JPH09269005A - Damping bearing having damping function - Google Patents
Damping bearing having damping functionInfo
- Publication number
- JPH09269005A JPH09269005A JP8078720A JP7872096A JPH09269005A JP H09269005 A JPH09269005 A JP H09269005A JP 8078720 A JP8078720 A JP 8078720A JP 7872096 A JP7872096 A JP 7872096A JP H09269005 A JPH09269005 A JP H09269005A
- Authority
- JP
- Japan
- Prior art keywords
- bearing
- damping
- bearing support
- supports
- support
- 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
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
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
- F16C19/04—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly
- F16C19/06—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly with a single row or balls
-
- 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
- F16C2360/23—Gas turbine engines
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Sliding-Contact Bearings (AREA)
- Support Of The Bearing (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、ジェットエンジン
におけるガスタービンの軸受支持構造に係わり、更に詳
しくは、減衰機能を備えたダンピング軸受に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a bearing support structure for a gas turbine in a jet engine, and more particularly to a damping bearing having a damping function.
【０００２】[0002]
【従来の技術】ジェットエンジンには、高速回転するガ
スタービンの軸受として、スクイズ・フィルム・ダンパ
を備えた軸受が用いられている。図４はこの軸受の模式
図であり、（Ａ）は部分断面図、（Ｂ）はスクイズ・フ
ィルム・ダンパ部（Ａ部）の拡大図である。2. Description of the Related Art In a jet engine, a bearing having a squeeze film damper is used as a bearing for a gas turbine rotating at a high speed. FIG. 4 is a schematic view of this bearing, (A) is a partial sectional view, and (B) is an enlarged view of a squeeze film damper portion (A portion).
【０００３】図４（Ａ）において、１は回転軸、２は軸
受、３は軸受サポート、４は軸受ハウジングである。軸
受サポート３には、軸受ハウジング４に隙間をもって嵌
合しているダンパ部３ａと、軸受ハウジング４に一端
（図で右端）が固定されたバネ部３ｂが設けられてい
る。バネ部３ｂは、スリットにより間隔を隔てて板バネ
状に形成され、軸受２を半径方向に弾性的に支持してい
る。In FIG. 4A, 1 is a rotary shaft, 2 is a bearing, 3 is a bearing support, and 4 is a bearing housing. The bearing support 3 is provided with a damper portion 3a fitted in the bearing housing 4 with a gap, and a spring portion 3b having one end (right end in the figure) fixed to the bearing housing 4. The spring portion 3b is formed in a leaf spring shape with a slit at an interval, and elastically supports the bearing 2 in the radial direction.
【０００４】図４（Ｂ）に示すように、スクイズ・フィ
ルム・ダンパは、軸受サポート３のダンパ部３ａと軸受
ハウジング４の間に形成され、Ｏリング５等で密封され
た空間に潤滑油を圧送して隙間Ｃに充満させたものであ
る。回転軸１が振動すると、軸受２を支持する隙間Ｃが
変化し、内部の潤滑油により振動を減衰させるようにな
っている。As shown in FIG. 4 (B), the squeeze film damper is formed between the damper portion 3a of the bearing support 3 and the bearing housing 4, and lubricates the space sealed by the O-ring 5 or the like. The gap C is filled by pressure. When the rotary shaft 1 vibrates, the clearance C that supports the bearing 2 changes, and the vibration is damped by the lubricating oil inside.
【０００５】図５は、軸受２に作用する慣性力とスクイ
ズ・フィルム・ダンパによる減衰力との関係図である。
この図において横軸はダンパレイノルズ数Ｒｅ（＝ρω
Ｃ2／μ．．式）であり、ρは油密度、ωは軸の回転
角速度、Ｃはダンパ半径隙間、μは油の粘度である。図
５は、通常の場合には、減衰力Ｆ２が慣性力Ｆ１より十
分大きく、軸振動による慣性力Ｆ１を減衰力Ｆ２で抑制
（減衰）させることができることがわかる。しかし、こ
の図でダンパレイノルズ数Ｒｅが約２．５以上になる
と、慣性力Ｆ１の方が大きくなり、軸振動を十分に減衰
できなくなる。このＲｅ＝２．５は、回転角速度ωが約
３２０Ｈｚに相当し、回転軸１が３２０×６０＝約１万
９０００ｒｐｍ以上で減衰が不十分になることを意味す
る。FIG. 5 is a diagram showing the relationship between the inertial force acting on the bearing 2 and the damping force of the squeeze film damper.
