JPH0143847B2 - - Google Patents

Info

Publication number
JPH0143847B2
JPH0143847B2 JP11958082A JP11958082A JPH0143847B2 JP H0143847 B2 JPH0143847 B2 JP H0143847B2 JP 11958082 A JP11958082 A JP 11958082A JP 11958082 A JP11958082 A JP 11958082A JP H0143847 B2 JPH0143847 B2 JP H0143847B2
Authority
JP
Japan
Prior art keywords
thrust bearing
thrust
bearing member
groove
shaft body
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
Application number
JP11958082A
Other languages
Japanese (ja)
Other versions
JPS5913113A (en
Inventor
Hiromi Sugi
Kyosaburo Furumura
Hiromitsu Asai
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
NSK Ltd
Original Assignee
NSK Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by NSK Ltd filed Critical NSK Ltd
Priority to JP11958082A priority Critical patent/JPS5913113A/en
Publication of JPS5913113A publication Critical patent/JPS5913113A/en
Publication of JPH0143847B2 publication Critical patent/JPH0143847B2/ja
Granted legal-status Critical Current

Links

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
    • F16C17/10—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

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Chemical & Material Sciences (AREA)
  • Oil, Petroleum & Natural Gas (AREA)
  • Sliding-Contact Bearings (AREA)

Description

【発明の詳細な説明】 この発明は、動圧形スラスト軸受に関し、とく
に、スラスト受部材を有する軸体を、スラスト軸
受部材を有するハウジングの内周に配設し、スラ
スト軸受部材とスラスト受部材との少なくとも一
方に動圧発生用のみぞを設けた動圧形スラスト軸
受において、スラスト軸受部材とスラスト受部材
との少なくとも一方には動圧発生用のみぞの流出
端側に環状凸部が突設され、スラスト軸受すき間
から環状凸部を通つて流出する潤滑剤の循環通路
を設けることにより、軸体の浮上量（軸方向変位
量）を安定させ、大きいスラスト負荷能力が得ら
れるようにしたものである。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a dynamic pressure type thrust bearing, and in particular, a shaft body having a thrust bearing member is disposed on the inner periphery of a housing having a thrust bearing member, and the thrust bearing member and the thrust bearing member are connected to each other. In a hydrodynamic type thrust bearing in which at least one of the thrust bearing member and the thrust receiving member is provided with a groove for generating dynamic pressure, an annular protrusion protrudes on the outflow end side of the groove for generating dynamic pressure. By providing a circulation path for the lubricant that flows out from the thrust bearing gap through the annular convex part, the floating height (axial displacement amount) of the shaft body is stabilized, and a large thrust load capacity can be obtained. It is something.

従来、この種の動圧形スラスト軸受として第１
図および第２図に示すものが知られている。両図
において、符号１は軸体、２はスラスト受部材、
３はハウジング４のスラスト軸受部をそれぞれ示
し、第１図のスラスト軸受部３のスラスト受面５
には、スパイラル状のみぞ６を形成され、第２図
のスラスト軸受部３のスラスト受面５には、ヘリ
ングボーン状のみぞ６が形成されている。 Conventionally, it was the first hydrodynamic thrust bearing of this type.
What is shown in FIG. 2 and FIG. 2 is known. In both figures, numeral 1 is a shaft body, 2 is a thrust receiving member,
3 indicates the thrust bearing portion of the housing 4, and the thrust bearing surface 5 of the thrust bearing portion 3 in FIG.
A spiral groove 6 is formed in the thrust bearing surface 5 of the thrust bearing portion 3 shown in FIG.

上記の軸体１が回転すると、みぞ６のポンピン
グ作用による動圧が発生して、潤滑剤がスラスト
軸受部３のスラスト受面５とスラスト受部材２の
スラスト端面７との間のスラスト軸受すき間８に
流入し、これにより軸体１が浮上してスラスト荷
重を支持する。 When the above-mentioned shaft body 1 rotates, dynamic pressure is generated due to the pumping action of the groove 6, and the lubricant is applied to the thrust bearing gap between the thrust bearing surface 5 of the thrust bearing part 3 and the thrust end surface 7 of the thrust bearing member 2. 8, which causes the shaft body 1 to float and support the thrust load.

上記の軸受をフラツトモータ等に使用する場合
は、軸体１に固定したロータとハウジング４に固
定したステータとが軸方向の微小すき間を隔てて
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、すなわち軸体１の浮上量を小さくして
安定させる必要がある。 When the above bearing is used in a flat motor etc., the rotor fixed to the shaft body 1 and the stator fixed to the housing 4 face each other on a plane with a small gap in the axial direction. It is necessary to stabilize the displacement, that is, the flying height of the shaft body 1 by reducing it.

しかし、スラスト軸受部３に動圧発生用のみぞ
６のみが設けられている従来の軸受では、軸体１
の停止時と回転時とにおける軸方向の位置が大き
く変化し、スラスト荷重が変化した場合や周囲温
度により油やグリース等の潤滑剤の粘度が変化し
た場合には軸体の浮上量に大きな変動が生ずるた
め、軸方向の位置が安定しないという欠点があ
る。とくに、第１図の軸受では、スラスト軸受部
３の内周縁から軸体１との間のすき間を通つて潤
滑剤が漏出するので、潤滑剤の圧力上昇が妨げら
れてスラスト負荷能力が低下する欠点がある。さ
らに、第１図および第２図の軸受の両者とも、ス
ラスト受部材２のスラスト端面７が、スラスト軸
受部３のスラスト受面５に大きな面積で接触して
いるため、起動トルクが大きい欠点がある。 However, in a conventional bearing in which only the groove 6 for generating dynamic pressure is provided in the thrust bearing part 3, the shaft body 1
If the axial position changes significantly between when the shaft is stopped and when it rotates, and if the thrust load changes or if the viscosity of lubricant such as oil or grease changes due to ambient temperature, the flying height of the shaft will change significantly. Since this occurs, there is a drawback that the axial position is unstable. In particular, in the bearing shown in FIG. 1, the lubricant leaks through the gap between the inner peripheral edge of the thrust bearing part 3 and the shaft body 1, which prevents the pressure of the lubricant from increasing and reduces the thrust load capacity. There are drawbacks. Furthermore, in both of the bearings shown in FIG. 1 and FIG. 2, the thrust end face 7 of the thrust bearing member 2 is in contact with the thrust bearing surface 5 of the thrust bearing part 3 over a large area, so the starting torque is large. be.

この発明は、上記の欠点を除去するためになさ
れたものであり、この発明の目的は、軸体の浮上
量が安定する動圧形スラスト軸受を提供すること
にあり、また、この発明の目的は、起動トルクが
小さく、大きいスラスト負荷能力が得られる動圧
形スラスト軸受を提供することにある。 This invention was made to eliminate the above-mentioned drawbacks, and an object of the invention is to provide a hydrodynamic thrust bearing in which the flying height of the shaft body is stable; The object of the present invention is to provide a dynamic pressure type thrust bearing that has a small starting torque and a large thrust load capacity.

