JPS5829407B2 - Jikuukeshijisouchi - Google Patents

Jikuukeshijisouchi

Info

Publication number
JPS5829407B2
JPS5829407B2 JP50141324A JP14132475A JPS5829407B2 JP S5829407 B2 JPS5829407 B2 JP S5829407B2 JP 50141324 A JP50141324 A JP 50141324A JP 14132475 A JP14132475 A JP 14132475A JP S5829407 B2 JPS5829407 B2 JP S5829407B2
Authority
JP
Japan
Prior art keywords
thrust
bearing
bearing sleeve
gap
holding hole
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
JP50141324A
Other languages
Japanese (ja)
Other versions
JPS5264550A (en
Inventor
滋 石原
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 JP50141324A priority Critical patent/JPS5829407B2/en
Publication of JPS5264550A publication Critical patent/JPS5264550A/en
Publication of JPS5829407B2 publication Critical patent/JPS5829407B2/en
Expired 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
    • F16C27/00—Elastic or yielding bearings or bearing supports, for exclusively rotary movement
    • F16C27/04—Ball or roller bearings, e.g. with resilient rolling bodies
    • F16C27/045—Ball or roller bearings, e.g. with resilient rolling bodies with a fluid film, e.g. squeeze film damping
    • 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
    • F16C21/00—Combinations of sliding-contact bearings with ball or roller bearings, for exclusively rotary movement
    • 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
    • F16C25/00—Bearings for exclusively rotary movement adjustable for wear or play
    • F16C25/06—Ball or roller bearings
    • F16C25/08—Ball or roller bearings self-adjusting
    • F16C25/086—Ball or roller bearings self-adjusting with magnetic means to preload the bearing
    • 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
    • F16C32/00—Bearings not otherwise provided for
    • F16C32/04—Bearings not otherwise provided for using magnetic or electric supporting means
    • F16C32/0406—Magnetic bearings
    • F16C32/0408—Passive magnetic bearings
    • F16C32/0423—Passive magnetic bearings with permanent magnets on both parts repelling each other
    • F16C32/0427—Passive magnetic bearings with permanent magnets on both parts repelling each other for axial load mainly
    • 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
    • F16C39/00—Relieving load on bearings
    • F16C39/06—Relieving load on bearings using magnetic means
    • F16C39/063—Permanent magnets
    • F16C39/066—Permanent magnets with opposing permanent magnets repelling each other
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/04—Sliding-contact bearings for exclusively rotary movement for axial load only
    • 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
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/54—Systems consisting of a plurality of bearings with rolling friction
    • 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
    • F16C2360/00—Engines or pumps

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Support Of The Bearing (AREA)

Description

【発明の詳細な説明】 この発明は、軸受の支持装置に関し、特に、軸受（こ外
嵌する軸受スリーブを、外部材に、スクイズ膜を介して
保持せしめる如き所謂ダンパ支持される軸受Ｑこ釦いて
、外部材と軸受スリーブの相互に対向するスラスト面に
、同一極性の磁石を設置し、磁力反発によってスラスト
間隙を構成せしめ、軸受（こかかる予圧あるいは回転軸
昏こ作用する内力または外力等（こよるスラスト荷重で
スラスト面が相互に接触して軸受スリーブの半径方向へ
の移動カ該スラスト面の摩擦でロックされ、所謂スクイ
ズ効果が阻害されるのを効果的に防止し、更に好壕し←
は、スプリングのような機械的な弾器を用いることなく
軸受に対して簡単（こ予圧を附与することのできる軸受
支持装置を提供する。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a support device for a bearing, and particularly to a bearing support device for supporting a so-called damper-supported bearing Q-button, in which a bearing sleeve is held on an external member via a squeeze film. Then, magnets of the same polarity are installed on the mutually opposing thrust surfaces of the external member and the bearing sleeve, and a thrust gap is formed by magnetic repulsion. This effectively prevents the thrust surfaces from coming into contact with each other due to this thrust load and locking the movement of the bearing sleeve in the radial direction due to the friction of the thrust surfaces, which inhibits the so-called squeeze effect. ←
provides a bearing support device that can easily apply preload to a bearing without using a mechanical force such as a spring.

一般（こ高速軸受で（こ、回転軸の不つりあいによる振
動を減衰するために、軸受の外輪に軸受スリーブを外嵌
し、この軸受スリーブを、ハウジングあるいは固定用の
ブツシュの如き外部材に、油のような粘性流体（こよっ
て形成されるスクイズ膜を介して取り付ける。Generally speaking, in high-speed bearings, in order to damp vibrations caused by unbalance of the rotating shaft, a bearing sleeve is fitted onto the outer ring of the bearing, and this bearing sleeve is attached to an external member such as a housing or a fixing bushing. Attach via a viscous fluid such as oil (thus forming a squeeze film).

而してこのスクイズ膜は、軸受スリーブと外部材との間
に形成された微少間隙に圧入された粘性流体で形成され
、軸受スリーブの軸回転Ｑこよる振動を吸収する。This squeeze film is formed of a viscous fluid that is press-fitted into a minute gap formed between the bearing sleeve and the external material, and absorbs vibrations caused by the shaft rotation Q of the bearing sleeve.

