JPS60220218A - Liquid bearing device - Google Patents
Liquid bearing deviceInfo
- Publication number
- JPS60220218A JPS60220218A JP59073310A JP7331084A JPS60220218A JP S60220218 A JPS60220218 A JP S60220218A JP 59073310 A JP59073310 A JP 59073310A JP 7331084 A JP7331084 A JP 7331084A JP S60220218 A JPS60220218 A JP S60220218A
- Authority
- JP
- Japan
- Prior art keywords
- shaft
- lubricant
- ring
- fixed
- sleeve
- 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
- F16C17/02—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
- F16C2370/00—Apparatus relating to physics, e.g. instruments
- F16C2370/12—Hard disk drives or the like
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 2 ・ 7 本発明は潤滑剤を用いた流体軸受装置に関する。[Detailed description of the invention] Industrial applications 2・7 The present invention relates to a hydrodynamic bearing device using a lubricant.
従来例の構成とその問題点
従来の流体軸受装置をビデオテープレコーダーの回転ヘ
ッド装置(以下VTRシリンダーと略t)に適用した例
について第1〜3図にその構成を示す。図において下部
シリンダー2の中央部には固定軸1が圧入固定され、固
定軸1にはディスク3が回転自在に挿入されディスク3
の上部にはスラスト受け4、上部シリンダー5、磁気へ
ラドeを有する。ディスク3の下部には回転する磁気へ
ラド6を介して磁気テープから取り出した映像信号を固
定側に伝達するだめの回転側ロータリー]・ランス7が
取り付けられ、それに対向して、下部シリンダー2には
その映像信号を受けるための固定側ロータリーi・ラン
ス8が取り付けられ回転側ユニット10を構成している
。1 to 3 show the structure of an example in which a conventional hydrodynamic bearing device is applied to a rotating head device of a video tape recorder (hereinafter referred to as a VTR cylinder). In the figure, a fixed shaft 1 is press-fitted into the center of the lower cylinder 2, and a disk 3 is rotatably inserted into the fixed shaft 1.
The upper part has a thrust receiver 4, an upper cylinder 5, and a magnetic helad e. A rotary lance 7 is attached to the lower part of the disk 3 to transmit the video signal taken out from the magnetic tape to the fixed side via a rotating magnetic head 6. A fixed-side rotary i-lance 8 for receiving the video signal is attached to constitute a rotating-side unit 10.
また、固定軸1の先端部には第3図に示すCリング9が
止められ、回転側ユニット10の抜は防止をしている。Further, a C ring 9 shown in FIG. 3 is fixed to the tip of the fixed shaft 1 to prevent the rotating unit 10 from being pulled out.
またディスク3には、さらにダイレクト駆動型モーター
のアマチャ−マグネット113
が取り付けられ、それに対向して下部シリンダー2には
、固定側コイルユニット12が取付けられ、11.12
でダイレクト駆動型モーター13を構成している。そし
てアマチャ−マグネット11は常に固定側コイルユニッ
ト12を600〜900グラムの力で吸引している。Further, an armature magnet 113 of a direct drive type motor is further attached to the disc 3, and a fixed side coil unit 12 is attached to the lower cylinder 2 opposite to it.
This constitutes a direct drive motor 13. The armature magnet 11 always attracts the stationary coil unit 12 with a force of 600 to 900 grams.
なお、固定軸1の上部と中央部の2ケ所にはエツチング
加工等により、ラジアルグループ14A。Note that radial groups 14A are formed at two locations on the upper and center portions of the fixed shaft 1 by etching or the like.
14Bが加工され、また、固定軸1の先端面1Aは平坦
かつ直角に精度よく加工されており、スラスト受け4に
対向してスラスト受け4の中央下面には第2図に示すよ
うな単列のスパイラルグループ16がエツチング等によ
り加工されている。そして14A、14B、1503ケ
所のそれぞれのグループ部には潤滑剤が注油されている
ため、前記モーター13により前記回転側ユニット10
が回転させられると、前記3ケ所のグループ部のポンピ
ング作用によって圧力が発生し、油膜の剛性が高くなっ
て回転側ユニット10は固定軸1に対して完全に浮上し
て回転するものである。ここでラジアルグループ14A
、 14Bとディスク3から構成される軸受部分をラ
ジアル軸受16、スラスト受け4と先端面1Aから構成
される軸受部分をスラスト軸受17と呼ぶ。14B is machined, and the tip surface 1A of the fixed shaft 1 is precisely machined to be flat and at right angles, and a single row as shown in FIG. The spiral group 16 is processed by etching or the like. Since lubricant is applied to each of the group parts 14A, 14B, and 1503 locations, the motor 13 drives the rotating unit 10.