すなわち、この発明は、図示する実施例のよう
に、スラスト軸受部材１５を有するハウジング１
０の内周にスラスト受部材３０を有する軸体４０
を配設し、スラスト軸受部材１５に設けたスラス
ト受面１６とスラスト受部材３０に設けたスラス
ト端面３２とが対向し、スラスト受面１６とスラ
スト端面３２との少なくとも一方に動圧発生用の
みぞ２０を設けた動圧形スラスト軸受において、
前記スラスト受面１６とスラスト端面３２との少
なくとも一方には動圧発生用のみぞ２０の流出端
側に沿つて環状凸部１８が同心状に突設され、軸
体４０の停止時に前記環状凸部１８を介してスラ
スト軸受部材１５とスラスト受部材３０とを接触
させ、軸体４０の回転時にスラスト軸受すき間３
４から環状凸部１８を通つて流出する潤滑剤をス
ラスト軸受すき間３４に還流させる循環通路を設
けたことを特徴とする動圧形スラスト軸受に係
る。以下、この発明の実施例について、図面を参
照して説明する。 That is, the present invention provides a housing 1 having a thrust bearing member 15 as in the illustrated embodiment.
A shaft body 40 having a thrust receiving member 30 on the inner circumference of
The thrust receiving surface 16 provided on the thrust bearing member 15 and the thrust end surface 32 provided on the thrust receiving member 30 face each other, and at least one of the thrust receiving surface 16 and the thrust end surface 32 has a structure for generating dynamic pressure. In a hydrodynamic thrust bearing with grooves 20,
At least one of the thrust receiving surface 16 and the thrust end surface 32 is provided with an annular protrusion 18 concentrically protruding along the outflow end side of the groove 20 for generating dynamic pressure. The thrust bearing member 15 and the thrust bearing member 30 are brought into contact via the portion 18, and the thrust bearing clearance 3 is closed when the shaft body 40 rotates.
The present invention relates to a dynamic pressure type thrust bearing characterized in that a circulation passage is provided for circulating lubricant flowing out from the lubricant 4 through the annular convex portion 18 into the thrust bearing gap 34. Embodiments of the present invention will be described below with reference to the drawings.

第３図は、この発明の第１実施例である。ハウ
ジング部材９には、同一中心軸線を有する小径の
円筒穴１１と大径の円筒穴１２とが、それぞれ上
下方向に開口して設けられている。小径の円筒孔
１１には、円筒状体のスリーブ１３を嵌合して固
定し、大径の円筒孔１２には、スラスト軸受部材
１５を嵌合し、該円筒孔１２の底面に密着させて
固定してある。ハウジング１０はハウジング部材
９とスリーブ１３とスラスト軸受部材１５とから
構成され、スリーブ１３は、その内周面にラジア
ル内面１４が形成されたラジアル軸受部材であ
る。スラスト軸受部材１５は、前記スリーブ１３
と同一の内径を有する円盤状体であり、スラスト
受面１６には、内周縁に沿つて環状凸部１８を同
心状に設け、該環状凸部１８の外側縁からスラス
ト受面１６の外周縁までの間にスパイラル状の動
圧発生用のみぞ２０が設けてある（同図ｂ参照）。
この環状凸部１８のスラスト受面１６からの高さ
は、数10μｍを限定として適宜選定する。また、
スラスト軸受部材１５の底面には、半径方向に連
通溝２１を設け、該連通溝２１を外周面の軸方向
に設けた流通溝２２に連通させてある。この連通
溝２１と流通溝２２とは、図示実施例のように１
組に限らず、複数組として設けてもよい。 FIG. 3 shows a first embodiment of the invention. The housing member 9 is provided with a small-diameter cylindrical hole 11 and a large-diameter cylindrical hole 12 having the same central axis and opening in the vertical direction, respectively. A cylindrical sleeve 13 is fitted and fixed in the small diameter cylindrical hole 11, and a thrust bearing member 15 is fitted in the large diameter cylindrical hole 12 and brought into close contact with the bottom surface of the cylindrical hole 12. It is fixed. The housing 10 is composed of a housing member 9, a sleeve 13, and a thrust bearing member 15, and the sleeve 13 is a radial bearing member having a radial inner surface 14 formed on its inner peripheral surface. The thrust bearing member 15 includes the sleeve 13
The thrust receiving surface 16 is provided with an annular convex portion 18 concentrically along the inner circumferential edge, and extends from the outer edge of the annular convex portion 18 to the outer circumferential edge of the thrust receiving surface 16. A spiral groove 20 for generating dynamic pressure is provided between the two ends (see b in the same figure).
The height of this annular convex portion 18 from the thrust receiving surface 16 is appropriately selected with a limit of several tens of micrometers. Also,
A communication groove 21 is provided in the bottom surface of the thrust bearing member 15 in the radial direction, and the communication groove 21 is communicated with a communication groove 22 provided in the axial direction on the outer peripheral surface. The communication groove 21 and the circulation groove 22 are connected to one another as in the illustrated embodiment.
It is not limited to one set, but may be provided as a plurality of sets.

上記のハウジング１０のスリーブ１３およびス
ラスト軸受部材１５には、スラスト受部材３０を
一体に成形した軸体４０を、スラスト受部材３０
を大径の円筒穴１２内に配置して貫通させてあ
る。スラスト受部材３０には、前記スラスト軸受
部材１５のスラスト受面１６に対向する平面状の
スラスト端面３２が形成され、軸体４０の停止時
においては、スラスト端面３２は、前記スラスト
軸受部材１５の環状凸部１８の上端面に接触し
て、スラスト軸受部材１５のスラスト受面１６と
の間にスラスト軸受すき間３４を形成している。
また、軸体４０には、スリーブ１３のラジアル内
面１４に対向するラジアル外面４４が形成され、
スリーブ１３のラジアル内面１４との間に、ラジ
アル軸受すき間４６を形成している。軸体４０の
ラジアル外面４４には、頂部がスラスト軸受部材
１５側に偏位した非対称のヘリングボーン状のみ
ぞ５０が設けてある。 The sleeve 13 and the thrust bearing member 15 of the housing 10 are provided with a shaft body 40 integrally molded with the thrust bearing member 30.
is arranged in a large diameter cylindrical hole 12 and penetrated therethrough. The thrust bearing member 30 is formed with a planar thrust end face 32 that faces the thrust bearing surface 16 of the thrust bearing member 15. When the shaft body 40 is stopped, the thrust end face 32 is formed on the thrust bearing member 15. A thrust bearing gap 34 is formed between the annular convex portion 18 and the thrust bearing surface 16 of the thrust bearing member 15 by contacting the upper end surface of the annular convex portion 18 .
Further, the shaft body 40 is formed with a radial outer surface 44 that faces the radial inner surface 14 of the sleeve 13,
A radial bearing gap 46 is formed between the sleeve 13 and the radial inner surface 14 . The radial outer surface 44 of the shaft body 40 is provided with an asymmetric herringbone-shaped groove 50 whose top portion is deviated toward the thrust bearing member 15 side.