然し乍ら、軸受誓こは、予圧あるいは回転軸に作用する
内力または外力等りこよるスラスト荷重が負荷される。However, the bearing is subjected to a thrust load such as a preload or an internal or external force acting on the rotating shaft.

このスラスト荷重は、軸受スリーブのスラスト面と外部
材のスラスト面で受けられる。This thrust load is received by the thrust surface of the bearing sleeve and the thrust surface of the external member.

従って、該スラスト面間にお−ける摩擦は、軸受スリー
ブの半径方向への移動をロックしてし１う。Friction between the thrust surfaces thus locks the radial movement of the bearing sleeve.

このような状態では、結局軸受スリーブは、外部材に対
し強固をこ固定されたも同然となり、スクイズ効果は発
揮されない。In such a state, the bearing sleeve ends up being as if it were firmly fixed to the external member, and no squeezing effect is exerted.

このようなスラスト面のロックを防止するために、該ス
ラスト面（負荷面）間に静圧流体軸受を形成させたり、
ボールを挟入設置したりして軸受スリーブが半径方向に
移動するのを自由にする効果を得ている（例えば米国特
許第３８４４６３０号、同第３７８４２６７号）。In order to prevent such locking of the thrust surfaces, a hydrostatic fluid bearing is formed between the thrust surfaces (load surfaces),
The effect of freeing the bearing sleeve to move in the radial direction is obtained by inserting balls (for example, US Pat. No. 3,844,630 and US Pat. No. 3,784,267).

これらの発明は、原理的には然るべき効果を発揮するも
のと考えられるが、例えばボールを用いる例では摩擦力
の減少は十分に得られず、ボールの取付手段やその他加
工技術の点で、微小スラスト間隙１こ用いる場合Ｑこ問
題が残り、また例えば静圧流体軸受の場合は、装置が比
較的大型複雑になリ、更ｔこ高精度を要求されるために
組立が繁雑となったりコストが嵩んだりする欠点がある
。Although these inventions are thought to have the desired effect in principle, for example, in cases where balls are used, the frictional force cannot be sufficiently reduced, and there are problems with the ball attachment means and other processing techniques. If a thrust gap of 1 is used, problems such as Q remain, and in the case of hydrostatic fluid bearings, for example, the device is relatively large and complex, and furthermore, high precision is required, making assembly complicated and costly. It has the disadvantage of being bulky.

この発明は、ダイパ支持軸受のかかる問題を解決するも
のである。This invention solves this problem of the diameter support bearing.

即ちこの発明の目的は、完全なスクイズ効果（ダイパ効
果）が得られる軸受支持装置を提供すること１こあり、
またこの発明の目的は、スラスト間隙の大小にかかわら
ずスクイズ効果が阻害されないだけの必要間隔を適確ｔ
こ設定された軸受支持装置を提供することにあり、更０
ここの発明の目的は、簡単な構造のスラスト面間隙保持
手段を有し安価で効果的な軸受支持装置を提供すること
にあり、また更にこの発明の目的は格別の弾器を用いな
くてもスクイズ効果を保障するスラスト間隙維持手段に
よって軸受に予圧を与え、軸受の高速性能が向上できる
軸受支持装置を提供することにある。That is, an object of the present invention is to provide a bearing support device that can obtain a perfect squeeze effect (diaper effect).
Further, it is an object of the present invention to accurately set the required spacing so that the squeezing effect is not inhibited, regardless of the size of the thrust gap.
The purpose of the present invention is to provide a bearing support device configured as described above, and furthermore,
It is an object of the present invention to provide a bearing support device which is inexpensive and effective and has a thrust face gap retaining means of a simple structure, and it is a further object of the invention to It is an object of the present invention to provide a bearing support device that can improve the high-speed performance of the bearing by applying preload to the bearing using a thrust gap maintaining means that ensures a squeezing effect.

即ちこの出願は、図の如く、外部材１内（こ、スクイズ
膜２を介して軸受スリーブ３を保持し、外部材１と軸受
スリーブ３の各スラスト面４，５に、同一極性の磁石６
，７を対向設置して、スラスト面４，５間に磁力反発に
よるスラスト間隙８を構成した軸受支持装置を特定発明
とし、更Ｑこ支承される軸９の軸方向に固定された軸受
１０に外嵌して一体化せる軸受スリーブ３を、外部材１
内にスクイズ膜２を介して保持し、外部材１と軸受スリ
ーブ３の各スクイズ面４（又は４’）、５と同一極性の
磁石６（又は６’）、７を対向して設置して、スラスト
面４（又は４’）、５間に磁力反発によってもたらされ
るスラスト間隙８を構成し、該スラスト間隙を磁力反発
に抗して縮小した状態Ｇこ設定することにより軸受１０
に磁力反発による予圧を附与した軸受支持装置を併合発
明とする。That is, in this application, as shown in the figure, a bearing sleeve 3 is held within an outer member 1 (through a squeeze film 2), and magnets 6 of the same polarity are attached to each thrust surface 4, 5 of the outer member 1 and the bearing sleeve 3.
, 7 are installed facing each other to form a thrust gap 8 due to magnetic repulsion between the thrust surfaces 4 and 5. The bearing sleeve 3, which can be fitted externally and integrated, is attached to the external material 1.
Magnets 6 (or 6') and 7 having the same polarity as the respective squeeze surfaces 4 (or 4') and 5 of the outer member 1 and the bearing sleeve 3 are placed facing each other. By forming a thrust gap 8 between the thrust surfaces 4 (or 4') and 5 caused by magnetic repulsion, and setting the thrust gap in a reduced state G against the magnetic repulsion, the bearing 10
The combined invention is a bearing support device in which a preload is applied by magnetic repulsion.

