝部 32…収束部 35…スラスト動圧溝 DESCRIPTION OF SYMBOLS 4 ... Rotating shaft 11, 12, 13 ... Bearing body 11A, 12A, 12B, 12C ... Bearing 21 ... Inner peripheral surface 22 ... Inner peripheral chamfered part 31 ... Radial dynamic pressure groove 31a, 31b ... Groove part 32 ... Convergent part 35 ... Thrust Dynamic pressure groove
───────────────────────────────────────────────────── フロントページの続き Fターム(参考) 3J011 AA10 AA11 AA12 BA02 BA08 CA03 JA02 KA02 KA03 LA01 MA03 5H605 BB05 BB14 CC04 DD03 EA06 EB06 EB17 GG09 GG14 5H607 BB01 BB14 BB25 CC01 DD03 DD16 GG01 GG09 GG12 ──────────────────────────────────────────────────続 き Continued on front page F term (reference) 3J011 AA10 AA11 AA12 BA02 BA08 CA03 JA02 KA02 KA03 LA01 MA03 5H605 BB05 BB14 CC04 DD03 EA06 EB06 EB17 GG09 GG14 5H607 BB01 BB14 BB25 CC01 DD03 DD16 GG01 GG09 GG09
Claims (10)
に、回転軸の回転方向に収束する複数の略V字状のラジ
アル動圧溝がヘリングボーン模様に形成され、このラジ
アル動圧溝の収束部が、軸方向一端側に偏っており、か
つ、略V字状をなすラジアル動圧溝の一方および他方の
各溝部のうちの前記一端側の溝部が、反対側の溝部より
も短く形成されていることを特徴とする動圧軸受。A plurality of substantially V-shaped radial dynamic pressure grooves converging in the rotation direction of the rotation shaft are formed in a herringbone pattern on an inner peripheral surface receiving a radial load from the rotation shaft. The converging portion is biased toward one end in the axial direction, and the groove on one end of one and the other of the radial dynamic pressure grooves forming a substantially V shape is formed shorter than the groove on the opposite side. A dynamic pressure bearing characterized by being made.
の少なくとも軸方向一端側に、回転軸の回転方向に収束
する複数の略V字状のラジアル動圧溝がヘリングボーン
模様に形成され、略V字状をなすラジアル動圧溝の一方
および他方の各溝部のうちの前記一端側の溝部が、反対
側の溝部よりも短く形成されていることを特徴とする動
圧軸受。2. A plurality of substantially V-shaped radial dynamic pressure grooves converging in the rotation direction of the rotating shaft are formed in a herringbone pattern on at least one axial end of an inner peripheral surface receiving a radial load from the rotating shaft, A dynamic pressure bearing, wherein the groove on one end of one and the other of the substantially dynamic V-shaped radial dynamic pressure grooves is formed shorter than the groove on the opposite side.
が、軸方向に間隔をおいて2箇所以上形成された動圧軸
受であって、軸方向の端部側に形成された各内周面の少
なくとも一方に、回転軸の回転方向に収束し、その収束
部が外側の端部側に偏った複数の略V字状のラジアル動
圧溝がヘリングボーン模様に形成され、かつ、略V字状
をなすラジアル動圧溝の一方および他方の各溝部のうち
の前記外側の端部側の溝部が、反対側の溝部よりも短く
形成されていることを特徴とする動圧軸受。3. A hydrodynamic bearing in which two or more inner peripheral surfaces receiving a radial load from a rotating shaft are formed at intervals in an axial direction, and each inner peripheral surface formed on an axial end portion side. A plurality of substantially V-shaped radial dynamic pressure grooves are formed in a herringbone pattern on at least one of the surfaces, the plurality of substantially dynamic V-shaped grooves being converged in the direction of rotation of the rotation shaft, and the converged portion is biased toward the outer end side. A dynamic pressure bearing, wherein a groove on the outer end side of one and the other of the radial dynamic pressure grooves having a letter shape is formed shorter than a groove on the opposite side.