上記の構成により、ハウジング１０のスリーブ
１３およびスラスト軸受部材１５を介してそれぞ
れ半径方向および軸方向に支持された軸体４０が
回転すると、スラスト軸受部材１５のスラスト受
面１６に設けてあるスパイラル状のみぞ２０のポ
ンピング作用による動圧が発生して、スラスト軸
受すき間３４に潤滑剤（この実施例では油、グリ
ースまたは空気等の気体）が半径方向内側に向つ
て流入する。軸体４０の回転初期においては、ス
ラスト受部材３０がスラスト軸受部材１５の環状
凸部１８の上端面に接触して、スラスト軸受すき
間３４に流入した潤滑剤の流出を遮断しているた
め、軸体４０の回転が進行するにつれて潤滑剤の
圧力が上昇して環状凸部１８における圧力が最も
高くなる。このようにして、潤滑剤の圧力が一定
の高さに上昇した時点で、スラスト受部材３０に
上向きの力が作用して軸体４０が浮上する。軸体
４０の浮上によつて、スラスト受部材３０と環状
凸部１８との間にすき間ｈができると、潤滑剤
が、環状凸部１８を超えてスラスト軸受部材１５
と軸体４０との間のすき間４８に流出するように
なるから、潤滑剤の圧力は低下する。潤滑剤が環
状凸部１８を超えて流出しても、軸体４０のラジ
アル外面４４には、非対称のヘリングボーン状の
みぞ５０が設けてあり、このみぞ５０による動圧
がラジアル軸受すき間４６に発生しているから、
ハウジング１０の外部に漏出することはなく、ス
ラスト軸受部材１５の連通溝２１と流通溝２２と
を経て再びスラスト軸受すき間３４に流入する。
このように、スラスト軸受部材１５と軸体４０と
の間のすき間４８と、スラスト軸受部材１５の連
通溝２１と、流通溝２２とを相互に連通させて、
潤滑剤の循環通路を形成し、環状凸部１８を超え
て流出した潤滑剤をスラスト軸受部材１５の周り
を循環させることにより、潤滑剤の圧力を一定に
保持することができるから、軸体４０が浮上した
ときのスラスト受部材３０とスラスト軸受部材１
５の環状凸部１８との間には、常時一定のすき間
ｈが維持されて軸体４０の浮上量が安定し、一定
のスラスト負荷能力が得られるとともに、軸体４
０の浮上量も小さくなる。 With the above configuration, when the shaft body 40 supported in the radial direction and the axial direction via the sleeve 13 and the thrust bearing member 15 of the housing 10 rotates, the spiral shape provided on the thrust bearing surface 16 of the thrust bearing member 15 rotates. Dynamic pressure is generated by the pumping action of the groove 20, and the lubricant (in this embodiment, a gas such as oil, grease, or air) flows radially inward into the thrust bearing gap 34. In the initial stage of rotation of the shaft body 40, the thrust bearing member 30 contacts the upper end surface of the annular convex portion 18 of the thrust bearing member 15 and blocks the outflow of the lubricant that has flowed into the thrust bearing gap 34. As the rotation of the body 40 progresses, the pressure of the lubricant increases and the pressure at the annular convex portion 18 becomes the highest. In this way, when the pressure of the lubricant increases to a certain level, an upward force acts on the thrust receiving member 30, causing the shaft body 40 to float. When a gap h is created between the thrust bearing member 30 and the annular convex portion 18 due to the floating of the shaft body 40, the lubricant passes over the annular convex portion 18 and flows into the thrust bearing member 15.
Since the lubricant flows into the gap 48 between the lubricant and the shaft 40, the pressure of the lubricant decreases. Even if the lubricant flows out beyond the annular convex portion 18, the radial outer surface 44 of the shaft body 40 is provided with an asymmetric herringbone-shaped groove 50, and the dynamic pressure due to this groove 50 is applied to the radial bearing clearance 46. Because it is occurring,
It does not leak out of the housing 10, but flows into the thrust bearing gap 34 again through the communication groove 21 and the circulation groove 22 of the thrust bearing member 15.
In this way, the gap 48 between the thrust bearing member 15 and the shaft body 40, the communication groove 21 of the thrust bearing member 15, and the circulation groove 22 are made to communicate with each other,
By forming a lubricant circulation passage and circulating the lubricant that has flowed out beyond the annular convex portion 18 around the thrust bearing member 15, the pressure of the lubricant can be kept constant. Thrust bearing member 30 and thrust bearing member 1 when floating
A constant gap h is always maintained between the shaft body 40 and the annular convex portion 18 of the shaft body 40, the flying height of the shaft body 40 is stabilized, and a constant thrust load capacity is obtained.
The flying height at 0 also becomes smaller.

なお、スラスト軸受部材１５の内径寸法をスリ
ーブ１３の内径寸法よりも大きくしてもよい。 Note that the inner diameter of the thrust bearing member 15 may be larger than the inner diameter of the sleeve 13.

第４図は、第３図で説明した第１実施例の変形
例である。この変形例では、スラスト軸受部材１
５のスラスト受面１６にヘリングボーン状の動圧
発生用のみぞ２０を設け、該みぞ２０の頂部（流
出端側）に２条の環状凸部１８を適宜の間隔をお
いて隣接させて設けてある。この環状凸部１８の
間の凹部に軸方向の循環孔２３を設け、該循環孔
２３を底部の半径方向に設けた連通溝２１に連通
させ、連通溝２１は外周面の軸方向に設けた流通
溝２２に連通させてある。また、ハウジング１０
の小径の円筒穴１１は、その内周面をラジアル内
面として軸体４０を貫通させ、軸体４０のラジア
ル外面４４には、スパイラル状のみぞ５０が設け
てある。 FIG. 4 shows a modification of the first embodiment explained in FIG. In this modification, the thrust bearing member 1
A herringbone-shaped groove 20 for generating dynamic pressure is provided in the thrust receiving surface 16 of 5, and two annular protrusions 18 are provided adjacently at an appropriate interval at the top of the groove 20 (outflow end side). There is. An axial circulation hole 23 is provided in the recess between the annular protrusions 18, and the circulation hole 23 is communicated with a communication groove 21 provided in the radial direction of the bottom, and the communication groove 21 is provided in the axial direction on the outer peripheral surface. It is communicated with the flow groove 22. In addition, housing 10
The small-diameter cylindrical hole 11 passes through the shaft body 40 with its inner peripheral surface serving as a radial inner surface, and a spiral groove 50 is provided in the radial outer surface 44 of the shaft body 40.

上記構成の軸受において、軸体４０が回転する
と、ヘリングボーン状のみぞ２０の動圧によつて
スラスト軸受すき間３４に流入した潤滑剤は、み
ぞ２０の頂部において最も高い圧力に上昇する。
これにより、軸体４０が浮上し、スラスト受部材
３０と環状凸部１８との間にすき間ｈができる
と、潤滑剤が環状凸部１８を超えて循環孔２３に
流出するので、その後は圧力が上昇することはな
く、一定のすき間ｈが維持された平衡状態とな
り、軸体４０の浮上量が安定する。循環孔２３に
流出した潤滑剤は、スラスト軸受部材１５の連通
溝２１から分岐してスラスト軸受部材１５と軸体
４０との間のすき間４８と流通溝２２とを経てス
ラスト軸受すき間３４に還流する。スラスト軸受
部材１５と軸体４０との間のすき間４８に流出し
た潤滑剤は、軸体４０のラジアル外面４４に設け
たスパイラル状のみぞ５０の動圧によつて、外部
への漏出が挿止される。 In the bearing configured as described above, when the shaft body 40 rotates, the lubricant flowing into the thrust bearing gap 34 due to the dynamic pressure in the herringbone-shaped groove 20 rises to the highest pressure at the top of the groove 20.
As a result, when the shaft body 40 floats and a gap h is created between the thrust receiving member 30 and the annular protrusion 18, the lubricant flows out into the circulation hole 23 over the annular protrusion 18. does not rise, resulting in an equilibrium state in which a constant gap h is maintained, and the flying height of the shaft body 40 is stabilized. The lubricant flowing into the circulation hole 23 branches from the communication groove 21 of the thrust bearing member 15, passes through the gap 48 between the thrust bearing member 15 and the shaft body 40, and the circulation groove 22, and then flows back into the thrust bearing gap 34. . The lubricant leaking into the gap 48 between the thrust bearing member 15 and the shaft body 40 is prevented from leaking to the outside by the dynamic pressure of the spiral groove 50 provided on the radial outer surface 44 of the shaft body 40. be done.

