JPH02129404A - Radial-type gas bearing device - Google Patents
Radial-type gas bearing deviceInfo
- Publication number
- JPH02129404A JPH02129404A JP28244988A JP28244988A JPH02129404A JP H02129404 A JPH02129404 A JP H02129404A JP 28244988 A JP28244988 A JP 28244988A JP 28244988 A JP28244988 A JP 28244988A JP H02129404 A JPH02129404 A JP H02129404A
- Authority
- JP
- Japan
- Prior art keywords
- rotating shaft
- bearing
- shaft
- axial direction
- gas 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.)
- Pending
Links
- 238000001125 extrusion Methods 0.000 abstract description 5
- 230000003068 static effect Effects 0.000 abstract description 3
- 238000010586 diagram Methods 0.000 description 5
- 244000208734 Pisonia aculeata Species 0.000 description 3
- 235000017166 Bambusa arundinacea Nutrition 0.000 description 1
- 235000017491 Bambusa tulda Nutrition 0.000 description 1
- 241001330002 Bambuseae Species 0.000 description 1
- 235000015334 Phyllostachys viridis Nutrition 0.000 description 1
- 239000011425 bamboo Substances 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 210000002784 stomach Anatomy 0.000 description 1
- 239000000725 suspension Substances 0.000 description 1
Landscapes
- Sliding-Contact Bearings (AREA)
Abstract
Description
【発明の詳細な説明】
〔発明の目的〕
（産業上の利用分野）
この発明は、ガスタービン工作機械等のような高速回転
機械に用いるラジアル形気体軸受装置に関する。DETAILED DESCRIPTION OF THE INVENTION [Object of the Invention] (Industrial Application Field) The present invention relates to a radial gas bearing device used in a high-speed rotating machine such as a gas turbine machine tool.
（従来の技術）
第５図は、従来のラジアル形気体軸受装置が回転機器に
ユニットどして取り付けられた状態を示す縦断面図であ
る。(Prior Art) FIG. 5 is a longitudinal cross-sectional view showing a state in which a conventional radial gas bearing device is attached as a unit to a rotating device.
一般に、このラジアル形気体軸受装置は、軸支承部とし
ての軸受ハウジングＩＡ、ＩＢから気体を噴射させ、回
転軸２と軸受ハウジング１Ａ、１Ｂとの間に気ｙｉ：層
を形成し、この気流層の気体支持力によって回転軸２を
浮遊させ、非接触にて回転軸２を支承リ−るものである
。この場合、２組の軸受ハウジングＩＡ、１Ｂの軸方向
位置はそれぞれ固定されている。したがって、これら軸
受ハウジングＩＡ、ＩＢ間距離すなわら軸支承部スパン
Ｊも一定距離に固定されている。In general, this radial type gas bearing device injects gas from the bearing housings IA and IB as shaft support parts to form an air layer between the rotating shaft 2 and the bearing housings 1A and 1B, and this air flow layer The rotating shaft 2 is suspended by the gas supporting force, and the rotating shaft 2 is supported and reeled without contact. In this case, the axial positions of the two sets of bearing housings IA and 1B are each fixed. Therefore, the distance between these bearing housings IA and IB, that is, the shaft support span J is also fixed at a constant distance.
なお、図中符号３Ａ、３８μラジアル形気体軸受装置の
静止枠を示し、符号４は回転機器の本体枠を示す。In the figure, reference numeral 3A indicates a stationary frame of a 38μ radial gas bearing device, and reference numeral 4 indicates a main body frame of a rotating device.
（発明が解決しようとする課題）
上記従来のラジアル形気体軸受装置においては、回転軸
２の定格回転速度がその回転軸系の危険速度の近傍に存
在するので、回転軸２に共振現象が表われる場合、軸受
ハウジングＩＡ、１Ｂからの気体の噴射量を変えて半径
方向の気体支承力を変化させ、これにより軸受ハウジン
グ１Ａ、１Ｂの剛性を変えて、回転軸系の危険速度を定
格回転速度から離すようにしている。(Problems to be Solved by the Invention) In the conventional radial type gas bearing device described above, the rated rotational speed of the rotating shaft 2 exists near the critical speed of the rotating shaft system, so a resonance phenomenon appears in the rotating shaft 2. In this case, the amount of gas injected from the bearing housings IA, 1B is changed to change the gas bearing force in the radial direction, and thereby the rigidity of the bearing housings 1A, 1B is changed, and the critical speed of the rotating shaft system is reduced to the rated rotational speed. I try to stay away from it.