In this figure, the horizontal axis is the damper Reynolds number Re (= ρω
C 2 / μ. . Where ρ is the oil density, ω is the rotational angular velocity of the shaft, C is the damper radius gap, and μ is the oil viscosity. FIG. 5 shows that in a normal case, the damping force F2 is sufficiently larger than the inertial force F1, and the inertial force F1 due to the shaft vibration can be suppressed (damped) by the damping force F2. However, when the damper Reynolds number Re becomes about 2.5 or more in this figure, the inertial force F1 becomes larger and the shaft vibration cannot be sufficiently damped. This Re = 2.5 means that the rotation angular velocity ω corresponds to about 320 Hz, and the rotation shaft 1 has 320 × 60 = about 19,000 rpm or more and the damping is insufficient.
【０００６】[0006]
【発明が解決しようとする課題】上述した従来の減衰機
能を備えたダンピング軸受では、ジェットエンジンの使
用範囲において、減衰力Ｆ２が常に慣性力Ｆ１より大き
く、軸振動による慣性力Ｆ１を減衰力Ｆ２で抑制（減
衰）させることができるように設定する。しかし、実際
に製作すると計算と相違して、使用範囲内で慣性力Ｆ１
の方が大きくなり、軸振動を十分に減衰できなくなるこ
とがある問題点があった。In the conventional damping bearing having the damping function described above, the damping force F2 is always larger than the inertial force F1 in the operating range of the jet engine, and the inertial force F1 due to the shaft vibration is reduced to the damping force F2. Set so that can be suppressed (damped) with. However, when actually manufactured, unlike the calculation, the inertial force F1
However, there is a problem in that the shaft vibration cannot be sufficiently dampened.
【０００７】ダンパによる減衰力Ｆ２は、Ｆ２＝Ｂω
ｄ．．式で示され（ｄは軸の振幅）、減衰係数Ｂは、
（Ｌ／Ｃ）3 の関数ｆで与えられる。ここで、回転角速
度ω、軸の振幅ｄ、及び隙間Ｃは使用条件で決まり自由
に変更できない。従って、上述した問題点が発生する
と、減衰力Ｆを大きくするためにダンパ幅Ｌを大きくす
る必要があるが、ダンパ幅Ｌの増加は、大幅な設計変更
を要すると共に相当の重量増を強いる問題点があった。The damping force F2 by the damper is F2 = Bω
d. . Equation (d is the amplitude of the axis), the damping coefficient B is
It is given by the function f of (L / C) 3 . Here, the rotation angular velocity ω, the shaft amplitude d, and the gap C are determined by the usage conditions and cannot be freely changed. Therefore, when the above-mentioned problems occur, it is necessary to increase the damper width L in order to increase the damping force F. However, an increase in the damper width L requires a large design change and causes a considerable weight increase. There was a point.
【０００８】本発明はかかる問題点を解決するために創
案されたものである。すなわち、本発明の目的は、設計
変更や重量増加なしに、減衰力を調整できる減衰機能を
備えたダンピング軸受を提供することにある。The present invention has been made to solve such a problem. That is, an object of the present invention is to provide a damping bearing having a damping function capable of adjusting the damping force without changing the design or increasing the weight.
【０００９】[0009]
【課題を解決するための手段】本発明によれば、回転軸
を支持するラジアル軸受と、ラジアル軸受を支持する軸
受サポートと、軸受サポートを支持する軸受ハウジング
とを備え、軸受サポートは、軸受ハウジングにより半径
方向に振動可能に弾性的に支持され、かつその間に油を
密封させて振動を減衰させるようになったダンピング軸
受において、軸受サポートに摩擦部材を軸方向に押付け
るスラストダンパ装置を更に備えた、ことを特徴とする
減衰機能を備えたダンピング軸受が提供される。According to the present invention, there is provided a radial bearing that supports a rotating shaft, a bearing support that supports the radial bearing, and a bearing housing that supports the bearing support, and the bearing support is a bearing housing. In a damping bearing that is elastically supported so as to be able to vibrate in the radial direction by means of which oil is hermetically sealed to damp the vibration, a thrust damper device that presses a friction member axially on the bearing support is further provided. A damping bearing having a damping function is also provided.