なお、循環孔２３から連通溝２１を通つて連通
溝２２に通ずる循環通路と、循環孔２３から連通
溝２１を通つてスラスト軸受部材と軸体との間の
すき間４８に通ずる循環通路とを別々に設けても
よい。 Note that the circulation passage from the circulation hole 23 to the communication groove 22 through the communication groove 21 and the circulation passage from the circulation hole 23 to the gap 48 between the thrust bearing member and the shaft body through the communication groove 21 are separated. may be provided.

第５図は、この発明の第２実施例である。この
実施例では、ハウジング部材９の円筒穴１１の下
端を溝形断面のラジアル軸受部材１３で閉塞し
て、軸体４０のラジアル外面４４側の端部を密閉
し、軸体４０のラジアル外面４４には、上下対称
のヘリングボーン状のみぞ５０を設けている。ス
ラスト軸受部材１５の構成は、第３図の場合と同
一であるから同一部分には同一符号を付して示
す。軸体４０の回転時における潤滑剤は、第３図
の実施例と同一の循環通路を経て還流する。 FIG. 5 shows a second embodiment of the invention. In this embodiment, the lower end of the cylindrical hole 11 of the housing member 9 is closed with the radial bearing member 13 having a groove-shaped cross section, the end on the radial outer surface 44 side of the shaft body 40 is sealed, and the radial outer surface 44 of the shaft body 40 is sealed. is provided with a vertically symmetrical herringbone-shaped groove 50. The configuration of the thrust bearing member 15 is the same as that shown in FIG. 3, so the same parts are designated by the same reference numerals. When the shaft body 40 rotates, the lubricant flows back through the same circulation path as in the embodiment shown in FIG.

第６図は、第５図の実施例の変形例であり、軸
体４０のラジアル外面４４部分を小径に成形し
て、軸６７に別体のスラスト受部材３０を固着し
た場合を示し、軸体４０のラジアル外面４４には
動圧発生用のみぞを設けないで、ハウジング１０
の円筒孔１１に直接挿入してある。 FIG. 6 shows a modification of the embodiment shown in FIG. 5, in which the radial outer surface 44 portion of the shaft body 40 is formed to have a small diameter, and a separate thrust receiving member 30 is fixed to the shaft 67. The housing 10 is not provided with a groove for generating dynamic pressure on the radial outer surface 44 of the body 40.
It is directly inserted into the cylindrical hole 11 of.

上記第３図ないし第５図の実施例においては、
軸体４０のラジアル外面４４に動圧発生用のみぞ
５０が設けてあるが、このみぞ５０は、ハウジン
グ１０側に設けることもできる。 In the embodiments shown in FIGS. 3 to 5 above,
A groove 50 for generating dynamic pressure is provided on the radial outer surface 44 of the shaft body 40, but this groove 50 may also be provided on the housing 10 side.

なお、スラスト軸受部材１５の内径寸法を円筒
孔１１の内径寸法より小さくし、スラスト軸受部
材１５のラジアル内面と、スラスト軸受部材１５
のラジアル内面に対向する軸体４０のラジアル外
面との少なくとも一方にヘリングボーン状のみぞ
又はスパイラル状のみぞを形成してもよい。 Note that the inner diameter of the thrust bearing member 15 is made smaller than the inner diameter of the cylindrical hole 11, so that the radial inner surface of the thrust bearing member 15 and the thrust bearing member 15
A herringbone groove or a spiral groove may be formed in at least one of the radial inner surface of the shaft body 40 and the opposing radial outer surface of the shaft body 40 .

第７図は、この発明をスピンドルユニツトに適
用した場合を示す第３実施例である。このスピン
ドルユニツトは、ラジアル軸受部６０ａとスラス
ト軸受部６０ｂとを一体に成形した動圧軸受部材
６０とラジアル軸受部材６２とを、それぞれハウ
ング部材９の上下両側に嵌着して、軸体４０の上
方のラジアル外面４４ａを動圧軸受部材６０のラ
ジアル軸受部６０ａにより、下方のラジアル外面
４４ｂをラジアル軸受部材６２によりそれぞれ半
径方向に支持している。軸体４０の上方のラジア
ル外面４４ａには上下非対称のヘリングボーン状
のみぞ５０ａが設けられ、また下方のラジアル外
面４４ｂには、上下対称のヘリングボーン状のみ
ぞ５０ｂが設けてある。ハウジング１０の両側端
部には、磁性流体シール６５を設け、ハウジング
１０内に封入された油、グリース等の潤滑剤の漏
出を防止している。 FIG. 7 shows a third embodiment in which the present invention is applied to a spindle unit. In this spindle unit, a hydrodynamic bearing member 60 and a radial bearing member 62, which are integrally molded with a radial bearing part 60a and a thrust bearing part 60b, are fitted to the upper and lower sides of the housing member 9, respectively, and the shaft body 40 is The upper radial outer surface 44a is supported in the radial direction by a radial bearing portion 60a of the dynamic pressure bearing member 60, and the lower radial outer surface 44b is supported in the radial direction by a radial bearing member 62. The upper radial outer surface 44a of the shaft body 40 is provided with a vertically asymmetrical herringbone-shaped groove 50a, and the lower radial outer surface 44b is provided with a vertically symmetrical herringbone-shaped groove 50b. Magnetic fluid seals 65 are provided at both ends of the housing 10 to prevent leakage of lubricants such as oil and grease sealed within the housing 10.

上記の動圧軸受部材６０のスラスト軸受部６０
ｂのスラスト受面には、前記第３図の実施例と同
様にスパイラル状の動圧発生用のみぞ２０と環状
凸部１８とが設けてある。 Thrust bearing portion 60 of the above hydrodynamic bearing member 60
The thrust receiving surface b is provided with a spiral groove 20 for generating dynamic pressure and an annular convex portion 18, similar to the embodiment shown in FIG.

動圧軸受部材６０のスラスト軸受部６０ｂと対
向するスラスト受部材３０は、軸６７と一体に成
形されているが、このスラスト受部材３０には、
軸６７との接合部に軸方向の循環孔３５が設けて
ある。 The thrust bearing member 30, which faces the thrust bearing portion 60b of the hydrodynamic bearing member 60, is integrally formed with the shaft 67.
An axial circulation hole 35 is provided at the joint with the shaft 67.