ところが、回転軸２の回転角速度λωがｍ：回転軸系の
質量
に：回転軸の剛性
なる領域においては、回転軸２に振れまわり速度Ｃ７７
面の前向き振れまわり自由振動が生ずる。However, in the region where the rotational angular velocity λω of the rotating shaft 2 is m: the mass of the rotating shaft system: the rigidity of the rotating shaft, the whirling speed of the rotating shaft 2 is C77.
A free vibration occurs in which the surface swings forward.
この自由振動は振幅が時間と共に層数関数的に増大する
不安定振動である。This free vibration is an unstable vibration whose amplitude increases as a function of the number of layers over time.
また、実際の回転軸系の危険速度ωｃｒは、２組の軸受
ハウジングＩＡ、１Ｂの剛性が等しいものｋｂ：軸支承
部（軸受ハウジング）の剛性で示され、回転軸の剛性に
と軸支承部の剛性ｋｂの関数となっている。したがって
、従来の如く、回転軸の剛性ｋを一定にして、軸支承部
の剛性ｋｂのみを変化させただけでは、第３図に示すよ
うに、軸支承部の剛性ｋｂが２倍（あるいは１／２倍に
）に変化しても、回転軸系の危険速度ω。。In addition, the actual critical speed ωcr of the rotating shaft system is expressed by the rigidity of the two sets of bearing housings IA and 1B, where kb is the stiffness of the shaft support (bearing housing). It is a function of the stiffness kb. Therefore, as in the past, if the rigidity k of the rotating shaft is kept constant and only the rigidity kb of the shaft support part is changed, the rigidity kb of the shaft support part will double (or /2 times), the critical speed ω of the rotating shaft system. .
は精々１０％弱の変化しか得られない。この結果、従来
のラジアル形気体軸受装置では、回転軸系の共振現象を
確実に回避できないおそれがある。can only obtain a change of less than 10% at most. As a result, the conventional radial type gas bearing device may not be able to reliably avoid the resonance phenomenon of the rotating shaft system.
この発明は、上記事情を考慮してなされたものであり、
回転軸系の危険速度を広範囲に亘って変更し回転軸の共
振現象を確実に回避できるラジアル形気体軸受装置を提
供することを目的とする。This invention was made in consideration of the above circumstances,
It is an object of the present invention to provide a radial type gas bearing device that can change the critical speed of a rotating shaft system over a wide range and reliably avoid a resonance phenomenon of the rotating shaft.
（発明の構成）
（課題を解決するための手段）
この発明は、回転軸と複数の軸支承部との間に、この軸
支承部から噴射される気流層が存在し、この気流層の気
体支承力によって上記回転軸が支持されるラジアル形気
体軸受装置において、上記複数の軸支承部が上記回転軸
の軸方向に移動して軸支承部スパンを変更し得るよう構
成されたものである。(Structure of the Invention) (Means for Solving the Problems) This invention provides an air flow layer between a rotating shaft and a plurality of shaft support parts, which is injected from the shaft support parts, and a gas in the air flow layer. In a radial gas bearing device in which the rotating shaft is supported by a support force, the plurality of shaft supporting parts are configured to be able to move in the axial direction of the rotating shaft to change the shaft supporting part span.
（作用）
回転軸系の危険速度は、回転軸の剛性と軸支承部の剛性
との関数になっているので、気体支承枠を変えて軸支承
部の剛性を変化させるばかりでなく、軸支承部スパンを
変化させて回転軸の剛性を変化させれば、回転軸系の危
険速度を広範囲にＨっで変更でき、その結果、回転軸系
の共振現象を確実に回避できる。(Function) The critical speed of a rotating shaft system is a function of the rigidity of the rotating shaft and the rigidity of the shaft bearing, so in addition to changing the rigidity of the shaft bearing by changing the gas bearing frame, By changing the rigidity of the rotating shaft by changing the partial span, the critical speed of the rotating shaft system can be changed over a wide range, and as a result, resonance phenomena in the rotating shaft system can be reliably avoided.
（実／Ｍ例） 以下、この発明の実施例を図面に基づいて説明する。(Real/M example) Embodiments of the present invention will be described below based on the drawings.