When the unit 10 is rotated, pressure is generated by the pumping action of the three group parts, and the rigidity of the oil film increases, so that the rotating unit 10 completely floats relative to the fixed shaft 1 and rotates. Here radial group 14A
, 14B and the disk 3 is called a radial bearing 16, and the bearing part made up of the thrust receiver 4 and the tip end surface 1A is called a thrust bearing 17.
しかしながらこの種の流体軸受装置は輸送中の長時間に
わたる振動や使用中に発生する落下衝撃等に耐える必要
があるが、これら強い振動や衝撃がかかった時に回転側
ユニット10が第1図の矢印に示す上下方向に振動し、
このときスラスト軸受17の潤滑剤を周囲に飛散させて
しまい、潤滑剤不足を生じるという欠点があった。However, this type of hydrodynamic bearing device needs to withstand long-term vibrations during transportation and falling shocks that occur during use. It vibrates in the vertical direction shown in
At this time, the lubricant of the thrust bearing 17 is scattered around, resulting in a shortage of lubricant.
発明の目的
本発明は上記従来の欠点を解消するものであり振動や落
下に対して強い、信頼性の高い流体軸受装置を得るもの
である。OBJECTS OF THE INVENTION The present invention solves the above-mentioned conventional drawbacks, and provides a highly reliable hydrodynamic bearing device that is resistant to vibrations and drops.
発明の構成
本発明の流体軸受装置は軸とスリーブと軸端面に当接し
、スリーブに固定されたスラスト受は部材を有し、軸端
面またはスラスト受は部材のいずれか一方にスパイラル
グループを有し、潤滑剤を51・ン
保持し、スリーブの軸端面近傍に空所を設け、この空所
内の軸にC字状リングを固着し、このC字状リングとス
ラスト受は部材の間の空所内に、リングをスリーブに固
定し、スリーブ内周と、軸外周との間に潤滑剤を保持す
るための隙間を設けたもので、振動や落下衝撃に対して
強い流体軸受装置である。Structure of the Invention The hydrodynamic bearing device of the present invention abuts the shaft, the sleeve, and the shaft end surface, the thrust bearing fixed to the sleeve has a member, and the shaft end surface or the thrust bearing has a spiral group on either one of the members. , a lubricant is held at 51 mm, a space is provided near the shaft end face of the sleeve, a C-shaped ring is fixed to the shaft within this space, and this C-shaped ring and the thrust receiver are inserted into the space between the members. In addition, a ring is fixed to a sleeve, and a gap is provided between the inner circumference of the sleeve and the outer circumference of the shaft to hold lubricant, making it a hydrodynamic bearing device that is resistant to vibrations and drop impacts.
実施例の説明
以下に本発明の一実施例を第4〜5図にもとづいて説明
する。図において18は固定軸、18Aは先端面、19
は下部シリンダー、2oはディスク、2OAはスリーブ
部、20Bは空所、21はスラスト受け、22は上部シ
リンダー、23は磁気ヘッド、24は回転側ロータリー
トランス、25は固定側ロータリートランス、26はC
リングであり、29はアマチャ−マグネット、30は固
定側コイルユニット、29.30でダイレクト駆動モー
タ31を構成する。また20,21.22゜23.24
.29で回転側ユニット28を構成する。32A 、3
2Bはラジアルグループ、33はスパイラルグループ、
18Aと21と33でスラスト軸受35を構成し、18
と20と32A・32Bでラジアル軸受34を構成する
。またスラスト軸受36、およびラジアル軸受34には
オイルまたは、グリースの潤滑剤36.37をそれぞれ
独立して注油する。CIJング26により、回転側ユニ
ット28の抜けを防止している。DESCRIPTION OF EMBODIMENTS An embodiment of the present invention will be described below with reference to FIGS. 4 and 5. In the figure, 18 is a fixed shaft, 18A is a tip end surface, and 19
is the lower cylinder, 2o is the disk, 2OA is the sleeve part, 20B is the cavity, 21 is the thrust receiver, 22 is the upper cylinder, 23 is the magnetic head, 24 is the rotary transformer on the rotating side, 25 is the rotary transformer on the fixed side, 26 is C
29 is an armature magnet, 30 is a fixed side coil unit, and 29.30 constitutes a direct drive motor 31. Also 20, 21.22゜23.24
.. 29 constitutes a rotation side unit 28. 32A, 3
2B is a radial group, 33 is a spiral group,
A thrust bearing 35 is composed of 18A, 21 and 33, and 18
, 20, 32A, and 32B constitute a radial bearing 34. Further, the thrust bearing 36 and the radial bearing 34 are each independently filled with lubricants 36 and 37 such as oil or grease. The CIJ ring 26 prevents the rotating unit 28 from coming off.
