JPH109268A - Bearing structure of high speed rotational shaft - Google Patents
Bearing structure of high speed rotational shaftInfo
- Publication number
- JPH109268A JPH109268A JP8161952A JP16195296A JPH109268A JP H109268 A JPH109268 A JP H109268A JP 8161952 A JP8161952 A JP 8161952A JP 16195296 A JP16195296 A JP 16195296A JP H109268 A JPH109268 A JP H109268A
- Authority
- JP
- Japan
- Prior art keywords
- oil film
- peripheral surface
- rotating shaft
- bearing
- housing
- 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
- 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
- F16C25/083—Ball or roller bearings self-adjusting with resilient means acting axially on a race ring 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
- 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
- F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
- F16C19/16—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls
- F16C19/163—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls with angular contact
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Rolling Contact Bearings (AREA)
- Support Of The Bearing (AREA)
- Magnetic Bearings And Hydrostatic Bearings (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、高速回転軸の軸受
構造の改良に関するものである。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an improvement in a bearing structure for a high-speed rotating shaft.
【０００２】[0002]
【従来の技術】例えばガスタービンやターボチャージャ
に用いられる回転軸は、これに連結されるコンプレッサ
インペラやタービンロータと共に高速回転する。2. Description of the Related Art For example, a rotating shaft used in a gas turbine or a turbocharger rotates at high speed together with a compressor impeller or a turbine rotor connected thereto.
【０００３】こうした高速回転軸の軸受構造として、回
転軸を転がり軸受により支承することにより、フリクシ
ョンを低減するとともに、転がり軸受を油膜緩衝層によ
りハウジング内周面に対して浮動支持することにより、
転がり軸受の振動を吸収するものがある(実開昭６３−
３６６３０号公報、参照)。As a bearing structure of such a high-speed rotating shaft, the rotating shaft is supported by a rolling bearing to reduce friction, and the rolling bearing is supported by floating on an inner peripheral surface of the housing by an oil film buffer layer.
Some of them absorb the vibration of rolling bearings.
36630).
【０００４】[0004]
【発明が解決しようとする課題】ところで、回転軸が各
転がり軸受に片持ち支持されるオーバーハング部を有
し、オーバーハング部にコンプレッサインペラやタービ
ンロータ等が結合される構造の場合、回転軸の曲げ変形
が生じ、回転軸の先端が円弧を描いて振れまわるみそす
り運動が発生する可能性がある。By the way, in the case where the rotating shaft has an overhang portion which is cantilevered by each rolling bearing, and a compressor impeller, a turbine rotor or the like is connected to the overhang portion, the rotating shaft is Bending deformation may occur, and a razor motion in which the tip of the rotating shaft fluctuates in an arc may occur.
【０００５】しかしながら、回転軸のオーバーハング部
から遠い先端側の転がり軸受において、ハウジング内周
面と転がり軸受間のダンパ間隙が軸方向に延びた従来構
造では、上記回転軸のみそすり運動が発生すると、ダン
パ間隙に形成される油膜緩衝層の端部で油膜が切れて、
ダンパ間隙を画成するハウジング内周面に対して軸受側
外周面の両端部が接触し、異常振動や異音が発生する可
能性がある。[0005] However, in the conventional structure in which the damper gap between the inner circumferential surface of the housing and the rolling bearing extends in the axial direction in the rolling bearing on the distal end side far from the overhang portion of the rotating shaft, only the rotating shaft generates a sliding motion. Then, the oil film is cut at the end of the oil film buffer layer formed in the damper gap,
Both ends of the bearing-side outer peripheral surface come into contact with the inner peripheral surface of the housing that defines the damper gap, and abnormal vibration and abnormal noise may occur.
【０００６】本発明は上記の問題点を鑑みてなされたも
のであり、高速回転軸の軸受構造において、回転軸のみ
そすり運動による異常振動や異音等の発生を防止するこ
とを目的とする。SUMMARY OF THE INVENTION The present invention has been made in consideration of the above problems, and has as its object to prevent occurrence of abnormal vibration, abnormal noise, and the like due to a sliding motion of only a rotating shaft in a bearing structure of a high-speed rotating shaft. .