第１図はこの発明に係るラジアル形気体軸受装置の一実
施例がユニツ１−として取り付けられた回転機器を示す
縦断面図、第２図は第１図の要部であり一実施例を示す
縦断面図である。FIG. 1 is a vertical cross-sectional view showing a rotating device in which an embodiment of the radial gas bearing device according to the present invention is attached as unit 1-, and FIG. 2 is a main part of FIG. 1 and shows one embodiment. FIG.
回転Ｉ１８の本体枠１１における軸方向両端には、向応
状態でラジアル形気体軸受装置の静止枠１２Ａ、１２Ｂ
がボルト等にて固定されている。これら本体枠１１およ
び静止枠１２Ａ、１２Ｂ内に回転軸１３が収容される。At both axial ends of the main body frame 11 of rotation I18, stationary frames 12A and 12B of a radial type gas bearing device are placed in a responsive state.
is fixed with bolts etc. The rotating shaft 13 is housed within the main body frame 11 and stationary frames 12A and 12B.
静止枠１２Ａ、１２Ｂ内には軸支承部としての軸受ハウ
ジング１４Ａ、１４Ｂが、複数例えば２組配設される。In the stationary frames 12A, 12B, a plurality of bearing housings 14A, 14B, for example, two sets, are arranged as shaft supporting parts.
この軸受ハウジング１４Ａ、Ｂは、静圧供給管１５Ａ、
１５Ｂから供給された気体を噴射して軸受ハウジング１
４Ａ、Ｂと回転軸１３との間に気流層を形成し、この気
流層の有する気体支承力によって回転軸１３を非接触支
承する。These bearing housings 14A, B have static pressure supply pipes 15A,
The bearing housing 1 is injected with the gas supplied from 15B.
An air layer is formed between 4A, 4B and the rotating shaft 13, and the rotating shaft 13 is supported in a non-contact manner by the gas supporting force of this air layer.
軸受ハウジング１４Ａ、Ｂは円筒状ホルダ１６Ａ、１６
Ｂの内周に嵌合され、またこれら円筒状ホルダ１６△、
Ｂは静止枠１２Ａ、Ｂの内周に軸方向スライド自在に嵌
合される。また、静止枠１２Ａ、Ｂの軸方向端面には、
周方向等配位置に複数個例えば３個の押出し相位！！調
整ボルト１７が設けられ、ざらにこれら押出し用位置調
整ボルト１７を挟む位置に引戻し用位置調整ボルト１８
が複数個（例えば３個）周方向等配位置に配設される。The bearing housings 14A, B are cylindrical holders 16A, 16
These cylindrical holders 16△,
B is fitted into the inner periphery of the stationary frames 12A and 12B so as to be slidable in the axial direction. Furthermore, on the axial end surfaces of the stationary frames 12A and 12B,
Multiple extrusion phases, for example 3, at equal positions in the circumferential direction! ! Adjustment bolts 17 are provided, and pullback position adjustment bolts 18 are provided at positions that roughly sandwich these extrusion position adjustment bolts 17.
A plurality of (for example, three) are arranged at equal positions in the circumferential direction.
押出（）用位置調整ポル１−１７は、静止枠１２Ａ２Ｂ
の軸方向端面に設けられたわし穴１９に螺合し、円筒状
ボルダ１６Ａ、Ｂの軸り向端面に接触して、軸受ハウジ
ング１４Δ、Ｂを本体枠１１側へ押出し移動さ１！るた
めに用いられる。また、引戻（）用位置調整ボルト１８
は、静止枠１２Δ、Ｂの軸方向端面に設（すられたぎり
穴２０を目通して円筒状ホルダ１６Ａ、Ｂに形成された
ねじ穴２１に螺合し、軸受ハウジング１４Ａ、Ｂを本体
枠１１から引戻して遠避けるために用いられる。Position adjustment port 1-17 for extrusion () is stationary frame 12A2B
The bearing housings 14Δ, B are pushed out and moved toward the main body frame 11 by being screwed into the slots 19 provided in the axial end faces of the cylindrical boulders 16A and 16B, and in contact with the axial end faces of the cylindrical boulders 16A and 16B. It is used to In addition, the position adjustment bolt 18 for pulling back ()
The bearing housings 14A, B are screwed into the screw holes 21 formed in the cylindrical holders 16A, B through the slotted holes 20, and the bearing housings 14A, B are removed from the main body frame 11. Used to pull back and avoid distance.