この発明の構成上の基本的な特徴は、外部材内（こスク
イズ膜を介し軸受スリーブを保持し外部材と軸受スリー
ブとの相対向するスラスト面に同一極性の磁石を設置し
て夫々のスラスト面を相反発離隔せしめ、スラスト面（
こおける摩擦を避けて該軸受スリーブの半径方向の移動
を円滑【こしてスクイズ効果（ダンパ効果）を十分に発
揮せしめるにある。The basic feature of the structure of this invention is that the bearing sleeve is held in the outer member (through this squeeze film), and magnets of the same polarity are installed on the opposing thrust surfaces of the outer member and the bearing sleeve. The thrust surface (
The purpose is to avoid friction caused by the bearing sleeve and to smoothly move the bearing sleeve in the radial direction, thereby fully exerting the squeeze effect (damper effect).

従って、その実施態様は、該スラスト面の構造において
種々選択できる。Therefore, the embodiment can be selected in various ways in the structure of the thrust surface.

例えば、磁石については、最も典型的な例としては永久
磁石を用いることができるが、場合によっては、電磁石
あるいは電磁石と永久磁石との組み合せも適用が可能で
ある。For example, as for the magnet, a permanent magnet can be used as the most typical example, but depending on the case, an electromagnet or a combination of an electromagnet and a permanent magnet can also be applied.

要する（こ、外部材のスラスト面とこれに対向する軸受
スリーブのスラスト面とが、磁力によって反発し合って
、該スラスト面間に常時相互接触を避ける如くスラスト
間隙が構成されればよい。It is sufficient that the thrust surface of the external member and the thrust surface of the bearing sleeve opposing it repel each other due to magnetic force, and a thrust gap is formed between the thrust surfaces to avoid constant contact with each other.

従って、該対向スラスト面に設置される磁石は、相互に
同極を対向する如く設定されることが重要である。Therefore, it is important that the magnets installed on the facing thrust surfaces are set so that the same poles face each other.

このような基本的な磁石の設定があれば、スラスト面の
構造やその設定位置は限定されない。As long as such basic magnet settings are available, the structure of the thrust surface and its setting position are not limited.

特に磁石が対向設置せるスラスト面で構成される間隙は
、磁石の磁力による反発を生じる点又は該反発を生じる
寸前即ち反発力の臨界点に設定すれば十分であるが、こ
の間隙は、磁力反発（こ抗して小さくするとと【こより
、実質的に軸に対し固定された状態の軸受スリーブを常
時軸方向をこ弾圧し、その弾圧力は、軸受スリーブ内に
保持される軸受１こかけられ所謂予圧を与える為の弾器
を兼ねること（こなる。In particular, it is sufficient to set the gap between the thrust surfaces of the magnets facing each other at the point where the magnetic force of the magnet causes repulsion or just before the repulsion occurs, that is, at the critical point of the repulsive force. (If the bearing sleeve is substantially fixed to the shaft, it will be constantly compressed in the axial direction, and the compressive force will be applied to each bearing held within the bearing sleeve.) It also serves as a ammunition to give so-called preload.

この場合、該スラスト間隙は、軸受スリーブの外周面と
外部材との間に形成されるスクイズ膜用の間隙と適当な
シールリングのような手段で仕切られた完全な空間であ
ってもよく、また前記スクイズ膜用の間隙と伺ら仕切ら
れることなくスクイズ膜を形成する粘性流体（実際（こ
は潤滑油のような流体）が該スラスト間隙に流入し適当
に流出するような構造であっても支障はない。In this case, the thrust gap may be a complete space separated by a squeeze membrane gap formed between the outer circumferential surface of the bearing sleeve and the external material by means such as a suitable sealing ring; Further, the structure is such that the viscous fluid (in fact, fluid such as lubricating oil) forming the squeeze film flows into the thrust gap and flows out appropriately without being partitioned from the gap for the squeeze film. There is no problem.

スラスト間隙にも粘性流体が適用され、スクイズ膜を形
成する該粘性流体が絶えず流動する構成は軸受内の冷却
Ｇこ効果的である。A configuration in which a viscous fluid is also applied to the thrust gap, and the viscous fluid that forms a squeeze film constantly flows, is effective for cooling the inside of the bearing.

而して第１図、第３図、第４図には、この発明の典型的
な実施例を示しである。FIGS. 1, 3, and 4 show typical embodiments of the present invention.

即ち第１図において外部材１は、回転機械のハウジング
であり、保持孔１′を有している。That is, in FIG. 1, the external member 1 is a housing of a rotating machine and has a holding hole 1'.