上記構成の軸受において、軸体４０が回転して
スラスト軸受すき間に３４流入した潤滑剤の圧力
が上昇し、スラスト受部材３０とスラスト軸受部
６０ｂの環状凸部１８との間にすき間ができて軸
体４０が浮上すると、環状凸部１８を超えて流出
した潤滑剤は、スラスト受部材３０の循環孔３５
に流出し、該循環孔３５からスラスト受部材３０
の反スラスト端面とハウジング１０との間のすき
間を経て、スラスト受部材３０の外周面とハウジ
ング１０との間のすき間を通り、スラスト軸受す
き間３４に還流して一定の圧力を保持する。 In the bearing configured as described above, as the shaft body 40 rotates, the pressure of the lubricant flowing into the thrust bearing gap 34 increases, and a gap is created between the thrust bearing member 30 and the annular convex portion 18 of the thrust bearing portion 60b. When the shaft body 40 floats, the lubricant flowing out beyond the annular convex portion 18 flows into the circulation hole 35 of the thrust receiving member 30.
from the circulation hole 35 to the thrust receiving member 30.
It passes through the gap between the anti-thrust end surface of the thrust bearing member 30 and the housing 10, passes through the gap between the outer peripheral surface of the thrust bearing member 30 and the housing 10, and returns to the thrust bearing gap 34 to maintain a constant pressure.

なお潤滑剤として空気を使用し、上方の磁性流
体シール６５を省略すると、軸体４０の回転時に
スラスト軸受すき間３４から環状凸部１８を通つ
て流出する潤滑剤が循環孔３５から外部に排出さ
れる。 Note that when air is used as the lubricant and the upper magnetic fluid seal 65 is omitted, the lubricant flowing out from the thrust bearing gap 34 through the annular convex portion 18 when the shaft body 40 rotates is discharged to the outside from the circulation hole 35. Ru.

第８図は、第７図の実施例の変形例であり、軸
６７が大径部４１と小径部４２とからなり、スラ
スト受部材３０を軸６７の小径部４２に嵌合して
固着した場合における潤滑剤の循環通路を示した
ものである。スラスト受部材３０の内周面の軸方
向に循環孔３５を設け、該循環孔３５の中間位置
とスラスト受部材３０の外周面との間に半径方向
の連通孔３６が設けてある。このようにすると、
循環孔３５に流入した潤滑剤が連通孔３６を経て
スラスト受部材３０の外周面に流出するから、潤
滑剤の流出方向を第７図のように軸方向ではな
く、半径方向に規制することができる。したがつ
て、ハウジング１０の両側端部、とくに、スラス
ト受部材３０側の端部を容易に密封できる。ハウ
ジング１０の両側端部にシール体６５を固定し、
このシール体６５と対向する軸体４０の外周面に
は、スパイラル状のみぞ５１ａ，５１ｂが設けて
ある。 FIG. 8 shows a modification of the embodiment shown in FIG. 7, in which the shaft 67 consists of a large diameter portion 41 and a small diameter portion 42, and the thrust receiving member 30 is fitted and fixed to the small diameter portion 42 of the shaft 67. This figure shows the lubricant circulation path in this case. A circulation hole 35 is provided in the axial direction of the inner peripheral surface of the thrust receiving member 30, and a radial communication hole 36 is provided between an intermediate position of the circulation hole 35 and the outer peripheral surface of the thrust receiving member 30. In this way,
Since the lubricant that has flowed into the circulation hole 35 flows out to the outer circumferential surface of the thrust receiving member 30 through the communication hole 36, the direction of the lubricant flow can be restricted to the radial direction rather than the axial direction as shown in FIG. can. Therefore, both ends of the housing 10, especially the end on the thrust receiving member 30 side, can be easily sealed. Seal bodies 65 are fixed to both ends of the housing 10,
Spiral grooves 51a and 51b are provided on the outer peripheral surface of the shaft body 40 facing the seal body 65.

第７図および第８図の実施例においては、動圧
軸受部材を一体形のものとして構成しているか
ら、軸受の組立が簡単にできるだけでなく、動圧
軸受部材を合成樹脂製とする場合においては、ス
ラスト軸受部とラジアル軸受部との双方に同時加
工により動圧発生用のみぞを設けることができ、
成形加工もきわめて容易になる。 In the embodiments shown in FIGS. 7 and 8, since the hydrodynamic bearing member is constructed as an integral piece, it is not only possible to assemble the bearing easily, but also when the hydrodynamic bearing member is made of synthetic resin. In this case, grooves for generating dynamic pressure can be provided in both the thrust bearing part and the radial bearing part by simultaneous machining.
Molding processing also becomes extremely easy.

前記第３図ないし第８図の各実施例において、
軸体を回転させる場合に限らず、ハウジングを回
転させるようにしてもよい。 In each of the embodiments shown in FIGS. 3 to 8,
In addition to rotating the shaft, the housing may also be rotated.

またハウジング１０をハウジング部材９とスリ
ーブ１３とスラスト軸受部材１５とから構成しな
いで、ハウジング１０を一つの部材から構成して
もよく、複数の部材から構成してもよい。 Moreover, the housing 10 may not be composed of the housing member 9, the sleeve 13, and the thrust bearing member 15, but may be composed of one member, or may be composed of a plurality of members.

さらに、動圧形スラスト軸受を縦形でなく、横
形でも倒置しても使用できる。 Furthermore, the dynamic pressure type thrust bearing can be used not only vertically but also horizontally or upside down.

第９図ないし第１３図は、この発明をフロツピ
ーデイスク駆動用モータ（フラツトモータ）の軸
受に適用した使用例である。 9 to 13 show examples of use of the present invention in a bearing of a floppy disk drive motor (flat motor).

第９図は、第１使用例を示し、同図において、
符号４０は軸体、７０は軸体４０に固着された回
転盤、７２は回転盤の頭部、７４は固定盤、７５
は固定盤７４に固着されたハウジング部材、１３
は軸体４０を半径方向に支持するスリーブ、１５
は回転盤７０を軸方向に支持するスラスト軸受部
材、７６はシール体、７８はロータ、８０はステ
ータをそれぞれ示す。 FIG. 9 shows a first usage example, in which:
40 is a shaft body, 70 is a rotary disk fixed to the shaft body 40, 72 is a head of the rotary disk, 74 is a fixed plate, 75
13 is a housing member fixed to a fixed platen 74;
15 is a sleeve that supports the shaft body 40 in the radial direction;
, a thrust bearing member that supports the rotary disk 70 in the axial direction, 76 a seal body, 78 a rotor, and 80 a stator, respectively.

第１０図は、第９図のハウジング部材７５、ス
リーブ１３およびスラスト軸受部材１５を拡大し
て示したものである。スリーブ１３の内周面に
は、ヘリングボーン状の動圧発生用のみぞ５０が
設けられている。スラスト軸受部材１５のスラス
ト受面１６には、内周縁に環状凸部１８を設け、
外周線にはスパイラル状の動圧発生用のみぞ２０
が設けてある。このみぞ２０は、トルクを小さく
する必要からスラスト受面１６の全面でなく、外
周縁に近接した一部分にのみ狭い幅で設ける。ま
た、スラスト軸受部材１５の内周面の軸方向に循
環溝２４を設け、該循環溝２４を底面の半径方向
に設けた連通溝２１を介して外周面の軸方向に設
けた流通溝２２に連通させてある。 FIG. 10 is an enlarged view of the housing member 75, sleeve 13, and thrust bearing member 15 shown in FIG. The inner peripheral surface of the sleeve 13 is provided with a herringbone-shaped groove 50 for generating dynamic pressure. The thrust bearing surface 16 of the thrust bearing member 15 is provided with an annular convex portion 18 on the inner peripheral edge.
There is a spiral groove 20 on the outer circumference for generating dynamic pressure.
is provided. This groove 20 is provided with a narrow width not on the entire surface of the thrust receiving surface 16 but only on a portion close to the outer peripheral edge in order to reduce the torque. Further, a circulation groove 24 is provided in the axial direction on the inner peripheral surface of the thrust bearing member 15, and the circulation groove 24 is connected to the circulation groove 22 provided in the axial direction on the outer peripheral surface via the communication groove 21 provided in the radial direction on the bottom surface. It has been communicated.