【０００７】[0007]
【課題を解決するための手段】請求項１に記載の高速回
転軸の軸受構造は、複数の転がり軸受に回転可能に支持
される回転軸を備え、回転軸は各転がり軸受に片持ち支
持されるオーバーハング部を有し、各転がり軸受けを支
持するハウジング内周面を備え、各転がり軸受の軸受外
周面とハウジング内周面の間に油膜緩衝層を形成するダ
ンパ隙間を画成し、ダンパ隙間に潤滑油を圧送する給油
通路を備える高速回転軸の軸受構造において、前記オー
バーハング部から最も離れた先端側に設けられる軸受外
周面にダンパ間隙を画成する外側油膜面を回転軸の径方
向に環状に突出させ、ダンパ間隙から連続してその間隙
を拡大する逃げ空間を備える。According to a first aspect of the present invention, there is provided a bearing structure for a high-speed rotating shaft, comprising a rotating shaft rotatably supported by a plurality of rolling bearings, the rotating shaft being cantilevered by each rolling bearing. An inner peripheral surface of a housing that supports each rolling bearing, and defines a damper gap that forms an oil film buffer layer between the outer peripheral surface of the bearing and the inner peripheral surface of the housing. In a bearing structure of a high-speed rotating shaft provided with an oil supply passage for feeding lubricating oil into the gap, the outer oil film surface defining a damper gap is formed on the outer peripheral surface of the bearing provided at the tip end furthest away from the overhang portion. A relief space is provided which is annularly protruded in the direction and extends continuously from the damper gap.
【０００８】請求項２に記載の高速回転軸の軸受構造
は、請求項１に記載の発明において、前記外側油膜面に
環状溝を形成し、環状溝を給油通路の出口に対峙するよ
うに配置する。According to a second aspect of the present invention, in the bearing structure for a high-speed rotating shaft, an annular groove is formed on the outer oil film surface, and the annular groove is disposed so as to face an outlet of the oil supply passage. I do.
【０００９】請求項３に記載の高速回転軸の軸受構造
は、請求項２に記載の発明において、前記環状溝とハウ
ジング内周面の間に複数の弾性球を介装し、各弾性球を
外側油膜面の中央に配置する。According to a third aspect of the present invention, in the bearing structure for a high-speed rotating shaft, a plurality of elastic spheres are interposed between the annular groove and the inner peripheral surface of the housing. It is located at the center of the outer oil film surface.
【００１０】請求項４に記載の高速回転軸の軸受構造
は、請求項１または２に記載の発明において、前記外側
油膜面に環状溝を挟んで外径が相違する大径外側油膜面
部と小径外側油膜面部を形成し、大径外側油膜面部を小
径外側油膜面部よりハウジング内周面の奥部に対峙する
ように配置する。According to a fourth aspect of the present invention, there is provided a bearing structure for a high-speed rotating shaft according to the first or second aspect, wherein the outer oil film surface has a large-diameter outer oil film surface portion having a different outer diameter with an annular groove interposed therebetween and a small diameter. An outer oil film surface portion is formed, and the large-diameter outer oil film surface portion is disposed so as to face a deeper portion of the inner circumferential surface of the housing than the small-diameter outer oil film surface portion.
【００１１】請求項５に記載の高速回転軸の軸受構造
は、請求項１から４のいずれか一つに記載の発明におい
て、前記転がり軸受のアウターレース外周面とハウジン
グ内周面の間に円筒状をしたリテーナを介装し、リテー
ナの軸受外周面にダンパ間隙を画成する外側油膜面を回
転軸の径方向に環状に突出させる。According to a fifth aspect of the present invention, in the bearing structure for a high-speed rotating shaft according to any one of the first to fourth aspects, the cylindrical structure is provided between the outer peripheral surface of the outer race of the rolling bearing and the inner peripheral surface of the housing. An outer oil film surface defining a damper gap on the outer peripheral surface of the bearing of the retainer is annularly projected in the radial direction of the rotating shaft.
【００１２】請求項６に記載の高速回転軸の軸受構造
は、請求項１から５のいずれか一つに記載の発明におい
て、前記転がり軸受のアウターレース外周面とハウジン
グ内周面の間に円筒状をしたリテーナを介装し、リテー
ナの軸受外周面と軸受内周面にダンパ間隙を画成する油
膜面をそれぞれ回転軸の径方向に環状に突出させ、各ダ
ンパ間隙から連続してその間隙を拡大する逃げ空間を備
え、内外の各油膜面に環状溝を形成し、内外の各環状溝
を連通する通孔を形成する。According to a sixth aspect of the present invention, in the bearing structure for a high-speed rotating shaft according to any one of the first to fifth aspects, the cylindrical structure is provided between an outer peripheral surface of the outer race of the rolling bearing and an inner peripheral surface of the housing. The oil film surfaces defining the damper gaps on the bearing outer circumferential surface and the bearing inner circumferential surface of the retainer are annularly projected in the radial direction of the rotating shaft, and the gaps are continuously formed from the respective damper gaps. And an annular groove is formed on each of the inner and outer oil film surfaces, and a through hole communicating with each of the inner and outer annular grooves is formed.
