JPS60143222A - Spindle unit - Google Patents
Spindle unitInfo
- Publication number
- JPS60143222A JPS60143222A JP22198984A JP22198984A JPS60143222A JP S60143222 A JPS60143222 A JP S60143222A JP 22198984 A JP22198984 A JP 22198984A JP 22198984 A JP22198984 A JP 22198984A JP S60143222 A JPS60143222 A JP S60143222A
- Authority
- JP
- Japan
- Prior art keywords
- thrust
- radial
- seal
- groove
- bearing
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
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)
- Chemical & Material Sciences (AREA)
- Oil, Petroleum & Natural Gas (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Sliding-Contact Bearings (AREA)
Abstract
Description
【発明の詳細な説明】
〔産業上の利用分野〕
この発明は事務機、映像機器、音響機器等の各方面に使
用されるスピンドルユニットに関する。DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a spindle unit used in various fields such as office machines, video equipment, and audio equipment.
従来のスピンドルユニットは軸体のラジアル荷重を一対
のラジアルすべり軸受で支え、軸体のスラスト荷重なス
ラストすべり軸受で支え、このスラストすべり軸受の軸
受すきまと一対のラジアルすべり軸受の軸受すきまとに
は同一の潤渭剤がそれぞれ存在していた。In a conventional spindle unit, the radial load of the shaft body is supported by a pair of radial sliding bearings, and the thrust load of the shaft body is supported by a thrust sliding bearing.The bearing clearance of this thrust sliding bearing and the bearing clearance of the pair of radial sliding bearings are The same moisturizing agent was present in each.
従って潤渭剤の粘度が高いときはラジアル負荷容量およ
びスラスト負荷容量はいずれも大きいがラジアルすべり
軸受およびスラストすべり軸受のトルクが高く、また潤
渭剤の粘度が低いときはラジアルすべり軸受およびスラ
ストすべり軸受のトルクは低いがラジアルすべり軸受お
よびスラストすべり軸受の負荷容量がいずれも小さかっ
た。Therefore, when the viscosity of the lubricant is high, the radial load capacity and thrust load capacity are both large, but the torque of the radial sliding bearing and thrust sliding bearing is high, and when the viscosity of the lubricant is low, the radial sliding bearing and thrust sliding bearing are Although the torque of the bearing was low, the load capacity of both the radial sliding bearing and the thrust sliding bearing was small.
この考案は大きなスラスト負荷容量を有すると共に低ト
ルクのスピンドルユニットを提供することを目白りとす
る。The aim of this invention is to provide a spindle unit with large thrust load capacity and low torque.
外筒１１に設けた円筒状孔１２に配設した軸体ｌは筒状
のシール外面８とを有し、前記外筒１１はラジアル外面
２．３と共働するラジアル内面１５．１６と、スラスト
端面６と共働するスラスト底面１８と、シール外面８と
共働するシール内面２２とを有し、前記スラスト端面６
とスラスト底面１８との少なくとも一力に動圧発生用の
みぞ７を設け、前記シール外面８とシール内面２２との
少なくとも一″５にシール作用を行なうみぞ９を設け、
前記スラスト端面６とスラスト底面１８との間のスラス
ト軸受すぎまβに潤渭剤が存在するスピンドルユニット
である。The shaft l disposed in a cylindrical hole 12 in the outer cylinder 11 has a cylindrical sealing outer surface 8, said outer cylinder 11 having a radial inner surface 15.16 cooperating with the radial outer surface 2.3; a thrust bottom surface 18 cooperating with the thrust end surface 6; and a seal inner surface 22 cooperating with the seal outer surface 8;
A groove 7 for generating dynamic pressure is provided in at least one part of the thrust bottom surface 18, and a groove 9 for performing a sealing action is provided in at least 1"5 of the outer seal surface 8 and the inner seal surface 22,
This is a spindle unit in which a lubricant exists in the thrust bearing groove β between the thrust end face 6 and the thrust bottom face 18.
