JPS5842656Y2 - gas bearing structure - Google Patents
gas bearing structureInfo
- Publication number
- JPS5842656Y2 JPS5842656Y2 JP16767479U JP16767479U JPS5842656Y2 JP S5842656 Y2 JPS5842656 Y2 JP S5842656Y2 JP 16767479 U JP16767479 U JP 16767479U JP 16767479 U JP16767479 U JP 16767479U JP S5842656 Y2 JPS5842656 Y2 JP S5842656Y2
- Authority
- JP
- Japan
- Prior art keywords
- bearing
- gas
- damper member
- gas bearing
- retainer
- 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
Links
Landscapes
- Support Of The Bearing (AREA)
- Magnetic Bearings And Hydrostatic Bearings (AREA)
Description
【考案の詳細な説明】
この考案は超高速高性能のターボ機械等に適用できるよ
うにしてその適用時の高速安定性を向上させ得るように
改良したガス軸受構造に関する。[Detailed Description of the Invention] This invention relates to an improved gas bearing structure that can be applied to ultra-high-speed, high-performance turbomachines, etc., and can improve high-speed stability when used.
一般に01Jング等のダンパ部材で支持されたガス軸受
は、高速回転時の安定性に優れて簡便であることから、
例えば歯科用バンドピースに広く実用化されて毎分50
万回転にも達している。Gas bearings supported by damper members such as 01J generally have excellent stability during high-speed rotation and are simple.
For example, it is widely used in dental band pieces, and
It has reached 10,000 rotations.
ところが、上記ガス軸受は、01Jング等ダンパ部材の
寸法精度に大きなバラツキがあることから、そのままで
は超高速、高性能のターボ機械には適用できなかった。However, the above-mentioned gas bearing could not be applied as it is to ultra-high-speed, high-performance turbomachinery because of large variations in the dimensional accuracy of damper members such as 01J rings.
すなわち、この種のターボ機械に上記ガス軸受をそのま
ま適用したのでは、軸受中心とケーシング中心とが一致
しないために、微小な隙間が要求されるターボ機械の軸
シールやシュラウド、隙間等を大きく設計しなければな
らず、ターボ機械の高性能化が達成できなくなる。In other words, if the gas bearing described above is applied as is to this type of turbomachinery, the center of the bearing and the center of the casing will not match, so the shaft seals, shrouds, gaps, etc. of turbomachinery that require minute gaps must be designed to be large. This would make it impossible to achieve higher performance in turbomachinery.
そこで、ダンパ部材の寸法精度を向上させればよいが、
しかし、その寸法精度はダンパ部材の成形加工上の点か
ら限界があってそれ以上に寸法精度を上げることは至難
の技術である。Therefore, it would be better to improve the dimensional accuracy of the damper member, but
However, the dimensional accuracy has a limit due to the molding process of the damper member, and it is an extremely difficult technique to further increase the dimensional accuracy.
この考案は上記事情に鑑みてなされたもので、その目的
は、特別な超精密加工等を一切必要とせずに通常の加工
技術で形成された0 1Jング等ダンパ部材を介して支
持されているものでありながら、軸シールやシュラウド
、隙間笠を小さく設計した超高速、高性能のターボ機械
に伺ら支障なく適用することができてその高速回転時の
安定性を確保できるように芯出し調整手段を設けたガス
軸受構造を簡単な構成で提供するにある。This idea was made in view of the above circumstances, and its purpose is to provide support through damper members such as 01J rings, which are formed using normal processing techniques without any special ultra-precision processing. However, it can be applied to ultra-high-speed, high-performance turbo machinery with small shaft seals, shrouds, and gap caps without any problems, and centering adjustment can be made to ensure stability during high-speed rotation. To provide a gas bearing structure provided with a means with a simple configuration.
以下に、この考案の好適一実施例を図面に基づいて説明
する。A preferred embodiment of this invention will be described below with reference to the drawings.