次に本発明のポインi・であるリング27について述べ
る。本発明においては、ディスク2oと固定軸18の間
にスラスト受け21に接してディスク20と共に回転す
るリング27を設けており本流体軸受装置に振動等が加
わっても潤滑剤36は飛散しに<<、少なくともリング
27と軸18との間の隙間には潤滑剤36は必ず保持さ
れる。また、スパイラルグループ33が潤滑剤を中央に
集める効果を有すると共に固定軸18の上部近傍の外周
またはリング27の内周のいずれかに、らせん溝38を
設けることで飛散した潤滑剤はより確実にスラスト軸受
35に集められる。20cは通気穴であり、気圧が変化
したときに、体積膨張した空気により潤滑剤37が押し
出される事を防止する。Next, the ring 27, which is the main point of the present invention, will be described. In the present invention, a ring 27 that contacts the thrust receiver 21 and rotates together with the disk 20 is provided between the disk 2o and the fixed shaft 18, so that even if vibration or the like is applied to the hydrodynamic bearing device, the lubricant 36 will not be scattered. <The lubricant 36 is always held at least in the gap between the ring 27 and the shaft 18. In addition, the spiral group 33 has the effect of collecting the lubricant in the center, and by providing the spiral groove 38 on either the outer circumference near the upper part of the fixed shaft 18 or the inner circumference of the ring 27, the scattered lubricant can be more reliably removed. It is collected in the thrust bearing 35. Reference numeral 20c is a ventilation hole, which prevents the lubricant 37 from being pushed out by volumetrically expanded air when the atmospheric pressure changes.
尚、リング27は弾性を有する例えばPES (ポリエ
ーテルサルフォン)やPBT (ポリブチレンテレフタ
レート)等の合成樹脂を用いることが、バネ性、耐油性
、耐クリープ性に優れる。The ring 27 is made of elastic synthetic resin such as PES (polyether sulfone) or PBT (polybutylene terephthalate), which has excellent spring properties, oil resistance, and creep resistance.
尚、実施例について軸の先端面IA、18Aが平面型軸
受の場合について述べたが、球面軸受や台形軸受であっ
ても同じことである。Although the embodiment has been described in the case where the shaft tip surfaces IA and 18A are planar bearings, the same applies even if they are spherical bearings or trapezoidal bearings.
発明の効果
以上のように軸と同軸にリングを設け、リング内周と軸
外周との間に隙間を設は潤滑剤を保持することにより振
動や落下衝撃に対しても安心な流体軸受装置が得られ、
その実用的効果は大なるものがある。As described above, by providing a ring coaxially with the shaft and creating a gap between the inner periphery of the ring and the outer periphery of the shaft to retain lubricant, we have created a fluid bearing device that is safe against vibrations and drop impacts. obtained,
Its practical effects are significant.
第1図は従来の流体軸受装置を示す断面図、第2図は従
来例のスパイラルグループの平面図、第3図は同Cリン
グの平面図、第4図は本発明の一実施例を示す断面図、
第6図は同要部拡大図である。
18・・・・・・軸、18A・・川・先端面、20山・
・ディスク、20A・・・・スリーブ、20B・・・・
・空所、21・・・・スラスト受は部材、26・・・・
・C字状リング、27・・・・・リング、33・・・・
・・スパイラルグループ36.37・・・・・潤滑剤。
代理人の氏名 弁理士 中 尾 敏 男 はが1名第1
図
第2図 第3図
形4図
第5図Fig. 1 is a sectional view showing a conventional hydrodynamic bearing device, Fig. 2 is a plan view of a conventional spiral group, Fig. 3 is a plan view of the same C-ring, and Fig. 4 is an embodiment of the present invention. cross section,
FIG. 6 is an enlarged view of the main part. 18...axis, 18A...river/tip surface, 20 peaks/
・Disc, 20A...Sleeve, 20B...