軸体ｌが外筒ｌＩＫ対して回転するスピンドルユニット
の作動時にスラスト軸受すきま乙の周囲の潤渭剤は動圧
発生用のみぞ７のボンピング作用によってスラスト軸受
すきま乙に流入し、スラスト軸受部１７は大きなスラス
ト負荷容量を有する。また、シール外面８とシール内囲
器との間のシールすきま１９内の流体はシール作用を行
うみぞ９のボンピング作用によってスラスト軸受すきま
乙の力へ流出するのでスラスト軸受すきまｎ内の潤渭剤
。さらに、互に共働するラジアル外面２．３とラジアル
内面】５．１６とを備えたラジアル軸受部１３．１４は
ラジアル負荷容量を有する。When the spindle unit in which the shaft l rotates with respect to the outer cylinder lIK is operated, the lubricant around the thrust bearing clearance O flows into the thrust bearing clearance O due to the pumping action of the groove 7 for generating dynamic pressure, and the thrust bearing part 17 has large thrust load capacity. In addition, the fluid in the seal gap 19 between the seal outer surface 8 and the seal inner container flows out into the thrust bearing gap A due to the pumping action of the groove 9 that performs the sealing action, so that the fluid in the thrust bearing gap N is absorbed. . Furthermore, the radial bearing part 13.14 with its cooperating radial outer surface 2.3 and radial inner surface 5.16 has a radial load capacity.
。第１図において、垂直に配設された軸体ｌの外筒面に
は円筒状のラジアル外面２．３が軸方向に距離を隔てて
二ケ所に設けられ、これらのラジアル外面２．３にはへ
リングボーン状の動圧発生用みぞ４．５がそれぞれ設け
られている。前記ｆｉｌ１体ｌの一力の端面には平面状
のスラスト端面６が設けられ、このスラスト端面−６に
は第２図に示すようにスパイラル状の動圧発生用のみぞ
７が設けられている。前記軸体ＩＫはスラス） ＺＭ面
側のラジアル外面３とスラスト端面６との間の部分に円
筒状のシール外面８が設けられ、このシール外面８状孔
１２に配設され、この外筒１１はラジアル荷重支持部材
Ｉｌｌと、ラジアル荷重支持部材Ｉｌｌ Ｋ固定した底
板２１１と、０リング３１１を介してラジアル荷重支持
部材ｉｌｌ Ｋ嵌合していると共に底板２１１上に配設
されたスラスト荷重支持部材４１１とから構成されてい
る。前記外筒１１にはラジアル外面２．３と共働してラ
ジアル軸受部】３．１４を構成する円筒状のラジアル内
面】５．１６が用１方向に距離を隔てて二ケ所に設けら
れ、また外筒１１にはスラスト端面６と共働してクラス
軸受軸受部１７を構成する平面状のスラスト底面１８と
、シール外面８と共働してシール部２Ｉを構成する円筒
状のシール内面２２とが設けられている。そして、スラ
スト端面６とスラスト底面１８との間のスラスト軸受す
きま２３に濶ｆ’ｆｌ剤が存在している。. In FIG. 1, cylindrical radial outer surfaces 2.3 are provided at two locations spaced apart from each other in the axial direction on the outer cylindrical surface of the vertically disposed shaft l. Each of the grooves 4.5 is provided with a herringbone-shaped groove 4.5 for generating dynamic pressure. A flat thrust end face 6 is provided on the single force end face of the fil 1 body, and this thrust end face 6 is provided with a spiral groove 7 for generating dynamic pressure as shown in FIG. . A cylindrical seal outer surface 8 is provided in a portion between the radial outer surface 3 and the thrust end surface 6 on the ZM surface side. The radial load support member Ill, the bottom plate 211 fixed to the radial load support member Ill K, and the thrust load support member disposed on the bottom plate 211 are fitted to the radial load support member IllK via an O-ring 311. 411. The outer cylinder 11 is provided with two cylindrical radial inner surfaces 5.16 spaced apart in one direction, which cooperate with the radial outer surface 2.3 to form a radial bearing portion 3.14. Further, the outer cylinder 11 has a planar thrust bottom surface 18 which cooperates with the thrust end surface 6 to constitute the class bearing bearing part 17, and a cylindrical seal inner surface 22 which cooperates with the seal outer surface 8 to constitute the seal part 2I. and is provided. The f'fl agent exists in the thrust bearing clearance 23 between the thrust end surface 6 and the thrust bottom surface 18.