この保持孔１′内には、その奥部に内周方向（こ延出せ
る段部１１を設け、入口部（こは、ナツト１２を軸方向
に位置調節できるように螺設しである。Inside this holding hole 1', a stepped portion 11 that can extend in the inner circumferential direction is provided at the deep end thereof, and an inlet portion is threaded so that the position of the nut 12 can be adjusted in the axial direction.

保持孔１′内には、その入口部と奥部の内周面に、シー
ルリング１３．１４を適当な間隔を保って滑動嵌挿され
ている。Seal rings 13 and 14 are slidably fitted into the holding hole 1' at an appropriate interval on the inner circumferential surface of the entrance and inner portion of the holding hole 1'.

保持孔１′の各シールリング１３．１４の間には、粘性
流体を供給する為の送液孔１５が各開設しである。Liquid feeding holes 15 for supplying viscous fluid are opened between each seal ring 13, 14 of the holding hole 1'.

かかる保持孔１′内をこは、その入口部と奥部に犬なる
大きさの間隙１６を設けて軸受スリーブ３を挿入設置す
る。The bearing sleeve 3 is inserted into the holding hole 1' with a dog-sized gap 16 provided between the entrance and the inner part thereof.

第１図の実施例の場合、軸受スリーブ３は、その環部が
断面路り字型を成し、外周にはシールリング１３，１４
の肉厚より犬なる幅でその内周面Ｏこ対してわずかの間
隔を維持できる深さの周溝１７．１７を掘設しである。In the case of the embodiment shown in FIG. 1, the ring portion of the bearing sleeve 3 has a cross-sectional shape, and seal rings 13, 14 are provided on the outer periphery.
A circumferential groove 17.17 is dug with a width a dog greater than the wall thickness and a depth that allows a slight spacing to be maintained on the inner circumferential surface of the groove.

而して軸受スリーブ３が前述の如く保持孔１１内（こ挿
入設置された際に、該溝１７．１７にてシールリング１
３．１４を受容し、且つ該溝の相互に最も離れた立上り
側面に該シールリング１３．１４の立上り、側面がわず
かな幅で摺接する。When the bearing sleeve 3 is inserted into the holding hole 11 as described above, the seal ring 1 is inserted into the groove 17.17.
3.14, and the rising side surfaces of the seal ring 13.14 that are farthest from each other slide into contact with the rising side surfaces of the grooves with a slight width.

かくして軸受スリーブ３の外周と外部材１の内周間の間
隙１６は、実質的に周溝１７，１７の相互に最も離れた
立上り側面で規定される幅の閉鎖系が構成される。Thus, the gap 16 between the outer periphery of the bearing sleeve 3 and the inner periphery of the outer member 1 constitutes a closed system with a width substantially defined by the mutually furthest rising sides of the circumferential grooves 17, 17.

図中１８はバネであり、軸受スリーブ３を半径方向に支
持している。In the figure, reference numeral 18 denotes a spring, which supports the bearing sleeve 3 in the radial direction.

この閉鎖系に粘性流体が圧送されスクイズ膜２が形成さ
れる。A viscous fluid is pumped into this closed system to form a squeeze film 2.

このスクイズ膜２は、ｔなる大きさの間隙１６の前記閉
鎖系でスクイズ効果（ダンパ効果）を発揮すると共に、
シールリング１３．１４の内周面と周溝１６，１７の底
部の間にわずかな間隙を形成しているので、この部分に
て急激な不つり合いの変化等による過渡的な軸受のふれ
回り回転を抑止している。This squeeze film 2 exerts a squeeze effect (damper effect) in the closed system of the gap 16 of size t, and
Since a small gap is formed between the inner circumferential surface of the seal ring 13, 14 and the bottom of the circumferential grooves 16 and 17, transient whirling rotation of the bearing due to sudden changes in unbalance, etc. can occur in this area. is suppressed.

かかる軸受スリーブ３内には、公知の軸受１０が該軸受
スリーブのＬ型部分に保持されている。In such a bearing sleeve 3 a known bearing 10 is held in an L-shaped part of the bearing sleeve.

そしてその軸受１０内には、軸９が固定保持されている
。A shaft 9 is fixedly held within the bearing 10.

保持孔１′の入口部に螺設せるナツト１２の内側には、
環状の座体１９，２０’が軸方向に遊動できるよう挿入
され、ナツト１２の内側に弾挿されたコイルスプリング
２０によって保持孔１′奥方に附勢されている。Inside the nut 12 screwed into the entrance of the holding hole 1', there is a
Annular seat bodies 19, 20' are inserted so as to be freely movable in the axial direction, and are biased toward the rear of the holding hole 1' by a coil spring 20 elastically inserted inside the nut 12.

而して座体１９，２０’は、スラスト方向の力に関する
限り外部材１と弾力的にではあるが実質的（こその一部
と着像すものとする。As far as the force in the thrust direction is concerned, the seat bodies 19, 20' are assumed to form a substantial, albeit elastic, part of the outer member 1.

この座体１９と２０′は、軸方向（こ重なり合って球面
座が構成されている。The seats 19 and 20' overlap in the axial direction to form a spherical seat.