・Vacancy, 21... Thrust receiver is a member, 26...
・C-shaped ring, 27...Ring, 33...
...Spiral group 36.37...Lubricant. Name of agent: Patent attorney Toshio Nakao (1st person)
Figure 2 Figure 3 Figure 4 Figure 5
Claims (2)
の端面に固定されたスラスト受は部材を有し前記軸端面
またはスラスト受は部材の当接面のいずれか一方にスパ
イラルグループを有し、前記スラスト受は部材と前記軸
端面との間に潤滑剤を保持し、前記スリーブの前記軸端
面近傍に空所を設け、前記空所内の前記軸にC字状リン
グを固着し、この空所内の前記C字状リングとスラスト
受は部材の間に、リングをスリーブに固定し、このリン
グ内周と前記軸外周との間に潤滑剤を保持するだめの間
隙を設けた流体軸受装置。(1) A shaft, a sleeve, and a thrust bearing that is in contact with the end face of the shaft and fixed to the end face of the sleeve has a member, and the shaft end face or the thrust bearing has a spiral group on either one of the contact surfaces of the member. The thrust receiver retains a lubricant between the member and the shaft end surface, a space is provided near the shaft end surface of the sleeve, a C-shaped ring is fixed to the shaft within the space, and the C-shaped ring is fixed to the shaft within the space. The C-shaped ring in the cavity and the thrust bearing are fixed to a sleeve, and a gap for retaining lubricant is provided between the inner periphery of the ring and the outer periphery of the shaft. .
成した運搬溝を設けた特許請求の範囲第1項記載の流体
軸受装置。(2) The hydrodynamic bearing device according to claim 1, further comprising a conveying groove configured to collect lubricant scattered in the gap at the center of rotation.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP59073310A JPS60220218A (en) | 1984-04-12 | 1984-04-12 | Liquid bearing device |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP59073310A JPS60220218A (en) | 1984-04-12 | 1984-04-12 | Liquid bearing device |
Publications (2)
Publication Number | Publication Date |
---|---|
JPS60220218A true JPS60220218A (en) | 1985-11-02 |
JPH0520605B2 JPH0520605B2 (en) | 1993-03-22 |
Family
ID=13514463
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP59073310A Granted JPS60220218A (en) | 1984-04-12 | 1984-04-12 | Liquid bearing device |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPS60220218A (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0597479A3 (en) * | 1992-11-12 | 1994-08-24 | Nec Corp | Magnetic disk drive spindle motor. |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5530528A (en) * | 1978-08-22 | 1980-03-04 | Matsushita Electric Ind Co Ltd | Bearing device |
JPS5850318A (en) * | 1981-09-18 | 1983-03-24 | Matsushita Electric Ind Co Ltd | Bearing device |
JPS58134219A (en) * | 1982-02-03 | 1983-08-10 | Matsushita Electric Ind Co Ltd | Fluid bearing device |
JPS58187615A (en) * | 1982-04-28 | 1983-11-01 | Matsushita Electric Ind Co Ltd | Fluid bearing device in direction of thrust |
-
1984
- 1984-04-12 JP JP59073310A patent/JPS60220218A/en active Granted
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5530528A (en) * | 1978-08-22 | 1980-03-04 | Matsushita Electric Ind Co Ltd | Bearing device |
JPS5850318A (en) * | 1981-09-18 | 1983-03-24 | Matsushita Electric Ind Co Ltd | Bearing device |
JPS58134219A (en) * | 1982-02-03 | 1983-08-10 | Matsushita Electric Ind Co Ltd | Fluid bearing device |
JPS58187615A (en) * | 1982-04-28 | 1983-11-01 | Matsushita Electric Ind Co Ltd | Fluid bearing device in direction of thrust |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0597479A3 (en) * | 1992-11-12 | 1994-08-24 | Nec Corp | Magnetic disk drive spindle motor. |
Also Published As
Publication number | Publication date |
---|---|
JPH0520605B2 (en) | 1993-03-22 |
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