以上のような構成で軸体ｌが外筒１１に対して回転する
と、スラスト軸受すきま乙の周囲の潤渭剤は動圧発生用
のみぞ７のボンピング作用によってスラスト刺１受すき
ま２３に流入し、スラスト軸受部１７は大きなスラスト
負荷容量を有する。また、シし、スラスト軸受すきまｎ
内の潤渭剤はラジアル外面２．３とラジアル内面１５．
１６との間のラジアル軸受すきま２７、あの力への流出
を抑制されている。さらに、開口Ｉ１１のラジアル軸受
すきま２７０両側の気体は開口側の動圧発生用みぞ４の
ボンピング作用によって開口側のラジアル軸受すきまＩ
に流入すると共に反開口側のラジアル軸受すき、まかの
両側の気体は反開口側の動圧発生用みぞ５のボンピング
作用によって反開口側のラジアル軸受すきまあに流入し
、一対のラジアルｌ１４−ｂ受部】３．１４はラジアル
負債容量を有すると共に低トルクでｋ）る第３図および
第４図はこの発明の他の実施例であるが、スラスト底面
■８の半径方向の中央部に球出を埋めこんでいるので平
面状のクラス１１’面１８また、一対のラジアル軸受す
きま２７．２８にはスラスト軸受すきま乙に存在する潤
渭剤より粘度の低い潤肩剤がそれぞれ存在している。こ
のようにすると、ラジアル軸受部】３．１４はラジアル
負荷容量を有すると共に低トルクであり、またス２ス）
ｌＱＩ＋受部１７は大きなスラスト負荷容量を有する
。さらにシール作用を行うみぞ９はシールすきま１９内
の流体をスラスト軸受すきまおの方へ流出する作用を行
うスパイラル状のみぞ１０９と、シールすきま１９内の
流体をラジアル軸受すきま２７、公のカへ流出する作用
を行うスパイラル状のみぞ２０９．とかう構成されてい
る。このようにすると、ラジアル軸受すきま２７．２８
に存在するｆＡ渭剤とスラスト軸受すきま２３に存在す
る潤渭剤とは混合しないので、ラジアル＋１１１受部１
３，１４０ラジアル負荷容量とトルなお図示の実施例で
はラジアル外面２．３に動圧発生用みぞ４．５を設けた
が、互に共働してラジアル軸受部１３．１４を構成する
ラジアル外面２．３とラジアル内面１５．１６との少な
くとも一力に動圧発生用みぞ４．５を設けても良い。When the shaft 1 rotates with respect to the outer cylinder 11 with the above configuration, the lubricant around the thrust bearing clearance 2 flows into the thrust bearing 1 clearance 23 by the pumping action of the groove 7 for generating dynamic pressure. , the thrust bearing portion 17 has a large thrust load capacity. Also, the thrust bearing clearance n
The moisturizer inside is on the radial outer surface 2.3 and the radial inner surface 15.
16 and the radial bearing clearance 27, the outflow of that force is suppressed. Furthermore, the gas on both sides of the radial bearing clearance 270 of the opening I11 is transferred to the radial bearing clearance I of the opening side by the pumping action of the dynamic pressure generating groove 4 on the opening side.
At the same time, the gas on both sides of the radial bearing on the opposite opening side flows into the radial bearing clearance on the opposite opening side by the pumping action of the dynamic pressure generation groove 5 on the opposite opening side, and the gas flows into the radial bearing clearance on the opposite opening side, and the gas flows into the radial bearing clearance on the opposite opening side. [B receiving part] 3.14 has a radial debt capacity and has a low torque k). Figs. 3 and 4 show other embodiments of the present invention. Since the ball protrusion is buried, the class 11' surface 18 is flat, and a lubricant with a lower viscosity than the lubricant present in the thrust bearing gap 27 and 28 is present in the pair of radial bearing gaps, respectively. There is. In this way, the radial bearing part]3.14 has a radial load capacity and low torque, and the radial bearing part]3.