この座体１９，２０’を含めた意味の外部材１は、前述
の如く保持孔１′の奥部に形成された段部１１と座体２
０′とが保持孔１′内で対向している。The external member 1 including the seat bodies 19 and 20' includes the stepped portion 11 formed at the inner part of the holding hole 1' and the seat body 2 as described above.
0' are opposed within the holding hole 1'.

そしてそれらの対向面は、外部材１側のスラスト面４を
構成する。These opposing surfaces constitute a thrust surface 4 on the external member 1 side.

このスラスト面４には、環状の溝２１が掘設してあり、
こと（こ環状の磁石６がスラスト面４と同一面を形成す
るように収容設置されている。An annular groove 21 is dug in this thrust surface 4,
(This annular magnet 6 is housed and installed so as to form the same plane as the thrust surface 4.

他方、保持孔１′の入口側及び奥側に釦ける両軸受スリ
ーブ３の前記外部材１側のスラスト面４に対向する側面
は、軸受スリーブ３側のスラスト面５を構成し、このス
ラスト面５にも環状の溝２２が掘設してあり、ここｔこ
、外部材１側の磁石６に対しこれと同じ極を向けるよう
に環状の磁石７がスラスト面５と面一に収容設置されて
いる。On the other hand, the side surfaces of both bearing sleeves 3, which are buttoned on the entrance side and back side of the holding hole 1', opposite to the thrust surface 4 on the external member 1 side constitute a thrust surface 5 on the bearing sleeve 3 side, and this thrust surface An annular groove 22 is also dug in 5, in which an annular magnet 7 is housed flush with the thrust surface 5 so that the same polarity as that of the magnet 6 on the external member 1 side is directed. ing.

かくして外部材１側のスラスト面４に釦ける磁石６と軸
受スリーブ３側のスラスト面５における同一極性の磁石
７とが対向設置される。Thus, the magnet 6 buttoned on the thrust surface 4 on the side of the external member 1 and the magnet 7 of the same polarity on the thrust surface 5 on the side of the bearing sleeve 3 are placed facing each other.

外部材１のスラスト面４と軸受スリーブ３のスラスト面
５との間には、スラスト間隙８が形成される。A thrust gap 8 is formed between the thrust surface 4 of the outer member 1 and the thrust surface 5 of the bearing sleeve 3.

このスラスト間隙８は、各スラスト面４，５に設定され
る磁石６，７の磁力反発の臨界点にスラスト面４，５を
設けるだけで形成される。This thrust gap 8 is formed simply by providing the thrust surfaces 4, 5 at critical points of magnetic repulsion of the magnets 6, 7 set on each thrust surface 4, 5.

従って極めて強力な磁性を有する磁石を用いること（こ
より、スラスト間隙８は大きく採ることができ、これは
比較的大型の軸受装置に好適する。Therefore, by using a magnet with extremely strong magnetism, the thrust gap 8 can be made large, which is suitable for a relatively large bearing device.

このようＱこスラスト間隙８は、磁石６，７の同一極性
の反発力の臨界位置にスラスト面４，５が位置するよう
にすれば少なくともその本来の技術目的は十分に満足で
きる。If the thrust surfaces 4 and 5 are located at the critical position of the repulsive forces of the same polarity of the magnets 6 and 7, the Q thrust gap 8 can sufficiently satisfy at least its original technical purpose.

第１図の実施例では、コイルスプリング２０（こより座
体２０′を軸方向に附勢し、スラスト面４で保持孔１′
の入口部の軸受スリーブ３を磁性反発力（こより軸方向
（こ押しているので、弾器の摩擦接触なしに十分な予圧
が与えられるように構成しである。In the embodiment shown in FIG. 1, the coil spring 20 (the coil spring 20) urges the seat body 20' in the axial direction, and the thrust surface 4
Since the bearing sleeve 3 at the inlet part is pushed in the axial direction by a magnetic repulsive force, sufficient preload can be applied without frictional contact of the projectile.

一般的には、軸受（こ予圧をかける場合はスプリングを
軸受側面に当接して行なう。Generally, when applying preload to a bearing, a spring is brought into contact with the side surface of the bearing.

この予圧の大きさの設定は、軸受と弾器との摩擦を考慮
しなければならない。When setting the magnitude of this preload, friction between the bearing and the ammunition must be taken into consideration.

この実施例では、コイルスプリング２０を用いているが
、これらの弾器機構は、軸受に直接接触することなく、
摩擦の点は全く考慮する必要はない。In this embodiment, coil springs 20 are used, but these elastic mechanisms do not come into direct contact with the bearings.
There is no need to consider friction at all.

この発明に用いる上記磁石６，７は、第２図の如く環状
を成し、スラスト面４，５に取り付けられる外周と内周
は、環状を威し非磁性体（黄銅やプラスチックス等）で
成る環体２３，２ｆｆで被覆されている。The magnets 6 and 7 used in this invention are annular as shown in FIG. 2, and the outer and inner peripheries attached to the thrust surfaces 4 and 5 are annular and made of non-magnetic material (brass, plastic, etc.). It is covered with a ring body 23, 2ff consisting of.

図示はしていないが、磁石は、軸受の種類構造（こよっ
て種々の形態を選択し得る。Although not shown in the drawings, the magnet may have a bearing type structure (therefore, various forms may be selected).