【００１３】請求項７に記載の高速回転軸の軸受構造
は、請求項６に記載の発明において、前記内外の環状溝
とハウジング内周面またはアウターレース外周面の間に
複数の弾性球を介装し、各弾性球を内外の各油膜面の中
央に配置する。According to a seventh aspect of the present invention, in the bearing structure for a high-speed rotating shaft, a plurality of elastic spheres are interposed between the inner and outer annular grooves and the inner peripheral surface of the housing or the outer peripheral surface of the outer race. And the respective elastic balls are arranged at the center of the inner and outer oil film surfaces.
【００１４】[0014]
【作用】請求項１に記載の高速回転軸の軸受構造におい
て、回転軸を各転がり軸受により支承することにより、
フリクションを低減する。各転がり軸受を油膜緩衝層に
よりハウジング内周面に対して浮動支持することによ
り、転がり軸受特有の振動を吸収する。In the bearing structure for a high-speed rotating shaft according to claim 1, the rotating shaft is supported by each rolling bearing,
Reduce friction. Each of the rolling bearings is supported by the oil film buffer layer in a floating manner with respect to the inner peripheral surface of the housing, thereby absorbing vibration inherent to the rolling bearings.
【００１５】ところで、運転時に回転軸は各転がり軸受
を介して片持ち支持されるオーバーハング部の曲げ変形
が生じ、回転軸の先端が円弧を描いて振れまわるみそす
り運動が発生する可能性がある。このみそすり運動が発
生すると、先端側の転がり軸受において、ハウジング内
周面に対して軸受外周面が傾斜し、両者間に画成される
ダンパ間隙の断面が楔状になる。By the way, during operation, the overshaft portion of the rotating shaft that is cantilevered via each rolling bearing may be bent and deformed, and the tip of the rotating shaft may draw a circular arc and oscillate. is there. When the rubbing motion is generated, the outer peripheral surface of the bearing is inclined relative to the inner peripheral surface of the housing in the rolling bearing on the distal end side, and the cross section of the damper gap defined between the two becomes wedge-shaped.
【００１６】本発明はこれに対処して、先端側の転がり
軸受において、リテーナの軸受外周面からダンパ間隙を
画成する外側油膜面を環状に突出させて、ダンパ間隙か
ら連続する間隙を拡大する逃げ空間が画成される構造の
ため、回転軸のみそすり運動が発生しても、ダンパ間隙
の端部で油膜緩衝層の油膜が切れてハウジング内周面に
軸受外周面の両端部が接触することを防止できる。この
結果、回転軸のみそすり運動が発生しても、転がり軸受
の近傍から異常振動や異音が発生することを防止でき
る。According to the present invention, in response to this, in the rolling bearing on the tip end side, the outer oil film surface defining the damper gap is annularly projected from the bearing outer peripheral surface of the retainer to enlarge the gap continuous from the damper gap. Due to the structure that the clearance space is defined, even if the rotating shaft only rubs, the oil film of the oil film buffer layer breaks at the end of the damper gap, and both ends of the bearing outer peripheral surface contact the housing inner peripheral surface. Can be prevented. As a result, it is possible to prevent abnormal vibration and abnormal noise from being generated near the rolling bearings even when the rotating shaft only performs the rubbing motion.
【００１７】請求項２に記載の高速回転軸の軸受構造に
おいて、給油通路を通ってダンパ間隙に供給された潤滑
油は、外側油膜面に刻まれた環状溝を介してダンパ間隙
の全周にわたるように導かれ、回転軸のみそすり運動が
発生しても、ダンパ間隙の端部で油膜緩衝層の油膜が切
れることが防止される。In the bearing structure for a high-speed rotating shaft according to the second aspect, the lubricating oil supplied to the damper gap through the oil supply passage extends over the entire circumference of the damper gap via the annular groove cut in the outer oil film surface. Thus, even if the rotary shaft is rubbed, the oil film of the oil film buffer layer is prevented from being broken at the end of the damper gap.