The lQI+ receiving section 17 has a large thrust load capacity. Furthermore, the groove 9 that performs the sealing action has a spiral groove 109 that acts to cause the fluid in the seal clearance 19 to flow out toward the thrust bearing clearance, and the fluid in the seal clearance 19 to the radial bearing clearance 27 and the public force. Spiral groove 209, which acts as a drain. It is structured like this. In this way, the radial bearing clearance is 27.28
The fA lubricant present in the thrust bearing gap 23 does not mix with the lubricant present in the thrust bearing clearance 23.
3,140 radial load capacity and torque In the illustrated embodiment, the groove 4.5 for generating dynamic pressure is provided on the radial outer surface 2.3, but the radial outer surface which cooperates with each other to constitute the radial bearing portion 13.14. 2.3 and the radial inner surface 15.16 may be provided with a groove 4.5 for generating dynamic pressure.
また、一対のラジアル軸受部１３ミ１４をいずれもすべ
り接触のすべり軸受としても良く、また一対のラジアル
軸受部】３．１４のうちの一つな動圧形の流体軸受とし
て他の一つをすべり接触のすべり軸受としても良い。Furthermore, both of the pair of radial bearings 13 and 14 may be sliding contact sliding bearings, or one of the pair of radial bearings [3.14] may be a hydrodynamic bearing of the hydrodynamic type, and the other one may be used as a hydrodynamic bearing. It may also be used as a sliding bearing with sliding contact.
さらに、スラスト端面６とスラスト底面１８との少なく
とも一力に動圧発生用のみぞ７を設けても良い。Furthermore, a groove 7 for generating dynamic pressure may be provided in at least one of the thrust end face 6 and the thrust bottom face 18.
また、シール外面８とシール内面２２との少なくとも一
力にシーＡ・作用を行うみぞ９を設けても良い。Further, a groove 9 may be provided that acts on at least one force between the seal outer surface 8 and the seal inner surface 22.
この−発明のスピンドルユニットによると、＄１休１は
平面状のスラスト端面６を有し、外ｆｍｌｌはスラスト
軸受６と共働するスラスト底面１８を有し、なスラスト
負荷容量を有する。また、軸体口言円筒状のシール外面
８を有し、外筒１１はシール外面８と共働するシール内
面２２を有し、前記シール外面８とシール内面器との少
なくとも一力にシール作用を行５みぞ９を設けたので、
スラスト軸受すきま２３に存在する潤渭剤がラジアル軸
受すきま２７、脂へ流出しない。さらに、シール外面８
とシー層内面ｎとは軸体ｌが外筒１１に対して回転する
スピンドルユニットの作動７中に非接触なので低トルク
である。また、軸体ｌは円筒状のラジアル外面２．３を
有し、外筒１１はラジアル外面２．５と共働するラジア
ル内面１５．１６を有するので、ラジアル軸受すきま２
７．２８には潤渭剤が存在しないよう匠することができ
ると共にスラスト軸受すきまるに存在する潤渭剤より粘
度の低い潤渭剤が存在すスピンドルユニットにすること
ができる。さらに、ラジアル軸受すきま２’７，２８に
はスラスト軸受すきま２］Ｃ存在する潤渭剤と異なる潤
ｒ肖剤が存在しても、シール作用を行なうみぞ９によっ
てラジアル軸受すきま２７、かｆＣ存在する潤渭剤とス
ジストｉ１ｔ＋受１きま７３に存在する潤ｍ剤との混合
を防止でき、ラジアル軸受部１３．１４の負荷容量とト
ルクの変動、スラスト軸受部１７の負荷容量とトルクの
変動、および軸体１の外筒１１に対する変位量の変動は
いずれも少なくできるという効果を有する。According to the spindle unit of this invention, the spindle unit 1 has a planar thrust end face 6, the outer frame has a thrust bottom face 18 cooperating with the thrust bearing 6, and has a thrust load capacity. Further, the shaft body has a cylindrical seal outer surface 8, and the outer cylinder 11 has a seal inner surface 22 that cooperates with the seal outer surface 8, and a sealing effect is exerted on at least one force between the seal outer surface 8 and the seal inner surface. Since we have set row 5 groove 9,