したが−）で、押出し用位置調整ポル１−１７および引
戻し用位置調整ボルト１８の調整によって軸受ハウジン
グ１４Ａ、Ｂの距離、つまり軸支承部スパンｆが可変と
なる。さらに、引戻し用位置調整ボルト１８の引張りや
押出し用位置調整ボルト１７の押付けによって、軸受ハ
ウジング１４Ａ。However, in (-), the distance between the bearing housings 14A and 14B, that is, the shaft support span f, becomes variable by adjusting the push-out position adjustment pole 1-17 and the pull-back position adjustment bolt 18. Furthermore, the bearing housing 14A is moved by pulling the pull-back position adjustment bolt 18 or pressing the push-out position adjustment bolt 17.
８σ）イ装置を強固に固定できる。8σ) A device can be firmly fixed.
一般に、回転＠１３の剛性には、
「：回転軸材のヤング率
■＝回転軸材の等価断面二次１−メン［・で表わされる
ので、軸支承部スパンｐを変えることにより上記式■に
よって回転＠１３の剛性ｋを変えることができる。さら
に、前述の式■により、回転軸１３のＲ性ｋを変動させ
ることによって回転軸系の危険速痘ωｃｒ＠変えること
ができる。第４図は、軸支承部スパン！８パラメータと
したときの回転軸系の危険速度ωｃｒを示す図である８
、これらのことから、回転軸系の危険速度ωｃｒ’＾め
たい場合には、軸支承部スパンｆを小さくして回転軸１
３のＭ１竹ｋを大きくし、かつ気体少承力を大きくして
軸受ハウジング１４△、Ｂの剛性ｋｂを大と］ハに／ｋ
ｂを小さくするよう調整する。逆に、回転軸系の危険速
位ω。、を低く抑えたい場合には、軸支承部スバンオを
大きくして回転軸１３の剛性ｋを小とし、かつ気体支承
力を小さくして軸受ハウジング１４Ａ、Ｂの剛性ｋｂを
小さくし、ｋ／ｋｂを大きくするよう、Ｊ整１“る。In general, the rigidity of rotation @13 is expressed as: Young's modulus of the rotating shaft member ■=Equivalent cross section of the rotating shaft member quadratic 1-men The rigidity k of the rotating shaft 13 can be changed by .Furthermore, by changing the R property k of the rotating shaft 13, the dangerous speed ωcr@ of the rotating shaft system can be changed according to the above-mentioned formula (2). is a diagram showing the critical speed ωcr of the rotating shaft system when the shaft support span!8 is a parameter.
, From these facts, if you want to reduce the critical speed ωcr'^ of the rotating shaft system, reduce the shaft support span f and reduce the rotational shaft 1.
3, M1 bamboo k is increased, and the gas bearing force is increased to increase the bearing housing 14△, and the rigidity kb of B is increased] to C/k
Adjust to reduce b. Conversely, the critical speed position ω of the rotating shaft system. , if it is desired to keep k/kb low, the shaft bearing part is made large to make the rigidity k of the rotary shaft 13 small, and the gas bearing force is made small to make the stiffness kb of the bearing housings 14A and B small. J adjustment 1" to make it larger.
このように軸受ハウジング１４Ａ、Ｂからの気体噴□□
□吊を変えて気体支承力を変化させ、これに五り軸支承
部（＠受ハウジング１４Ａ、Ｂ）の剛１ｉｋ、を変化さ
せるだけでなく、軸支承部スバンノを変化させて回転軸
１３の剛性ｋを変化させるので、回転軸系の危険速邸ω
、ｒを広範囲に口って変更できる。その結果、回転軸に
の共振現象を確実に回避することができ、任意の回転ｍ
ａに適用可能な汎用性の高いラジアル形気体軸受装置を
提供できる。In this way, gas jets from the bearing housings 14A and 14B
□The suspension is changed to change the gas bearing force, and in addition to this, the stiffness of the five-axis bearing part (@receiving housing 14A, B) is changed, and the shaft bearing part Svanno is changed to increase the rotational shaft 13. Since the stiffness k is changed, the critical speed of the rotating shaft system ω
, r can be changed widely. As a result, it is possible to reliably avoid resonance phenomena on the rotating shaft, and any rotation m
It is possible to provide a highly versatile radial gas bearing device that can be applied to a.