図中符号1はラジアルタービンなど超高速高性能のター
ボ機械のケーシングであり、その軸受部分にはターボ機
械の回転軸2がガス軸受Aを介して支承させである。Reference numeral 1 in the figure is a casing of an ultra-high-speed, high-performance turbomachine such as a radial turbine, and a rotating shaft 2 of the turbomachine is supported via a gas bearing A at the bearing portion of the casing.
このガス軸受Aは、回転軸2のスラストカラ一部3に衝
合させたスラット軸受を兼ねるリテーナ4と、このリテ
ーナにOリングからなるダンパ部材5,6を介して支持
させたジャーナル軸受7とを有する構造になっている。This gas bearing A includes a retainer 4 which also serves as a slat bearing and is abutted against a thrust collar part 3 of a rotating shaft 2, and a journal bearing 7 which is supported by this retainer via damper members 5 and 6 made of O-rings. It has a structure that has
すなわち上記リテーナ4は、軸方向一端面(図中上端面
)が回転軸2のスラストカラ一部3に衝合するスラスト
軸受面4aとして形成され、かつ内周壁面にスラスト軸
受面4a側の開口径より大径の段差孔部8がダンパ収納
兼ガス導入用空間部として形成しであるもので、ケーシ
ング1に設けたガス供給孔9を上記スラストカラ一部3
とスラスト軸受面4aとの間および段差孔部8内に接続
させるためのガス導入分岐孔10および11と、潤滑ガ
スを導出するためのガス排気孔12とを有してスラスト
軸受面4aとの反対面にダイヤフラム16および押え板
17がそれぞれ同心的に取付けられる構造となっている
。That is, the retainer 4 has one end surface in the axial direction (upper end surface in the figure) formed as a thrust bearing surface 4a that abuts against the thrust collar part 3 of the rotating shaft 2, and has an opening diameter on the side of the thrust bearing surface 4a on the inner peripheral wall surface. A step hole 8 with a larger diameter is formed as a space for housing the damper and for introducing gas, and the gas supply hole 9 provided in the casing 1 is connected to the thrust collar part 3.
It has gas introduction branch holes 10 and 11 for connection between and the thrust bearing surface 4a and inside the step hole 8, and a gas exhaust hole 12 for leading out lubricating gas. The structure is such that a diaphragm 16 and a presser plate 17 are each attached concentrically to the opposite surface.
一方、ジャーナル軸受7は、周壁中間部を貫通するガス
通孔13を有して外周壁に軸方向へ適宜の間隙で離間す
る一方の環状鍔14.15が一体形成された構造になっ
ている。On the other hand, the journal bearing 7 has a gas passage hole 13 passing through the middle part of the peripheral wall, and has annular flanges 14 and 15 integrally formed on the outer peripheral wall and spaced apart from each other with an appropriate gap in the axial direction. .
斯様なジャーナル軸受7はダンパ部材5゜6を介してリ
テーナ4の段差孔部8で弾性的に保持さ減、その状態に
のいて、図中上側のダンパ部材5はリテーナ4とジャー
ナル軸受7との間で段差孔部8の上側段壁と環状鍔14
との間に形成された空間部に収納され、かつ図中下側の
ダンパ部材6はジャーナル軸受7の下側環状鍔15の下
側でリテーナ4とジャーナル軸受7との間に介在してい
る。Such journal bearing 7 is elastically held in step hole 8 of retainer 4 via damper member 5. between the upper step wall of the step hole 8 and the annular collar 14.
The damper member 6 on the lower side of the figure is interposed between the retainer 4 and the journal bearing 7 below the lower annular collar 15 of the journal bearing 7. .
もって、上下の環状鍔14.15を有するジャーナル軸
受7は、どの部分においても固定側のリテーナ4は雰よ
り後述のダイヤフラム16や押え板17などと直接接触
しない弾性的支持構成にしである。Therefore, the journal bearing 7 having the upper and lower annular flanges 14, 15 has an elastic support structure in which the retainer 4 on the fixed side does not come into direct contact with the diaphragm 16, presser plate 17, etc., which will be described later.