【００１０】本発明の好ましい実施形態によれば、前記
軸受サポートは、回転軸に直交する垂直面を有し、前記
軸受ハウジングは、軸受サポートの垂直面に面する側が
開口した空洞を有し、前記スラストダンパ装置は、軸受
ハウジングの空洞内に軸方向に遊動可能に挿入された摩
擦部材と、該摩擦部材を軸受サポートの垂直面に押付け
る付勢部材と、からなる。According to a preferred embodiment of the present invention, the bearing support has a vertical surface orthogonal to the rotation axis, and the bearing housing has a cavity whose side facing the vertical surface of the bearing support is open. The thrust damper device includes a friction member axially movably inserted in the cavity of the bearing housing, and a biasing member for pressing the friction member against the vertical surface of the bearing support.
【００１１】上記本発明の構成によれば、軸受サポート
に摩擦部材を軸方向に押付けるスラストダンパ装置を備
えているので、このスラストダンパ装置により、減衰力
を付加し減衰力を高めることができる。また、このスラ
ストダンパ装置を、軸受ハウジングの空洞内に軸方向に
遊動可能に挿入された摩擦部材と、該摩擦部材を軸受サ
ポートの垂直面に押付ける付勢部材と、から構成するこ
とにより、摩擦係数の異なる摩擦部材、或いはバネ定数
の異なる付勢部材に交換することにより、設計変更や重
量増加なしに、減衰力をある程度自由に調整することが
できる。According to the above-mentioned structure of the present invention, since the bearing support is provided with the thrust damper device for pushing the friction member in the axial direction, the damping force can be added and the damping force can be increased by this thrust damper device. . Further, by configuring the thrust damper device by a friction member axially movably inserted in the cavity of the bearing housing, and a biasing member for pressing the friction member against the vertical surface of the bearing support, By replacing the friction member with a different friction coefficient or the urging member with a different spring constant, the damping force can be adjusted to some extent freely without changing the design or increasing the weight.
【００１２】[0012]
【発明の実施の形態】以下、本発明の好ましい実施形態
を図面を参照して説明する。なお、各図において共通す
る部分には同一の符号を付して使用する。図１は、本発
明による減衰機能を備えたダンピング軸受の部分断面図
である。この図において、本発明のダンピング軸受１０
は、回転軸１を支持するラジアル軸受２と、ラジアル軸
受２を支持する軸受サポート１３と、軸受サポート１３
を支持する軸受ハウジング１４とを備えている。また、
軸受サポート１３は、軸受ハウジング１４により半径方
向に振動可能に弾性的に支持され、かつその間に油を密
封させてスクイズ・フィルム・ダンパを構成し振動を減
衰させるようになっている。すなわち、軸受サポート１
３には、軸受ハウジング１４に隙間をもって嵌合してい
るダンパ部１３ａと、軸受ハウジング１４に一端（図で
右端）が固定されたバネ部１３ｂが設けられている。こ
のバネ部１３ｂは、スリットにより間隔を隔てて板バネ
状に形成され、軸受２を半径方向に弾性的に支持してい
る。かかる構成は、従来のスクイズ・フィルム・ダンパ
（図４参照）と同様である。DESCRIPTION OF THE PREFERRED EMBODIMENTS Preferred embodiments of the present invention will be described below with reference to the drawings. In the drawings, common parts are denoted by the same reference numerals. FIG. 1 is a partial sectional view of a damping bearing having a damping function according to the present invention. In this figure, the damping bearing 10 of the present invention is shown.
Is a radial bearing 2 that supports the rotating shaft 1, a bearing support 13 that supports the radial bearing 2, and a bearing support 13
And a bearing housing 14 for supporting. Also,
The bearing support 13 is elastically supported by a bearing housing 14 so as to be capable of vibrating in the radial direction, and oil is sealed between them to form a squeeze film damper to damp vibration. That is, bearing support 1
3, a damper portion 13a fitted into the bearing housing 14 with a gap and a spring portion 13b having one end (right end in the figure) fixed to the bearing housing 14 are provided. The spring portion 13b is formed in the shape of a leaf spring at intervals with a slit, and elastically supports the bearing 2 in the radial direction. Such a structure is similar to that of the conventional squeeze film damper (see FIG. 4).