第１１図および第１２図は、それぞれ第１０図
の第１変形例および第２変形例である。 11 and 12 are a first modification and a second modification of FIG. 10, respectively.

第１１図は、スラスト軸受部材１５のスラスト
受面１６の外周縁の一部に設けたスパイラル状の
みぞ２０の内側縁に沿つて環状凸部１８を設け、
該環状凸部１８の内側に循環孔２３を設けて該循
環孔２３を連通溝２１を介して流通溝２２に連通
させた場合を示し、第１２図は、スラスト軸受部
材１５のスラスト受面１６の外周縁の一部にヘリ
ングボーン状のみぞ２０を設け、該みぞ２０の頂
部に２条の環状凸部１８をそれぞれ設け、該環状
凸部１８の間に設けた循環孔２３ａとみぞ２０の
内側に設けた循環孔２３ｂと流通溝２２とをそれ
ぞれ連通溝２１に連通させた場合を示す。 In FIG. 11, an annular convex portion 18 is provided along the inner edge of a spiral groove 20 provided on a part of the outer peripheral edge of the thrust bearing surface 16 of the thrust bearing member 15,
A case is shown in which a circulation hole 23 is provided inside the annular convex portion 18 and the circulation hole 23 is communicated with the circulation groove 22 via the communication groove 21. FIG. A herringbone-shaped groove 20 is provided in a part of the outer peripheral edge of the groove 20, two annular protrusions 18 are provided at the top of the groove 20, and a circulation hole 23a provided between the annular protrusions 18 and the groove 20 are provided. A case is shown in which the circulation hole 23b and the circulation groove 22 provided on the inside are respectively communicated with the communication groove 21.

第１３図は、第２使用例を示し、軸体４０のラ
ジアル外面側部を固定盤７４に貫通して、スラス
ト軸受部材１５を倒置形とした場合である。符号
１３はスリーブ、３０は軸体４０に固着されたス
ラスト受部材、７０はスラスト受部材３０に固着
された回転盤、７２は軸体４０の上端に固着され
た頭部、７５は固定盤７４に固着されたハウジン
グ部材、７８はロータ、８０はスラータをそれぞ
れ示す。スラスト軸受部材１５の構成は前記第３
図の場合と同様であり、軸体４０のラジアル外面
には非対称のヘリングボーン状のみぞ５０が設け
てある。 FIG. 13 shows a second usage example, in which the radial outer surface side of the shaft body 40 penetrates the fixed platen 74, and the thrust bearing member 15 is made into an inverted type. 13 is a sleeve, 30 is a thrust receiving member fixed to the shaft body 40, 70 is a rotary disk fixed to the thrust receiving member 30, 72 is a head fixed to the upper end of the shaft body 40, and 75 is a fixed plate 74. 78 is a rotor, and 80 is a sluter, respectively. The structure of the thrust bearing member 15 is the same as that of the third
Similar to the case shown in the figure, the radial outer surface of the shaft body 40 is provided with an asymmetrical herringbone-shaped groove 50.

上記第９図ないし第１３図の軸受において、軸
体４０が回転したときの軸体４０の浮上および潤
滑剤の循環の作動は、前述した第３図ないし第６
図の場合と同様であるが、とくにこのようなフラ
ツトモータにこの発明を適用することにより、回
転盤７０がスラスト軸受部材１５の環状凸部１８
との間の微少すき間に油膜または気体膜を形成し
て、スラスト軸受部材１５のスラスト受面１６に
対して平行状態を保持して回転するから、スラス
ト軸受部材１５のスラスト受面１６がスリーブ１
３のラジアル内面１４に対して正確に垂直になる
ようにしておけば、回転盤７０のアキシアル振れ
が小さくなり、これによつて、回転盤７０の頭部
７２の側面におけるラジアル振れを小さくするこ
とができ、きわめて高い回転精度を安定して得る
ことが可能となる。 In the bearings shown in FIGS. 9 to 13 above, the floating of the shaft 40 and the circulation of lubricant when the shaft 40 rotates are similar to those shown in FIGS. 3 to 6 described above.
Although it is similar to the case shown in the figure, by applying the present invention to such a flat motor in particular, the rotary disk 70 can be attached to the annular convex portion 18 of the thrust bearing member 15.
The thrust bearing surface 16 of the thrust bearing member 15 rotates while maintaining a parallel state to the thrust bearing surface 16 of the thrust bearing member 15 by forming an oil film or a gas film in a minute gap between the sleeve 1 and the sleeve 1.
3, the axial runout of the rotary disk 70 can be reduced, thereby reducing the radial vibration on the side surface of the head 72 of the rotary disk 70. This makes it possible to stably obtain extremely high rotational accuracy.

第１４図はこの発明の応用例であるが、スラス
ト軸受すき間３４から環状凸部１８を通つて流出
する潤滑剤の循環通路がなく、またラジアル外面
４４に動圧発生用のみぞがない。なお図示の実施
例の他の個所は第３図の実施例とほぼ同様に構成
されている。 FIG. 14 shows an application example of the present invention, but there is no circulation path for lubricant flowing out from the thrust bearing gap 34 through the annular convex portion 18, and there is no groove in the radial outer surface 44 for generating dynamic pressure. The other parts of the illustrated embodiment are constructed almost the same as the embodiment shown in FIG.

従つて潤滑剤として空気を使用すると、軸体４
０の回転時にスラスト軸受すき間３４から環状凸
部１８を通つて流出する潤滑剤がラジアル内面１
４とラジアル外面４４との間のすき間から外部に
排出される。 Therefore, if air is used as a lubricant, the shaft 4
The lubricant flowing out from the thrust bearing gap 34 through the annular convex portion 18 during the rotation of 0 is the radial inner surface 1.
4 and the radial outer surface 44.

以上、説明したところから明らかなように、こ
の発明は、スラスト軸受部材のスラスト受面とス
ラスト受部材に設けたスラスト端面との少なくと
も一方に形成された動圧発生用のみぞの流出端側
に環状凸部を突設して、該環状凸部を介してスラ
スト軸受部材とスラスト受部材とを接触させ、軸
体の回転時においてスラスト軸受すき間に流入し
た潤滑剤の圧力を環状凸部により上昇させて軸体
を軸方向に変位させ、環状凸部を通つて流出した
潤滑剤を循環通路を経て還流させる構成としてい
る。したがつて、この発明によれば、スラスト軸
受すき間の潤滑剤の圧力が、スラスト受部材とス
ラスト軸受部材との間のすき間によつて調整され
るから一定であり、軸体の軸方向変位が安定し、
一定のスラスト負荷能力が得られる。 As is clear from the above description, the present invention provides a groove for generating dynamic pressure formed on at least one of the thrust receiving surface of the thrust bearing member and the thrust end surface provided on the thrust receiving member. An annular projection is provided to bring the thrust bearing member into contact with the thrust receiving member through the annular projection, and the pressure of the lubricant flowing into the thrust bearing gap when the shaft rotates is increased by the annular projection. The lubricant flowing out through the annular convex portion is circulated through the circulation passage by displacing the shaft body in the axial direction. Therefore, according to the present invention, the pressure of the lubricant in the thrust bearing gap is constant because it is adjusted by the gap between the thrust bearing member and the thrust bearing member, and the axial displacement of the shaft body is stable,
A constant thrust load capacity is obtained.