端面に、回転軸の回転方向に向かうにしたがって外周側
から内周側に延びる複数のスラスト動圧溝が略放射状に
形成されているとともに、回転軸からラジアル荷重を受
ける内周面に、回転軸の回転方向に収束する複数の略V
字状のラジアル動圧溝がヘリングボーン模様に形成され
ていることを特徴とする動圧軸受。4. A plurality of thrust dynamic pressure grooves which extend from the outer peripheral side to the inner peripheral side as going in the rotation direction of the rotary shaft are formed substantially radially on one end face which receives a thrust load from the rotary shaft. A plurality of substantially Vs converging in the rotation direction of the rotating shaft are provided on an inner peripheral surface receiving a radial load from the rotating shaft.
A hydrodynamic bearing in which a U-shaped radial dynamic pressure groove is formed in a herringbone pattern.
端面に、回転軸の回転方向に向かうにしたがって外周側
から内周側に延びる複数のスラスト動圧溝が略放射状に
形成されているとともに、回転軸からラジアル荷重を受
ける内周面に、回転軸の回転方向に収束する複数の略V
字状のラジアル動圧溝がヘリングボーン模様に形成さ
れ、さらに、ラジアル動圧溝の収束部が、前記スラスト
動圧溝が形成された端面側に偏っており、かつ、略V字
状をなすラジアル動圧溝の一方および他方の各溝部のう
ちのスラスト動圧溝が形成された端面側の溝部が、反対
側の溝部よりも短く形成されていることを特徴とする動
圧軸受。5. A plurality of thrust dynamic pressure grooves extending radially from an outer peripheral side to an inner peripheral side in a rotation direction of the rotating shaft are formed on one end face of the rotating shaft, which receives a thrust load from the rotating shaft. A plurality of substantially Vs converging in the rotation direction of the rotating shaft are provided on an inner peripheral surface receiving a radial load from the rotating shaft.
A radial dynamic pressure groove having a V-shape is formed in a herringbone pattern, and a converging portion of the radial dynamic pressure groove is biased toward the end face side where the thrust dynamic pressure groove is formed, and has a substantially V shape. A dynamic pressure bearing, wherein a groove on the end face side of the radial dynamic pressure groove on which the thrust dynamic pressure groove is formed is shorter than a groove on the opposite side.
端面に、回転軸の回転方向に向かうにしたがって外周側
から内周側に延びる複数のスラスト動圧溝が略放射状に
形成されているとともに、回転軸からラジアル荷重を受
ける内周面の少なくとも前記スラスト動圧溝が形成され
た端面側の端部に、回転軸の回転方向に収束する複数の
略V字状のラジアル動圧溝がヘリングボーン模様に形成
され、さらに、前記スラスト動圧溝が形成された端面側
に形成されたラジアル動圧溝の収束部が、スラスト動圧
溝が形成された端面側に偏っており、かつ、略V字状を
なすラジアル動圧溝の一方および他方の各溝部のうちの
スラスト動圧溝が形成された端面側の溝部が、反対側の
溝部よりも短く形成されていることを特徴とする動圧軸
受。6. A plurality of thrust dynamic pressure grooves extending radially from an outer peripheral side toward an inner peripheral side in a direction of rotation of the rotary shaft are formed on one end face of the rotary shaft receiving a thrust load from the rotary shaft. A plurality of substantially V-shaped radial dynamic pressure grooves converging in the direction of rotation of the rotary shaft are herringbone at least at the end of the inner peripheral surface receiving the radial load from the rotary shaft on the end face side where the thrust dynamic pressure grooves are formed. Further, the converging portion of the radial dynamic pressure groove formed on the end face side where the thrust dynamic pressure groove is formed is biased toward the end face side where the thrust dynamic pressure groove is formed, and substantially V The dynamic pressure is characterized in that, of the radial dynamic pressure grooves having a U-shape, the groove on the end face side where the thrust dynamic pressure groove is formed is shorter than the groove on the opposite side. bearing.