【００１３】なお、本発明は、この構成に限定されず、
スクイズ・フィルム・ダンパを備えた別の周知の軸受に
も適用することができる。The present invention is not limited to this configuration,
It can also be applied to other known bearings with squeeze film dampers.
【００１４】図２は、図１のＢ部の部分拡大図である。
図１及び図２に示すように、本発明のダンピング軸受１
０は、更に、軸受サポート１３に摩擦部材１６を軸方向
に押付けるスラストダンパ装置１８を備えている。図２
に示すように、軸受サポート１３は、回転軸１に直交す
る垂直面１３ｃを有する。また、軸受ハウジング１４
は、軸受サポート１３の垂直面１３ｃに面する側が開口
した空洞１４ａを有する。更に、この図において、スラ
ストダンパ装置１８は、軸受ハウジング１４の空洞１４
ａ内に軸方向に遊動可能に挿入された摩擦部材１６と、
摩擦部材１６を軸受サポート１３の垂直面１３ｃに押付
ける付勢部材１７とからなり、摩擦部材１６を押付け力
Ｎで押し付けている。FIG. 2 is a partially enlarged view of portion B in FIG.
As shown in FIGS. 1 and 2, the damping bearing 1 of the present invention.
0 further includes a thrust damper device 18 for pressing the friction member 16 against the bearing support 13 in the axial direction. FIG.
As shown in, the bearing support 13 has a vertical surface 13c orthogonal to the rotation axis 1. In addition, the bearing housing 14
Has a cavity 14a whose side facing the vertical surface 13c of the bearing support 13 is open. Further, in this figure, the thrust damper device 18 is shown as the cavity 14 of the bearing housing 14.
a friction member 16 inserted in a so as to be axially movable,
The friction member 16 includes a biasing member 17 that presses the friction member 16 against the vertical surface 13c of the bearing support 13, and the friction member 16 is pressed by a pressing force N.
【００１５】空洞１４ａは、周方向に間隔を隔てて複数
設けるのがよい。また、空洞１４ａを円筒形に形成し、
この内部に円筒形の摩擦部材１６を遊動するように挿入
するのがよい。また、同様に空洞１４ａをドーナツ状に
一体に形成し、摩擦部材１６もドーナツ状に一体に形成
してもよい。A plurality of cavities 14a are preferably provided at intervals in the circumferential direction. In addition, the cavity 14a is formed into a cylindrical shape,
It is preferable to insert a cylindrical friction member 16 into the inside so as to float. Similarly, the cavity 14a may be integrally formed in a donut shape, and the friction member 16 may be integrally formed in a donut shape.
【００１６】なお、スラストダンパ装置１８の構成は、
図１，図２に示す構成に限定されず、例えば、軸受サポ
ート１３に両面が垂直なディスク状部分を設け、この部
分を１対の摩擦部材で挟さみ込むように構成してもよ
い。The structure of the thrust damper device 18 is as follows.
The configuration is not limited to the configuration shown in FIGS. 1 and 2, and for example, the bearing support 13 may be provided with a disk-shaped portion whose both surfaces are vertical, and this portion may be sandwiched by a pair of friction members.
【００１７】図３は、図１及び図２に示した本発明のダ
ンピング軸受１０のモデル図である。この図において、
ｍは軸受サポート１３の質量、Ｆｃｏｓωｔは回転軸の
振動による慣性力、ｋｄはバネ定数、ｃはスクイズフィ
ルム減衰係数、Ｎは押付け力、ｋはサポートバネ定数、
μは摩擦係数である。図３に示す２つの式は、このモデ
ルにおける基礎方程式であり、（１）は振動変位が微小
でダンパーがスリップしていない場合、（２）は振動変
位が大きくダンパーがスリップしている場合を示してい
る。この２つの式から、本発明のスラストダンパ装置１
８を設けることにより、慣性力Ｆｃｏｓωｔを低減させ
ることができることがわかる。FIG. 3 is a model diagram of the damping bearing 10 of the present invention shown in FIGS. In this figure,
m is the mass of the bearing support 13, Fcosωt is the inertial force due to the vibration of the rotating shaft, kd is the spring constant, c is the squeeze film damping coefficient, N is the pressing force, k is the support spring constant,
μ is a coefficient of friction. The two equations shown in FIG. 3 are the basic equations in this model. (1) shows the case where the vibration displacement is minute and the damper does not slip, and (2) shows the case where the vibration displacement is large and the damper slips. Shows. From these two equations, the thrust damper device 1 of the present invention
It can be seen that the inertia force Fcosωt can be reduced by providing No. 8.