また、この発明によれば、軸体が回転して軸方
向に変位した時点から潤滑剤の還流が始まり、潤
滑剤の圧力が調整されるので軸体の軸方向変位を
小さくすることができ、さらに、周囲温度により
潤滑剤の粘度が変化した場合でも、軸体の軸方向
変位が変動することはない。また、スラスト負荷
能力が高いとともに、潤滑剤の漏出もない。 Further, according to the present invention, the reflux of the lubricant starts from the moment the shaft body rotates and is displaced in the axial direction, and the pressure of the lubricant is adjusted, so that the axial displacement of the shaft body can be reduced. Furthermore, even if the viscosity of the lubricant changes due to ambient temperature, the axial displacement of the shaft body will not change. In addition, the thrust load capacity is high and there is no leakage of lubricant.

また、この発明によれば、軸体の停止時には、
スラスト受部材とスラスト軸受部材とが環状凸部
を介して接触し、接触面積が小さいから起動トル
クを小さくすることができる。 Further, according to this invention, when the shaft body is stopped,
The thrust receiving member and the thrust bearing member are in contact with each other via the annular convex portion, and since the contact area is small, the starting torque can be reduced.

さらに、スラスト軸受部材の動圧発生用のみぞ
と環状凸部とは、プレスまたはモールデイングに
より一体成形することができるから、簡易な工程
で安価な生産が可能となる。 Furthermore, since the groove for generating dynamic pressure and the annular convex portion of the thrust bearing member can be integrally formed by pressing or molding, it is possible to produce the thrust bearing member at a low cost with a simple process.

【図面の簡単な説明】[Brief explanation of drawings]

第１図および第２図は、それぞれ従来の動圧形
スラスト軸受を示し、第１図ａおよび第２図ａは
その断面図、第１図ｂおよび第２図ｂはスラスト
受面の平面図、第３図はこの発明の第１実施例を
示し、同図ａはその断面図、同図ｂはスラスト受
面の平面図、第４図はこの発明の第１実施例の変
形例を示し、同図ａはその断面図、同図ｂはスラ
スト受面の平面図、第５図はこの発明の第２実施
例を示す断面図、第６図はこの発明の第２実施例
の変形例を示す断面図、第７図はこの発明の第３
実施例を示す断面図、第８図はこの発明の第３実
施例の変形例を示す断面図、第９図はこの発明の
第１使用例を示す断面図、第１０図ａは第９図の
要部拡大断面図、第１０図ｂはその平面図、第１
１図および第１２図はそれぞれこの発明の第１使
用例の第１変形例および第２変形例を示し、第１
１図ａおよび第１２図ａはその断面図、第１１図
ｂおよび第１２図ｂはその平面図、第１３図はこ
の発明の第２使用例を示す断面図、第１４図はこ
の発明の応用例を示す断面図である。 図中、１０はハウジング、１４はラジアル内
面、１５はスラスト軸受部材、１６はスラスト受
面、１８は環状凸部、２０は動圧発生用のみぞ、
２１は連通溝、２２は流通溝、２３は循環孔、３
０はスラスト受部材、３２はスラスト端面、３４
はスラスト軸受すき間、３５は循環孔、３６は連
通孔、４０は軸体、４４はラジアル外面、４８は
スラスト軸受部材と軸体との間のすき間である。 Figures 1 and 2 respectively show conventional dynamic pressure type thrust bearings, Figures 1a and 2a are cross-sectional views thereof, and Figures 1b and 2b are plan views of the thrust bearing surface. , FIG. 3 shows a first embodiment of the present invention, FIG. 3A shows a cross-sectional view thereof, FIG. , Figure a is a cross-sectional view thereof, Figure b is a plan view of the thrust receiving surface, Figure 5 is a cross-sectional view showing the second embodiment of the present invention, and Figure 6 is a modification of the second embodiment of the present invention. FIG. 7 is a sectional view showing the third embodiment of the present invention.
8 is a sectional view showing a modification of the third embodiment of the invention, FIG. 9 is a sectional view showing the first usage example of the invention, and FIG. 10a is FIG. Figure 10b is an enlarged sectional view of the main part of
1 and 12 respectively show a first modification and a second modification of the first usage example of the present invention.
1a and 12a are sectional views thereof, FIGS. 11b and 12b are plan views thereof, FIG. 13 is a sectional view showing a second usage example of the present invention, and FIG. 14 is a sectional view of the present invention. It is a sectional view showing an example of application. In the figure, 10 is a housing, 14 is a radial inner surface, 15 is a thrust bearing member, 16 is a thrust bearing surface, 18 is an annular convex portion, 20 is a groove for generating dynamic pressure,
21 is a communication groove, 22 is a circulation groove, 23 is a circulation hole, 3
0 is a thrust receiving member, 32 is a thrust end face, 34
35 is a thrust bearing gap, 35 is a circulation hole, 36 is a communication hole, 40 is a shaft body, 44 is a radial outer surface, and 48 is a gap between the thrust bearing member and the shaft body.

Claims (1)