が、軸方向に間隔をおいて2箇所以上形成された動圧軸
受であって、軸方向の端部に形成された前記内周面に連
続する端面に、回転軸の回転方向に向かうにしたがって
外周側から内周側に延びる複数のスラスト動圧溝が略放
射状に形成されているとともに、内周面の少なくとも前
記スラスト動圧溝が形成された側の端部に、回転軸の回
転方向に収束する複数の略V字状のラジアル動圧溝がヘ
リングボーン模様に形成され、さらに、スラスト動圧溝
が形成された端面側に形成されたラジアル動圧溝の収束
部が、スラスト動圧溝が形成された端面側に偏ってお
り、かつ、略V字状をなすラジアル動圧溝の一方および
他方の各溝部のうちのスラスト動圧溝が形成された端面
側の溝部が、反対側の溝部よりも短く形成されているこ
とを特徴とする動圧軸受。7. A hydrodynamic bearing in which two or more inner peripheral surfaces receiving a radial load from a rotating shaft are formed at intervals in an axial direction, wherein the inner peripheral surface is formed at an axial end. A plurality of thrust dynamic pressure grooves extending from the outer peripheral side to the inner peripheral side as going in the rotation direction of the rotating shaft are formed in a substantially radial shape on the end face continuous with, and at least the thrust dynamic pressure grooves on the inner peripheral face are A plurality of substantially V-shaped radial dynamic pressure grooves converging in the rotating direction of the rotating shaft are formed in a herringbone pattern at an end on the formed side, and further formed on an end face side where the thrust dynamic pressure grooves are formed. The converging portion of the formed radial dynamic pressure groove is biased toward the end face side where the thrust dynamic pressure groove is formed, and the thrust motion of one and the other of the substantially V-shaped radial dynamic pressure grooves is changed. The groove on the end face side where the pressure groove is formed A dynamic pressure bearing characterized by being formed shorter than the groove.
記ラジアル動圧溝におけるスラスト動圧溝が形成された
端面側の溝部の端部とが、直接または軸孔の端縁に形成
された面取り部を介して連通していることを特徴とする
請求項4〜7のいずれかに記載の動圧軸受。8. An inner peripheral end of the thrust dynamic pressure groove and an end of the radial dynamic pressure groove on an end face side where the thrust dynamic pressure groove is formed, directly or at an edge of a shaft hole. The dynamic pressure bearing according to any one of claims 4 to 7, wherein the dynamic pressure bearing communicates via a formed chamfer.
記ラジアル動圧溝におけるスラスト動圧溝が形成された
端面側の溝部の端部とが対応して近接していることを特
徴とする請求項4〜8のいずれかに記載の動圧軸受。9. An inner peripheral end portion of the thrust dynamic pressure groove and an end portion of the radial dynamic pressure groove on an end face side where the thrust dynamic pressure groove is formed are correspondingly close to each other. The dynamic pressure bearing according to any one of claims 4 to 8, wherein:
請求項1〜9のいずれかに記載の動圧軸受。10. The dynamic pressure bearing according to claim 1, which is a sintered oil-impregnated bearing.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2001053683A JP2002257132A (en) | 2001-02-28 | 2001-02-28 | Dynamic pressure bearing |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2001053683A JP2002257132A (en) | 2001-02-28 | 2001-02-28 | Dynamic pressure bearing |
Publications (1)
Publication Number | Publication Date |
---|---|
JP2002257132A true JP2002257132A (en) | 2002-09-11 |
Family
ID=18914118
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP2001053683A Pending JP2002257132A (en) | 2001-02-28 | 2001-02-28 | Dynamic pressure bearing |
Country Status (1)
Country | Link |
---|---|
JP (1) | JP2002257132A (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2009049070A3 (en) * | 2007-10-09 | 2009-07-02 | Smartin Technologies Llc | Compact non-contact mechanical coupling, damping and/or load bearing device |
CN106089692A (en) * | 2016-07-01 | 2016-11-09 | 魏宇坤 | A kind of cryogenic liquid pump self-lubricating contact device and method |
-
2001
- 2001-02-28 JP JP2001053683A patent/JP2002257132A/en active Pending
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2009049070A3 (en) * | 2007-10-09 | 2009-07-02 | Smartin Technologies Llc | Compact non-contact mechanical coupling, damping and/or load bearing device |
US8562217B2 (en) | 2007-10-09 | 2013-10-22 | Smartin Technologies Llc | Compact non-contact mechanical coupling, damping and/or load bearing device |
CN106089692A (en) * | 2016-07-01 | 2016-11-09 | 魏宇坤 | A kind of cryogenic liquid pump self-lubricating contact device and method |
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