【００１８】なお、本発明は上述した実施形態に限定さ
れず、本発明の要旨を逸脱しない範囲で種々変更できる
ことは勿論である。It should be noted that the present invention is not limited to the above-described embodiment, and it is needless to say that various changes can be made without departing from the gist of the present invention.
【００１９】[0019]
【発明の効果】上述したように本発明の構成によれば、
軸受サポート１３に摩擦部材１６を軸方向に押付けるス
ラストダンパ装置１８を備えることにより、減衰力を付
加して減衰力を高めることができる。また、このスラス
トダンパ装置１８を、軸受ハウジング１４の空洞１４ａ
内に軸方向に遊動可能に挿入された摩擦部材１６と、摩
擦部材１６を軸受サポート１３の垂直面１３ｃに押付け
る付勢部材１７とから構成することにより、摩擦係数μ
の異なる摩擦部材１６、或いはバネ定数ｋｄの異なる付
勢部材１７に交換することにより、設計変更や重量増加
なしに、減衰力をある程度自由に調整することができ
る。As described above, according to the configuration of the present invention,
By providing the bearing support 13 with the thrust damper device 18 that presses the friction member 16 in the axial direction, a damping force can be added and the damping force can be increased. In addition, the thrust damper device 18 is installed in the cavity 14 a of the bearing housing 14.
The friction member 16 is inserted in the shaft so as to be free to move in the axial direction, and the biasing member 17 that presses the friction member 16 against the vertical surface 13c of the bearing support 13 is used.
By changing the friction member 16 having a different value or the biasing member 17 having a different spring constant kd, the damping force can be adjusted to some extent without changing the design or increasing the weight.
【００２０】従って、本発明の減衰機能を備えたダンピ
ング軸受は、設計変更や重量増加なしに、減衰力を調整
できる、等の優れた効果を有する。Therefore, the damping bearing having the damping function of the present invention has an excellent effect that the damping force can be adjusted without changing the design or increasing the weight.
【図１】本発明による減衰機能を備えたダンピング軸受
の部分断面図である。FIG. 1 is a partial cross-sectional view of a damping bearing having a damping function according to the present invention.
【図２】図１の部分拡大図である。FIG. 2 is a partially enlarged view of FIG.
【図３】本発明の減衰機能を備えたダンピング軸受のモ
デル図である。FIG. 3 is a model diagram of a damping bearing having a damping function according to the present invention.
【図４】スクイズ・フィルム・ダンパを備えた従来のダ
ンピング軸受の模式図である。FIG. 4 is a schematic view of a conventional damping bearing provided with a squeeze film damper.
【図５】軸受に作用する慣性力とスクイズ・フィルム・
ダンパによる減衰力との関係図である。[Fig. 5] Inertial force acting on the bearing and squeeze film
It is a relationship diagram with the damping force by a damper.
１ 回転軸 ２ 軸受 ３ 軸受サポート ３ａ ダンパ部 ３ｂ バネ部 ４ 軸受ハウジング ５ Ｏリング １０ ダンピング軸受 １３ 軸受サポート １３ａ ダンパ部 １３ｂ バネ部 １３ｃ 垂直面 １４ 軸受ハウジング １４ａ 空洞 １６ 摩擦部材 １７ 付勢部材 １８ スラストダンパ装置 1 rotating shaft 2 bearing 3 bearing support 3a damper part 3b spring part 4 bearing housing 5 O-ring 10 damping bearing 13 bearing support 13a damper part 13b spring part 13c vertical surface 14 bearing housing 14a cavity 16 friction member 17 biasing member 18 thrust damper apparatus
Claims (2)
アル軸受を支持する軸受サポートと、軸受サポートを支
持する軸受ハウジングとを備え、軸受サポートは、軸受
ハウジングにより半径方向に振動可能に弾性的に支持さ
れ、かつその間に油を密封させて振動を減衰させるよう
になったダンピング軸受において、 軸受サポートに摩擦部材を軸方向に押付けるスラストダ
ンパ装置を更に備えた、ことを特徴とする減衰機能を備
えたダンピング軸受。1. A radial bearing that supports a rotating shaft, a bearing support that supports the radial bearing, and a bearing housing that supports the bearing support, and the bearing support is elastically elastically vibrated in a radial direction by the bearing housing. A damping bearing, which is supported and is configured to seal oil between them to damp vibrations, is further provided with a thrust damper device that axially presses a friction member against a bearing support. Damping bearing equipped.