【特許請求の範囲】 １ スラスト軸受部材を有するハウジングの内周
にスラスト受部材を有する軸体を配設し、スラス
ト軸受部材に設けたスラスト受面とスラスト受部
材に設けたスラスト端面とが対向し、スラスト受
面とスラスト端面との少なくとも一方に動圧発生
用のみぞを設けた動圧形スラスト軸受において、
前記スラスト受面とスラスト端面との少なくとも
一方には動圧発生用のみぞの流出端側に沿つて環
状凸部が同心状に突設され、軸体の停止時に前記
環状凸部を介してスラスト軸受部材とスラスト受
部材とを接触させ、軸体の回転時にスラスト軸受
すき間から環状凸部を通つて流出する潤滑剤をス
ラスト軸受すき間に還流させる循環通路を設けた
ことを特徴とする動圧形スラスト軸受。 ２ スラスト受面にスパイラル状のみぞを形成
し、スラスト受面の内周縁に環状凸部を設け、ス
ラスト軸受部材と軸体との間のすき間と、スラス
ト軸受部材の底面の半径方向に設けた連通溝およ
び外周面の軸方向に設けた流通溝とにより潤滑剤
の循環通路が形成されている特許請求の範囲第１
項記載の動圧形スラスト軸受。 ３ スラスト受面にヘリングボーン状のみぞを形
成し、該みぞの頂部に２条の環状凸部を隣接して
設け、スラスト軸受部材と軸体との間のすき間
と、環状凸部相互間の凹部に軸方向に設けた循環
孔と、スラスト軸受部材の底面の半径方向に設け
た連通溝および外周面の軸方向に設けた流通溝と
により潤滑剤の循環通路が形成されている特許請
求の範囲第１項記載の動圧形スラスト軸受。 ４ スラスト受面にスパイラル状のみぞを形成
し、スラスト受面の内周縁に環状凸部を設け、ス
ラスト受部材の軸との接合部の軸方向に設けた循
環孔と、スラスト受部材の反スラスト端面および
外周面とハウジングとの間のすき間とにより潤滑
剤の循環通路が形成されている特許請求の範囲第
１項記載の動圧形スラスト軸受。 ５ スラスト受面にスパイラル状のみぞを形成
し、スラスト受面の内周縁に環状凸部を設け、ス
ラスト受部材の軸との接合部の軸方向に設けた循
環孔と、該循環孔とスラスト受部材の外周面との
間に設けた連通孔とにより潤滑剤の循環通路が形
成されている特許請求の範囲第１項記載の動圧形
スラスト軸受。 ６ 軸体のラジアル外面側部がハウジングを貫通
し、ハウジングのラジアル内面と軸体のラジアル
外面との少なくとも一方に、スラスト軸受部材側
に頂部が偏位した非対称のヘリングボーン状のみ
ぞが形成されている特許請求の範囲第１項ないし
第５項の何れかに記載の動圧形スラスト軸受。[Claims] 1. A shaft body having a thrust bearing member is disposed on the inner periphery of a housing having a thrust bearing member, and a thrust bearing surface provided on the thrust bearing member and a thrust end face provided on the thrust bearing member are opposed to each other. However, in a dynamic pressure type thrust bearing in which a groove for generating dynamic pressure is provided on at least one of the thrust receiving surface and the thrust end surface,
At least one of the thrust receiving surface and the thrust end face has an annular protrusion protruding concentrically along the outflow end side of the groove for generating dynamic pressure, and when the shaft body is stopped, the thrust is generated through the annular protrusion. A dynamic pressure type characterized in that a bearing member and a thrust bearing member are brought into contact with each other, and a circulation passage is provided in which the lubricant that flows out from the thrust bearing gap through the annular convex portion when the shaft body rotates is returned to the thrust bearing gap. Thrust bearing. 2 A spiral groove is formed on the thrust bearing surface, an annular convex portion is provided on the inner peripheral edge of the thrust bearing surface, and an annular convex portion is provided in the gap between the thrust bearing member and the shaft body and in the radial direction of the bottom surface of the thrust bearing member. Claim 1, wherein a lubricant circulation passage is formed by the communication groove and the circulation groove provided in the axial direction on the outer peripheral surface.
Dynamic pressure type thrust bearing as described in . 3 A herringbone-shaped groove is formed on the thrust bearing surface, and two annular protrusions are provided adjacent to each other at the top of the groove to reduce the gap between the thrust bearing member and the shaft body and between the annular protrusions. A lubricant circulation passage is formed by a circulation hole provided in the axial direction in the recess, a communication groove provided in the radial direction on the bottom surface of the thrust bearing member, and a circulation groove provided in the axial direction on the outer peripheral surface. A hydrodynamic thrust bearing as described in Range 1. 4 A spiral groove is formed on the thrust receiving surface, an annular convex portion is provided on the inner peripheral edge of the thrust receiving surface, and a circulation hole is provided in the axial direction of the joint with the shaft of the thrust receiving member, and 2. The dynamic pressure type thrust bearing according to claim 1, wherein a lubricant circulation passage is formed by a gap between the thrust end face, the outer peripheral surface, and the housing. 5 A spiral groove is formed on the thrust receiving surface, an annular convex portion is provided on the inner peripheral edge of the thrust receiving surface, a circulation hole is provided in the axial direction of the joint with the shaft of the thrust receiving member, and the circulation hole and the thrust 2. The dynamic pressure type thrust bearing according to claim 1, wherein a lubricant circulation passage is formed by a communication hole provided between the receiving member and the outer circumferential surface of the receiving member. 6. The radial outer surface side of the shaft body passes through the housing, and an asymmetric herringbone-shaped groove is formed on at least one of the radial inner surface of the housing and the radial outer surface of the shaft body, the top of which is deviated toward the thrust bearing member. A dynamic pressure type thrust bearing according to any one of claims 1 to 5.
JP11958082A 1982-07-09 1982-07-09 Dynamic-pressure thrust bearing Granted JPS5913113A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP11958082A JPS5913113A (en) 1982-07-09 1982-07-09 Dynamic-pressure thrust bearing

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP11958082A JPS5913113A (en) 1982-07-09 1982-07-09 Dynamic-pressure thrust bearing

Publications (2)

Publication Number Publication Date
JPS5913113A JPS5913113A (en) 1984-01-23
JPH0143847B2 true JPH0143847B2 (en) 1989-09-22

Family

ID=14764869

Family Applications (1)

Application Number Title Priority Date Filing Date
JP11958082A Granted JPS5913113A (en) 1982-07-09 1982-07-09 Dynamic-pressure thrust bearing

Country Status (1)

Country Link
JP (1) JPS5913113A (en)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS62194021A (en) * 1986-02-17 1987-08-26 Ebara Res Co Ltd Spiral group bearing
JPH01238712A (en) * 1988-03-16 1989-09-22 Canon Inc Rotation device
JPH085369Y2 (en) * 1988-06-27 1996-02-14 光洋精工株式会社 Thrust hydrodynamic bearing
DE3900729A1 (en) * 1989-01-12 1990-07-19 Philips Patentverwaltung TURNING ANODE TUBE WITH A SLIDING BEARING, ESPECIALLY A SPIRAL GROOVE BEARING
KR100467363B1 (en) * 2001-04-16 2005-01-24 머신나우 주식회사 Sliding Bearing using Leaf Springs
JP4846470B2 (en) * 2005-07-20 2011-12-28 Ｎｔｎ株式会社 DYNAMIC PRESSURE BEARING DEVICE AND MOTOR HAVING THE SAME

Also Published As

Publication number Publication date
JPS5913113A (en) 1984-01-23

Similar Documents

Publication Publication Date Title
US6456458B1 (en) Disk-drive motor rotating on a magnetically counterbalanced single hydrodynamic thrust bearing
US6034454A (en) Motor
US5847479A (en) Self-pressure-balanced hydrodynamic bearing spindle motor
JP3665549B2 (en) Thrust dynamic pressure bearing and spindle motor provided with the same
US5634724A (en) Hydrodynamic bearing for spindle motor having high inertial load
US6854889B2 (en) Hydrodynamic pressure bearing, spindle motor in which it is utilized, and disk-drive device furnished with the spindle motor
US7048444B2 (en) Fluid lubricated bearing device
US7604411B2 (en) Fluid lubricated bearing device
US6793394B2 (en) Hydrodynamic bearing device
US20030002757A1 (en) Dynamic bearing device and motor having the same
US20060120643A1 (en) Fluid lubricated bearing device
US7524113B2 (en) Hydrodynamic bearing device
JP2004270820A (en) Fluid dynamic-pressure bearing, spindle motor and recording disk driver
US7940492B2 (en) Hydrodynamic bearing device, spindle motor, and recording and reproducing apparatus
US7237955B2 (en) Hydrodynamic bearing and disc rotation apparatus using the same
JPH0143847B2 (en)
US7237956B2 (en) Hydrodynamic bearing and disc rotation apparatus using the same
JP2005016556A (en) Conical dynamic pressure bearing device, and recording disk drive device having the same
JP2006112614A (en) Dynamic pressure bearing device
JPH033805B2 (en)
JP3842499B2 (en) Hydrodynamic bearing unit
JP2000352416A (en) Dynamic pressure type bearing unit and its manufacture
KR100517085B1 (en) Fluid dynamic bearing motor
JP3828464B2 (en) Spindle motor and disk drive device having the same
JPH10299763A (en) Spindle motor for dynamic bearing