そして、リテーナ4の下面には下側のダンパ部材6を押
えるべくダイヤフラム16を介して押え板17が複数の
取付ボルト18でねじ止めされている。A presser plate 17 is screwed to the lower surface of the retainer 4 via a diaphragm 16 with a plurality of mounting bolts 18 in order to press the lower damper member 6 .
その押え板17に、ダイヤフラム16を介してダンパ部
材6を圧縮する芯出し調整手段として複数の調整ねじ1
9が周方向略等間隔に設けである。A plurality of adjustment screws 1 are provided on the presser plate 17 as centering adjustment means for compressing the damper member 6 via the diaphragm 16.
9 are provided at approximately equal intervals in the circumferential direction.
しかして、ケーシング1と回転軸2の同心度を改善する
必要がある場合には、それらの同心度を適当な方法で測
定して同心度を改善させ得る位置の調整ねじ19を回動
操作することにより、この調整ねじ19でダイヤフラム
16を介してダンパ部材6を環状鍔15との間で軸方向
へ部分的に圧縮させればよく、もって、上記ダンパ部材
6が圧縮部分でジャーナル軸受7を径方向に押動変位さ
せることとなるため、ケーシング1と回転軸2の同心度
は目的通りに改善される。Therefore, if it is necessary to improve the concentricity between the casing 1 and the rotating shaft 2, measure the concentricity by an appropriate method and rotate the adjustment screw 19 at a position where the concentricity can be improved. This allows the damper member 6 to be partially compressed in the axial direction between the damper member 6 and the annular collar 15 via the diaphragm 16 using the adjustment screw 19, so that the damper member 6 can compress the journal bearing 7 in the compressed portion. Since the casing 1 is pushed and displaced in the radial direction, the concentricity between the casing 1 and the rotating shaft 2 is improved as intended.
なお、上記実施例において、ケーシング1のガス供給孔
9に送られたガスは、リテーナ4のガス導入分岐孔10
.11のそれぞれを通ってスラスト軸受面4a部および
ジャーナル軸受7を潤滑してガス排気孔12を通ること
により排気される流れとなる。In the above embodiment, the gas sent to the gas supply hole 9 of the casing 1 is transferred to the gas introduction branch hole 10 of the retainer 4.
.. 11, the thrust bearing surface 4a and the journal bearing 7 are lubricated, and the gas is exhausted by passing through the gas exhaust hole 12.
以上型するにこの考案では、次のごとき種々の効果が得
られる。In summary, this invention provides the following various effects.
(1)OIJング等のダンパ部材を用いたガス軸受構造
でありながら、そのダンパ部材を軸方向へ部分的に圧縮
してジャーナル軸受を径方向に変位させ得る芯出し調整
手段を備えつけ、これによりジャーナル軸受の芯出し調
整を随時随意に行なえるようにしたので、上記ダンパ部
材の寸法精度(加工精度)のバラツキをジャーナル軸受
の芯出し調整によって是正することができる。(1) Although the gas bearing structure uses a damper member such as an OIJ ring, it is equipped with a centering adjustment means that can partially compress the damper member in the axial direction and displace the journal bearing in the radial direction. Since the centering of the journal bearing can be adjusted at any time, variations in the dimensional accuracy (machining accuracy) of the damper member can be corrected by adjusting the centering of the journal bearing.
(2)従って、この考案によるガス軸受は、超高速高性
能のターボ機械に伺ら支障なく適用することができ、そ
の高速回転時においても安定性を保障し得る。(2) Therefore, the gas bearing according to this invention can be applied to ultra-high-speed, high-performance turbomachinery without any problems, and can ensure stability even during high-speed rotation.
(3)また、上記ダンパ部材は特別な超精密加工等を一
切節すことなく通常の加工技術で形成されたものを用い
ればよいので、ガス軸受の製作加工が容易化してコスト
ダウンが図れる。(3) Furthermore, since the damper member can be formed using normal processing techniques without any special ultra-precision processing, the gas bearing can be manufactured easily and costs can be reduced.