例えば同じ環状でも相対応する円錐形状を成しているも
のは対向するスラスト面が相対応する円錐形状を成して
いる場合に用い得る。For example, the same annular shape but corresponding conical shapes can be used when the opposing thrust surfaces have corresponding conical shapes.

この場合、前記予圧と関連して軸受の求心にも貢献する
。In this case, in conjunction with the preload, it also contributes to the centripetal movement of the bearing.

その他スラスト面でうじを予め回転方向にピンのような
手段で回転方向（このみ固定して釦き、磁石の分割ピー
スをスラスト面に多数配列する場合もあり、更Ｇこ該分
割ピースを環状Ｇこ接続した状態でスラスト面（こ設置
することもあり得る。In other cases, the maggots are fixed in the rotating direction on the thrust surface with a means such as a pin (button), and a large number of divided pieces of magnets are arranged on the thrust surface. It is also possible to install the thrust surface with this connected.

第３図の実施例は、この発明をタービンの軸受装置に適
用した例である。The embodiment shown in FIG. 3 is an example in which the present invention is applied to a bearing device for a turbine.

タービンＴを有するタービン軸９には、その構造上太線
矢印方向にスラスト荷重がかかる。Due to its structure, a thrust load is applied to the turbine shaft 9 having the turbine T in the direction of the bold arrow.

この実施例では、タービン軸９のかかるスラスト荷重を
受けてもスラスト面間の接触がなく、軸受（こ予圧をか
け、更に軸方向にもダンパ支持する構造にした。In this embodiment, there is no contact between the thrust surfaces even when receiving the thrust load applied by the turbine shaft 9, and the structure is such that a preload is applied to the bearing, and the damper is also supported in the axial direction.

即ち保持孔１′の入口部に、外周に取り付はフランジ２
４を内周に保持孔１′の内径を小さくする如きリブ状の
部分２５を有するブシュ２６が取り付けられている。That is, a flange 2 is attached to the outer periphery of the inlet of the holding hole 1'.
A bush 26 is attached to the inner periphery of the bushing 26, which has a rib-shaped portion 25 that reduces the inner diameter of the holding hole 1'.

而してブシュ２６のリブ状の部分２５の内側は、外部材
１のスラスト面４を形成し、ここに磁石６が設定されて
いる。The inner side of the rib-shaped portion 25 of the bushing 26 forms the thrust surface 4 of the outer member 1, and the magnet 6 is set here.

保持孔１内には、入口部と奥部とに前記実施例と同様（
こ軸受スリーブ３を介して軸受１０が設定される。Inside the holding hole 1, there is a hole (
A bearing 10 is installed via the bearing sleeve 3.

保持孔１′の奥の外部材１側のスラスト面４には、磁石
６が設置される。A magnet 6 is installed on the thrust surface 4 on the side of the external member 1 at the back of the holding hole 1'.

保持孔１′の奥の軸受スリーブ３は、前記実施例と同様
のスラスト面５にて外部材１側のスラスト面４（こ対向
し、そのスラスト面５にスラスト面４の磁石６と同一極
性の磁石７を有し、磁力反発（こよってもたらされるス
ラスト間隙８をトいて設置される。The bearing sleeve 3 at the back of the holding hole 1' has a thrust surface 5 similar to that of the previous embodiment, which faces the thrust surface 4 on the external member 1 side, and has a thrust surface 5 having the same polarity as the magnet 6 of the thrust surface 4. It has a magnet 7 and is installed through magnetic repulsion (thus creating a thrust gap 8).

この軸受スリーブ３は、その外周ラジアル方向に２条の
フランジ２７が適当な間隔をむいて突設しである。This bearing sleeve 3 has two flanges 27 protruding from its outer periphery in the radial direction at appropriate intervals.

このフランジ２７は、その外周端が保持孔１′の内周面
に対しわずかな間隔を維持するだけ突出し、これをこよ
って軸受スリーブ３の落ち込みを抑止している。The outer peripheral end of the flange 27 protrudes from the inner peripheral surface of the holding hole 1' by a small distance, thereby preventing the bearing sleeve 3 from falling.

またこの場合、フラン２２７の外側には、フランジ外側
壁をその１１延長して掘り下げた周溝１７，１７を有し
、ここに保持孔１′内周に摺接するシールリング１３，
１４を溝底昏こわずかの間隙を耘いて受容している。In this case, the outer side of the flange 227 has circumferential grooves 17, 17 dug by extending the outer wall of the flange 11, and the seal ring 13, which slides into contact with the inner circumference of the holding hole 1', is provided on the outer side of the flange 227.
14 has been accepted through a small gap at the bottom of the ditch.

而して軸受スリーブ３のフランジ２７間の外周面、保持
孔１′内周面間に間隙１６が設けられ、ここに送液孔１
５より送られてくる粘性流体（こよりスクイズ膜２が形
成される。A gap 16 is provided between the outer circumferential surface between the flanges 27 of the bearing sleeve 3 and the inner circumferential surface of the holding hole 1'.
The viscous fluid sent from 5 forms the squeeze film 2.