以−Ｆのように、この発明に二係るラジアル形気体軸受
装置によれば、？！数の軸支承部が回転軸の軸方向に移
動して軸支承部スパンを変更しく９るよう構成されたこ
とから、回転軸の剛性も変更できるので、気体支承力を
変えて軸支承部の剛性を変えるだけの場合に比べ回転軸
系の危険速度を広範囲（百って変更でき、回転軸系の共
振現象を確実に回避できる。According to the radial type gas bearing device according to the second aspect of the present invention, as shown in FIG. ! Since several shaft bearings are configured to move in the axial direction of the rotating shaft to change the shaft bearing span, the rigidity of the rotating shaft can also be changed, so the gas bearing force can be changed to change the shaft bearing span. Compared to the case where only the rigidity is changed, the critical speed of the rotating shaft system can be changed over a wide range (more than 100 times), and resonance phenomena in the rotating shaft system can be reliably avoided.
第１図はぐ二の発明に係るラジアル形気体軸受装置の一
実施例がコーニツｉ・どし７で取り付けられた回転機器
を示す衛面図、第２図は第１図の要部で６）りこの発明
の一実施例を示す縦断面図、第３図は回転軸系の危険速
度の変化をに、、’ｋｂをパラメータとして表わした図
、第４図は＠支承部スパンをパラメータとした回転軸系
の危険速度を表わした図、第５図は従来のラジアル形気
体軸受装置を回転ｖｉ器に装着した縦断面図である。Fig. 1 is a diagram showing a rotating device in which an embodiment of the radial gas bearing device according to Haguji's invention is installed in a Konitz I/Doshi 7; Fig. 2 is the main part of Fig. 1; 6) Figure 3 is a longitudinal cross-sectional view showing an embodiment of this invention. Figure 3 is a diagram showing changes in the critical speed of the rotating shaft system using 'kb as a parameter. Figure 4 is a diagram showing @bearing span as a parameter. FIG. 5, which is a diagram showing the critical speed of a rotating shaft system, is a longitudinal cross-sectional view of a conventional radial type gas bearing device installed in a rotating vi device.
１１・・・本体枠、１２Δ、１２Ｂ・・・静止枠、１３
・・・回転軸、１４Ａ、１４Ｂ・・・軸受ハウジング、
１６Ａ、１６Ｂ・・・円筒状ホルダ、１７・・・押出し
２用位胃Ａ整ボルト、１Ｂ・・・引戻し相位置調整ボル
ト１、代理人弁理士 則 近 惠 仏
間 第 了 丸 健11... Main body frame, 12Δ, 12B... Stationary frame, 13
... Rotating shaft, 14A, 14B... Bearing housing,
16A, 16B...Cylindrical holder, 17...Extrusion 2 position stomach A adjustment bolt, 1B...Retraction phase position adjustment bolt 1, Patent attorney Nori Chika Kei Butsuma Dai Ryo Maru Ken
Claims (1)
射される気流層が存在し、この気流層の気体支承力によ
つて上記回転軸が支持されるラジアル形気体軸受装置に
おいて、上記複数の軸支承部が上記回転軸の軸方向に移
動して軸支承部スパンを変更し得るよう構成されたこと
を特徴とするラジアル形気体軸受装置。In a radial type gas bearing device, an air flow layer injected from the shaft support exists between the rotation shaft and the plurality of shaft support parts, and the rotation shaft is supported by the gas bearing force of the air flow layer. A radial type gas bearing device, characterized in that the plurality of shaft support parts are configured to be able to move in the axial direction of the rotating shaft to change the shaft support part span.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP28244988A JPH02129404A (en) | 1988-11-10 | 1988-11-10 | Radial-type gas bearing device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP28244988A JPH02129404A (en) | 1988-11-10 | 1988-11-10 | Radial-type gas bearing device |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH02129404A true JPH02129404A (en) | 1990-05-17 |
Family
ID=17652570
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP28244988A Pending JPH02129404A (en) | 1988-11-10 | 1988-11-10 | Radial-type gas bearing device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH02129404A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2010156155A (en) * | 2008-12-27 | 2010-07-15 | Aero Facility Kk | Heliport and deck material for the same |
-
1988
- 1988-11-10 JP JP28244988A patent/JPH02129404A/en active Pending
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2010156155A (en) * | 2008-12-27 | 2010-07-15 | Aero Facility Kk | Heliport and deck material for the same |
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