垂直面を有し、前記軸受ハウジングは、軸受サポートの
垂直面に面する側が開口した空洞を有し、前記スラスト
ダンパ装置は、軸受ハウジングの空洞内に軸方向に遊動
可能に挿入された摩擦部材と、該摩擦部材を軸受サポー
トの垂直面に押付ける付勢部材と、からなる、ことを特
徴とする請求項１に記載の減衰機能を備えたダンピング
軸受。2. The bearing support has a vertical surface orthogonal to the rotation axis, the bearing housing has a cavity whose side facing the vertical surface of the bearing support is open, and the thrust damper device has a bearing housing. 2. The damping function according to claim 1, further comprising: a friction member axially movably inserted in the cavity of the above, and a biasing member for pressing the friction member against a vertical surface of the bearing support. Damping bearing with.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP8078720A JPH09269005A (en) | 1996-04-01 | 1996-04-01 | Damping bearing having damping function |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP8078720A JPH09269005A (en) | 1996-04-01 | 1996-04-01 | Damping bearing having damping function |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH09269005A true JPH09269005A (en) | 1997-10-14 |
Family
ID=13669724
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP8078720A Pending JPH09269005A (en) | 1996-04-01 | 1996-04-01 | Damping bearing having damping function |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH09269005A (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2008007697A1 (en) * | 2006-07-12 | 2008-01-17 | Mitsubishi Heavy Industries, Ltd. | Bearing support structure and gas turbine |
| GB2444935A (en) * | 2006-12-06 | 2008-06-25 | Rolls Royce Plc | Accommodating radial excursions of a turbofan gas turbine engine shaft |
| CN105339115A (en) * | 2013-06-28 | 2016-02-17 | 株式会社牧野铣床制作所 | Main spindle device for machine tool and machine tool |
| US9878408B2 (en) | 2013-09-13 | 2018-01-30 | Makino Milling Machine Co., Ltd. | Machine tool |
| US10160075B2 (en) | 2013-06-28 | 2018-12-25 | Makino Milling Machine Co., Ltd. | Main spindle device for machine tool and machine tool |
| US10400630B2 (en) * | 2017-08-22 | 2019-09-03 | General Electric Company | Squeeze film damper for a gas turbine engine |
-
1996
- 1996-04-01 JP JP8078720A patent/JPH09269005A/en active Pending
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2008007697A1 (en) * | 2006-07-12 | 2008-01-17 | Mitsubishi Heavy Industries, Ltd. | Bearing support structure and gas turbine |
| US8128339B2 (en) | 2006-07-12 | 2012-03-06 | Mitsubishi Heavy Industries, Ltd. | Bearing support structure and gas turbine |
| GB2444935A (en) * | 2006-12-06 | 2008-06-25 | Rolls Royce Plc | Accommodating radial excursions of a turbofan gas turbine engine shaft |
| US8430622B2 (en) | 2006-12-06 | 2013-04-30 | Rolls-Royce Plc | Turbofan gas turbine engine |
| CN105339115A (en) * | 2013-06-28 | 2016-02-17 | 株式会社牧野铣床制作所 | Main spindle device for machine tool and machine tool |
| EP3015201A4 (en) * | 2013-06-28 | 2017-03-08 | Makino Milling Machine Co., Ltd. | Main spindle device for machine tool and machine tool |
| US10160075B2 (en) | 2013-06-28 | 2018-12-25 | Makino Milling Machine Co., Ltd. | Main spindle device for machine tool and machine tool |
| US9878408B2 (en) | 2013-09-13 | 2018-01-30 | Makino Milling Machine Co., Ltd. | Machine tool |
| US10400630B2 (en) * | 2017-08-22 | 2019-09-03 | General Electric Company | Squeeze film damper for a gas turbine engine |
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