図においてはスクイズ膜２は、十分な程度の厚さに構成
され、このスクイズ膜２により十分のスクイズ効果（ダ
ンパ効果）が得られ更（こフランジ２７と保持孔１′内
面との微小間隙にて所謂落込みを防止している。In the figure, the squeeze film 2 is configured to have a sufficient thickness, and a sufficient squeeze effect (damper effect) can be obtained by this squeeze film 2. This prevents so-called depression.

保持孔１′の人口部の軸受スリーブ３もほぼ同様の構成
に成りそのスラスト面５（こ外部材１のスラスト面４の
磁石６と同一極性の磁石７を有している。The bearing sleeve 3 of the artificial part of the retaining hole 1' has a substantially similar construction and has a thrust surface 5 thereof (a magnet 7 of the same polarity as the magnet 6 of the thrust surface 4 of the outer member 1).

この保持孔１′の入口部の軸受スリーブ３の外周には、
ラジアル方向Ｑこ大きく張り出したスラストフランジ２
８が設けられ、外部材１とブシュ２６先端のスラスト面
４′との間に形成された溝２９内に受容されている。On the outer periphery of the bearing sleeve 3 at the entrance of the holding hole 1',
Thrust flange 2 that protrudes greatly in the radial direction Q
8 is provided and received in a groove 29 formed between the outer member 1 and the thrust surface 4' of the tip of the bushing 26.

スラストフランジ２８のスラスト面５とブシュ２６の先
端のスラスト面４′には、各々同一極性の磁石７，６′
を設け、スラスト面５，４′間に磁力反発によってもた
らされる間隙８を構成する。The thrust surface 5 of the thrust flange 28 and the thrust surface 4' of the tip of the bushing 26 are provided with magnets 7, 6' of the same polarity, respectively.
A gap 8 is formed between the thrust surfaces 5 and 4' by magnetic repulsion.

スクイズ膜２の粘性流体はこの間隙Ｇこも満される。The viscous fluid in the squeeze membrane 2 also fills this gap G.

この実施例では、各スラスト間隙８の大きさは、予め軸
受スリーブ３と外部材１の各スラスト面５゜４（４’）
の磁石７，６（６’）の磁力反発の臨界点より近ずけて
セットしである。In this embodiment, the size of each thrust gap 8 is set in advance by 5°4 (4') of each thrust surface of the bearing sleeve 3 and the outer member 1.
It is set closer to the critical point of magnetic repulsion of the magnets 7, 6 (6').

而して軸受けには、磁石反発なこよる予圧がかけられる
が、タービンＴを回すこと（こより生じる反力【こよる
スラスト荷重が太線の矢印方向にかかるので、軸９は同
方向に移動する。A preload is applied to the bearing due to magnetic repulsion, but by rotating the turbine T (reaction force generated by this) a thrust load is applied in the direction of the bold arrow, so the shaft 9 moves in the same direction.

従ってスラスト間隙８の大きさｔｌ、ｔ２はｔ／１．
ｔ’２ｔこ変化する。Therefore, the sizes tl and t2 of the thrust gap 8 are t/1.
t'2t changes.

このときのスラスト荷重は、保持孔１′の入口部の軸受
（こ釦ける２個所のスラスト面４，５及び４′。At this time, the thrust load is applied to the bearing at the entrance of the holding hole 1' (the two thrust surfaces 4, 5 and 4' that press the button).

５′間の磁力反発で十分に受けられる。The magnetic repulsion between 5′ is sufficient.

他方保持孔１′の奥の軸受は、間隙８が大きくなるので
予圧は低下するが、予め磁力反発の臨界点よりスラスト
面４，５を相互（こ近すけであるので予圧は零Ｑこはな
らない。On the other hand, for the bearing at the back of the holding hole 1', the preload decreases because the gap 8 becomes larger. It won't happen.

この実施例の場合、スクイズ膜２を形成する粘性流体は
、保持孔１′の入口部の軸受では、スラストフランジ２
８と外部材１との間にも満され、特に、タービンＴの回
転（こよるスラスト振動を減衰する。In this embodiment, the viscous fluid forming the squeeze film 2 is transferred to the thrust flange 2 at the bearing at the inlet of the holding hole 1'.
8 and the external member 1, and particularly damps thrust vibrations caused by the rotation of the turbine T.

このスラストフランジ２８を用いる方式は、スラスト荷
重（こ対する支持力の所謂力のモメントが大きくなり極
めて効果的である。This method using the thrust flange 28 is extremely effective because the thrust load (the so-called moment of supporting force against it) becomes large.

よってスクイズ膜２による径方向のダンパ効果は摩擦抵
抗なく完全に発揮される。Therefore, the damper effect in the radial direction by the squeeze film 2 is fully exerted without frictional resistance.

第４図の実施例は、第３図の実施例と同様スラストフラ
ンジ２８を有する軸受スリーブ３を用いている。The embodiment of FIG. 4 uses a bearing sleeve 3 having a thrust flange 28, similar to the embodiment of FIG.

この場合、スラストフランジ２８には、１個の磁石７が
その両極を対向する外部材１のスラスト面４，４に設け
た同一極性の磁石６，６と対向せしめる。In this case, in the thrust flange 28, one magnet 7 has both poles facing magnets 6, 6 of the same polarity provided on the thrust surfaces 4, 4 of the opposing external member 1.