図面はこの考案の好適一実施例を示すガス軸受構造の断
面図である。
図中、4はリテーナ乃至スラスト軸受、5,6はダンパ
部材、7はジャーナル軸受、16.19は芯出し調整手
段として例示したダイヤフラムと調整ねじである。The drawing is a sectional view of a gas bearing structure showing a preferred embodiment of this invention. In the figure, 4 is a retainer or thrust bearing, 5 and 6 are damper members, 7 is a journal bearing, and 16 and 19 are a diaphragm and an adjustment screw, which are illustrated as centering adjustment means.
Claims (1)
テーナ乃至スラスト軸受に支持されたガス軸受構造にお
いて、ダンパ部材を軸方向に圧縮してジャーナル軸受を
径方向に変位させる芯出し調整手段を備えたことを特徴
とするガス軸受構造。In a gas bearing structure in which a journal bearing is supported by a retainer or a thrust bearing via a damper member such as an 01J ring, a centering adjustment means is provided for compressing the damper member in the axial direction and displacing the journal bearing in the radial direction. Gas bearing structure featuring
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP16767479U JPS5842656Y2 (en) | 1979-12-04 | 1979-12-04 | gas bearing structure |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP16767479U JPS5842656Y2 (en) | 1979-12-04 | 1979-12-04 | gas bearing structure |
Publications (2)
Publication Number | Publication Date |
---|---|
JPS5684124U JPS5684124U (en) | 1981-07-07 |
JPS5842656Y2 true JPS5842656Y2 (en) | 1983-09-27 |
Family
ID=29678526
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP16767479U Expired JPS5842656Y2 (en) | 1979-12-04 | 1979-12-04 | gas bearing structure |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPS5842656Y2 (en) |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP6767720B2 (en) * | 2015-07-08 | 2020-10-14 | パナソニックIpマネジメント株式会社 | Turbomachinery |
CN111156180A (en) * | 2020-01-19 | 2020-05-15 | 至玥腾风科技集团有限公司 | Gas compressor, rotor system and micro gas turbine |
-
1979
- 1979-12-04 JP JP16767479U patent/JPS5842656Y2/en not_active Expired
Also Published As
Publication number | Publication date |
---|---|
JPS5684124U (en) | 1981-07-07 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US7371011B2 (en) | Turbocharger shaft bearing system | |
JPH0540273Y2 (en) | ||
US7517154B2 (en) | Turbocharger shaft bearing system | |
GB1446878A (en) | Bearing arrangements in gas turbine engines | |
US3692372A (en) | Thermally expansible bearing assembly | |
GB2241994B (en) | A mounting assembly for a shaft | |
KR890000267B1 (en) | Bearing device for an exhaust gas turbo changer with tandem rolling contact bearing | |
ATE49456T1 (en) | STORAGE OF AN EXHAUST GAS TURBOCHARGER. | |
US4465446A (en) | Radial and thrust bearing mountings providing independent loading | |
IT1237935B (en) | ENGINE BEARING ASSEMBLY | |
US4184720A (en) | Air-supported bearing for turbine engines | |
US4209207A (en) | Thrust bearing assembly | |
US20030072509A1 (en) | Bearing system for high-speed rotating machinery | |
JPS5842656Y2 (en) | gas bearing structure | |
JPH0639884B2 (en) | Turbin Shaft Seal Assembly | |
US5257905A (en) | Rotor coupling anti-windage apparatus | |
JPS6014989Y2 (en) | gas bearing structure | |
GB2225394A (en) | Shaft sealing arrangement | |
US3865504A (en) | Axial compressor | |
JP2826640B2 (en) | How to fix ceramic bearings | |
CA1185644A (en) | Bearing support structure | |
JPH0218241Y2 (en) | ||
CN220869703U (en) | Axial positioning structure of sliding bearing of canned motor pump | |
JPS5910346Y2 (en) | Bearing structure for high-speed rotating equipment | |
GB775456A (en) | Improvements in or relating to rotatable member mounting device |