The lubricant present in the thrust bearing clearance 23 does not flow out into the radial bearing clearance 27 and into the grease. Furthermore, the seal outer surface 8
and the inner surface of the sea layer n are not in contact with each other during operation 7 of the spindle unit in which the shaft l rotates with respect to the outer cylinder 11, so the torque is low. Moreover, since the shaft body l has a cylindrical radial outer surface 2.3 and the outer cylinder 11 has a radial inner surface 15.16 that cooperates with the radial outer surface 2.5, the radial bearing clearance 2
7.28 can be designed so that no lubricant is present, and the spindle unit can be designed to have a lubricant with a lower viscosity than the lubricant present in the thrust bearing clearance. Furthermore, even if a lubricant different from the lubricant present in the thrust bearing clearance 2]C is present in the radial bearing clearances 2'7 and 28, the radial bearing clearance 27 and fC exists due to the groove 9 that performs the sealing action. It is possible to prevent the mixing of the lubricant existing in the sujist i1t + bearing 1 gap 73 with the lubricant present in the sujist i1t + bearing 1 gap 73, and to prevent fluctuations in the load capacity and torque of the radial bearing portions 13 and 14, and fluctuations in the load capacity and torque of the thrust bearing portion 17. This has the effect that fluctuations in the amount of displacement of the shaft body 1 with respect to the outer cylinder 11 can both be reduced.
第１図はこの発明の一実施例を示すスピンドルユニット
の断面図、第２図は第１図に示す軸体の下面図、第３図
はこの発明の他の実輸例を示すスピンドルユニットの断
面図、第４図は第３１ｇ１Ｋ示す軸体の下面図である。
図中、■は軸体、２．３けラジアル外面、６けスラスト
端面、７は動圧発生用のみぞ、８けシール外面、９はシ
ール作用を行うみぞ、１１け外筒、１２は円部状孔、１
５．１６はラジアル内面、】８けスラスト底面、２２は
シール内面、乙はスラス） １ｆｌ−＋受すきまである
。
特許出願人 日本精工株式会社FIG. 1 is a sectional view of a spindle unit showing one embodiment of the present invention, FIG. 2 is a bottom view of the shaft shown in FIG. The sectional view, FIG. 4, is a bottom view of the shaft body shown in No. 31g1K. In the figure, ■ is the shaft body, 2.3 radial outer surface, 6 thrust end face, 7 groove for dynamic pressure generation, 8 seal outer surface, 9 groove for sealing, 11 outer cylinder, 12 circular part hole, 1
5.16 is the radial inner surface, ]8 is the bottom of the thrust, 22 is the seal inner surface, O is the thrust) 1fl-+ receiving clearance. Patent applicant: NSK Ltd.
Claims (6)
は外用面に設けた円筒状のラジアル外面２．３と、軸端
に設けた平面状のスラスト端面６と、ラジアル外面２．
３とスラスト端面６との間に設けた円筒状のシール外面
８とを有し、前記外ｍ １１はラジアル外面２．３と共
働するラジアル内面１５．１６と、スラスト端面６と共
働するスラスト底面１８と、シール外面８と共働するシ
ール内面ｎとを有し、前記スラスト端面６とスラスト底
面１８との少なくとも一力に動圧発生用のみぞ７を設け
、前記シール外面８とシール内面ｎとの少なくとも一力
にシール作用を行なうみぞ９を設け、前記スラスト端面
６とスラスト底面１８との間のスラスト軸受すきま２３
に潤渭剤が存在するスピンドルユニット。(1) Shaft l disposed in cylindrical hole 12 provided in outer cylinder 11
A cylindrical radial outer surface 2.3 provided on the external surface, a planar thrust end surface 6 provided on the shaft end, and a radial outer surface 2.3.