而してこの場合、軸受スリーブ３は、両面からスラスト
支持される。In this case, the bearing sleeve 3 is thrust supported from both sides.

尚この実施例の場合、軸受スリーブ３は、シールリング
をこよってスクイズ膜２の粘性流体はシールされること
なく軸受機構にも流出して軸受の冷却に貢献するように
なっている。In the case of this embodiment, the viscous fluid in the squeeze film 2 of the bearing sleeve 3 passes through the seal ring and flows out into the bearing mechanism without being sealed, thereby contributing to the cooling of the bearing.

この発明によれば、軸受はその軸受スリーブがスラスト
方向にロックされることなくスクイズ膜は、効果的にダ
ンパ作用を行なうことができる。According to this invention, the squeeze film of the bearing can effectively perform a damping action without the bearing sleeve being locked in the thrust direction.

しかもスラスト間隙を磁力反発力の臨界点より小さく採
ることにより、軸受に対し摩擦を全く附与することなく
予圧することができる。Moreover, by making the thrust gap smaller than the critical point of magnetic repulsion, it is possible to preload the bearing without imparting any friction at all.

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

第１図は側断面、第２図は磁石の１例を示す斜視図、第
３図は別実施例の側断面図、第４図は更に別実施例の側
断面図である。 図中１は外部材、２はスクイズ膜、３は軸受スリーブ、
４，４′は外部材のスラスト面、５は軸受スリーブのス
ラスト面、６．６’は外部材のスラスト面の磁石、７は
軸受スリーブのスラスト面の磁石、８はスラスト間隙、
９は軸、１０は軸受。1 is a side sectional view, FIG. 2 is a perspective view showing one example of the magnet, FIG. 3 is a side sectional view of another embodiment, and FIG. 4 is a side sectional view of yet another embodiment. In the figure, 1 is the external material, 2 is the squeeze membrane, 3 is the bearing sleeve,
4 and 4' are thrust surfaces of the external member, 5 are thrust surfaces of the bearing sleeve, 6 and 6' are magnets of the thrust surface of the external material, 7 are magnets of the thrust surface of the bearing sleeve, and 8 are thrust gaps;
9 is the shaft, 10 is the bearing.

Claims (1)

【特許請求の範囲】 １ 外部材内に、スクイズ膜を介して軸受スリーブを保
持し、外部材と軸受スリーブの各スラスト面に、同一極
性の磁石を対向設置して、スラスト面間に磁力反発（こ
よるスラスト間隙を構成した軸受支持装置。 ２ 支承される軸に固定された軸受（こ外嵌して一体化
せる軸受スリーブを、外部材内（こスクイズ膜を介して
保持し、外部材と軸受スリーブの各スラスト面に、同一
極性の磁石を対向して設置して、スラスト面間に磁力反
発によってもたらされるスラスト間隙を構成し、該スラ
スト間隙を、磁力反発に抗して縮小した状態に設定する
ことにより軸９に磁力反発による予圧を附与した軸受支
持装置。[Claims] 1. A bearing sleeve is held within an external member through a squeeze film, and magnets of the same polarity are placed facing each other on each thrust surface of the external member and the bearing sleeve to create magnetic repulsion between the thrust surfaces. (Bearing support device that constitutes a thrust gap like this. Magnets of the same polarity are installed facing each other on each thrust surface of the bearing sleeve to form a thrust gap created by magnetic repulsion between the thrust surfaces, and the thrust gap is reduced against the magnetic repulsion. A bearing support device in which a preload is applied to the shaft 9 by magnetic repulsion.
JP50141324A 1975-11-25 1975-11-25 Jikuukeshijisouchi Expired JPS5829407B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP50141324A JPS5829407B2 (en) 1975-11-25 1975-11-25 Jikuukeshijisouchi

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP50141324A JPS5829407B2 (en) 1975-11-25 1975-11-25 Jikuukeshijisouchi

Publications (2)

Publication Number Publication Date
JPS5264550A JPS5264550A (en) 1977-05-28
JPS5829407B2 true JPS5829407B2 (en) 1983-06-22

Family

ID=15289265

Family Applications (1)

Application Number Title Priority Date Filing Date
JP50141324A Expired JPS5829407B2 (en) 1975-11-25 1975-11-25 Jikuukeshijisouchi

Country Status (1)

Country Link
JP (1) JPS5829407B2 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6236846B2 (en) * 1984-03-07 1987-08-10 Chugoku Kikai Seisakusho Kk

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2452025A1 (en) * 1979-03-20 1980-10-17 Aerospatiale PRACTICALLY NULL AXIAL ROLLING BEARING
JP6777417B2 (en) * 2016-04-04 2020-10-28 Ntn株式会社 Vibration damping bearing device
JP6856403B2 (en) * 2017-02-24 2021-04-07 本田技研工業株式会社 Squeeze film damper bearing device
JP2020026865A (en) * 2018-08-16 2020-02-20 ミネベアミツミ株式会社 Rotation device

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6236846B2 (en) * 1984-03-07 1987-08-10 Chugoku Kikai Seisakusho Kk

Also Published As

Publication number Publication date
JPS5264550A (en) 1977-05-28

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