3 and a cylindrical sealing outer surface 8 provided between the thrust end surface 6, said outer surface m11 having a radial inner surface 15.16 cooperating with the radial outer surface 2.3 and a thrust end surface 6. It has a thrust bottom surface 18 and a seal inner surface n that cooperates with the seal outer surface 8, and a groove 7 for generating dynamic pressure is provided in at least one of the thrust end surfaces 6 and the thrust bottom surface 18, and the seal outer surface 8 and the seal inner surface n cooperate with each other. A groove 9 is provided for sealing at least one side with the inner surface n, and a thrust bearing clearance 23 between the thrust end surface 6 and the thrust bottom surface 18 is provided.
The spindle unit has a moisturizing agent.
１５．１６との少なくとも一力に動圧発生用みぞ４．５
を設けた特許請求の範囲第【項記載のスピンドルユニッ
ト。(2) A groove 4.5 for generating dynamic pressure in at least one of the radial outer surface 2.3 and the radial inner surface 15.16 that cooperate with each other.
A spindle unit according to claim 1, which provides:
１５．１６がすべり接触のすべり軸受を構成する特許請
求の範囲第１項記載のスピンドルユニット。(3) A spindle unit according to claim 1, wherein the radial outer surface 2.3 and the radial inner surface 15.16, which cooperate with each other, form a sliding bearing in sliding contact.
スラスト底面１８とが点接触する特許請求の範囲第１項
記載のスピンドルユニット。(4) The spindle unit according to claim 1, wherein the thrust end face 6 and the thrust bottom face 18 make point contact when the spindle unit is at rest.
内面ｎとの間のシールすきま１９内の流体をスラスト軸
受すきま乙の方へ流出する作用を行う特許請求の範囲第
１項記載のスピンドルユニット。(5) The spindle according to claim 1, in which the groove 9 that performs the sealing function functions to cause the fluid in the seal gap 19 between the seal outer surface 8 and the seal inner surface n to flow out toward the thrust bearing gap B. unit.
１５．１６との間のラジアル軸受すきま２７．２８には
スラスト軸受すきま乙に存在する潤渭剤より粘度の低い
潤渭剤が存在し、シール作用を行うみぞ９がシールすき
ま１９内の流体をスラスト軸受すきま乙の力へ流出する
作用を行うみぞ１０９と、シールすきま１９内の流体を
ラジアル軸受すきま２７．２８０力へ流出する作用を行
うみぞ２０９とから構成される特許請求の範囲第１項記
載のスピンドルユニット。(6) In the radial bearing gap 27.28 between the radial outer surface 2.3 and the radial inner surface 15.16, which cooperate with each other, there is a lubricant with a lower viscosity than the lubricant present in the thrust bearing gap B. Groove 9, which performs a sealing action, has a groove 109, which performs the action of causing the fluid in the seal clearance 19 to flow out to the thrust bearing clearance A, and a groove 109, which performs the action of flowing the fluid in the seal clearance 19 to the radial bearing clearance 27.280. 2. The spindle unit according to claim 1, comprising a groove 209 for performing the following steps.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP22198984A JPS60143222A (en) | 1984-10-24 | 1984-10-24 | Spindle unit |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP22198984A JPS60143222A (en) | 1984-10-24 | 1984-10-24 | Spindle unit |
Related Child Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP59263055A Division JPS60143223A (en) | 1984-12-14 | 1984-12-14 | Spindle unit |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS60143222A true JPS60143222A (en) | 1985-07-29 |
| JPS6229647B2 JPS6229647B2 (en) | 1987-06-27 |
Family
ID=16775332
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP22198984A Granted JPS60143222A (en) | 1984-10-24 | 1984-10-24 | Spindle unit |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS60143222A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6071014A (en) * | 1998-12-30 | 2000-06-06 | International Business Machines Corporation | Spindle motor with hybrid air/oil hydrodynamic bearing |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS63173729U (en) * | 1987-06-09 | 1988-11-11 |
-
1984
- 1984-10-24 JP JP22198984A patent/JPS60143222A/en active Granted
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6071014A (en) * | 1998-12-30 | 2000-06-06 | International Business Machines Corporation | Spindle motor with hybrid air/oil hydrodynamic bearing |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS6229647B2 (en) | 1987-06-27 |
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