【００１８】請求項３に記載の高速回転軸の軸受構造に
おいて、軸受外周面はハウジング内周面に対して油膜緩
衝層を介して浮動支持されるとともに、弾性球を介して
弾性支持されることにより、転がり軸受に生じる振動が
吸収される。In the bearing structure for a high-speed rotating shaft according to claim 3, the outer peripheral surface of the bearing is floatingly supported on the inner peripheral surface of the housing via an oil film buffer layer and is elastically supported via an elastic ball. Thereby, the vibration generated in the rolling bearing is absorbed.
【００１９】すなわち、ダンパ間隙を画成する外側油膜
面の軸方向の幅が短縮されるのに伴って油膜緩衝層によ
る負荷能力が低下する分を、弾性球の弾性復元力が補
い、径方向の振動を減衰する。That is, as the axial width of the outer oil film surface that defines the damper gap is reduced, the load capacity of the oil film buffer layer is reduced, and the elastic restoring force of the elastic sphere compensates for the decrease in the load capacity of the elastic sphere. Damping the vibration of
【００２０】弾性球は外側油膜面の中央に配置されてい
るため、回転軸のみそすり運動が発生しても、弾性球の
弾性変形量を適正に維持し、径方向の振動を減衰する。Since the elastic sphere is arranged at the center of the outer oil film surface, even if the rotary shaft is rubbed, the amount of elastic deformation of the elastic sphere is properly maintained and the radial vibration is attenuated.
【００２１】請求項４に記載の高速回転軸の軸受構造に
おいて、ダンパ間隙は大径外側油膜面部によって画成さ
れる間隙は小径外側油膜面部よって画成される間隙より
小さいため、大径外側油膜面部を経てハウジングの内側
に流入する潤滑油量を抑えられ、大部分の潤滑油が小径
外側油膜面部を経てハウジングの外側に流出する。この
結果、ハウジングの内部に形成される戻り側油通路の断
面積を小さくして、装置のコンパクト化がはかれる。In the bearing structure for a high-speed rotating shaft according to claim 4, the gap defined by the large-diameter outer oil film surface portion is smaller than the gap defined by the small-diameter outer oil film surface portion. The amount of lubricating oil flowing into the inside of the housing through the surface portion is suppressed, and most of the lubricating oil flows out of the housing through the small-diameter outer oil film surface portion. As a result, the cross-sectional area of the return-side oil passage formed inside the housing is reduced, and the device is made compact.
【００２２】請求項５に記載の高速回転軸の軸受構造に
おいて、潤滑油が給油通路を通ってダンパ間隙に供給さ
れることにより、リテーナはハウジング内周面に対して
油膜緩衝層を介して浮動支持される。In the bearing structure for a high-speed rotating shaft according to the fifth aspect, since the lubricating oil is supplied to the damper gap through the oil supply passage, the retainer floats on the inner peripheral surface of the housing via the oil film buffer layer. Supported.
【００２３】請求項６に記載の高速回転軸の軸受構造に
おいて、給油通路を通ってダンパ間隙に供給された潤滑
油は、外側油膜面に刻まれた環状溝を介してダンパ間隙
の全周にわたるように導かれ、回転軸のみそすり運動が
発生しても、ダンパ間隙の端部で油膜緩衝層の油膜が切
れることが防止される。In the bearing structure for a high-speed rotating shaft according to the present invention, the lubricating oil supplied to the damper gap through the oil supply passage extends over the entire circumference of the damper gap via the annular groove formed on the outer oil film surface. Thus, even if the rotary shaft is rubbed, the oil film of the oil film buffer layer is prevented from being broken at the end of the damper gap.
【００２４】環状溝に導かれる潤滑油の一部が各通孔を
通って内側ダンパ間隙に供給されることにより、アウタ
ーレース外周面はリテーナに対して油膜緩衝層を介して
浮動支持される。When a part of the lubricating oil guided to the annular groove is supplied to the inner damper gap through each through hole, the outer race outer peripheral surface is floatingly supported by the retainer via the oil film buffer layer.
【００２５】通孔を通って内側ダンパ間隙に供給された
潤滑油は、内側油膜面に刻まれた内側環状溝を介して内
側ダンパ間隙の全周にわたるように導かれ、回転軸のみ
そすり運動が発生しても、内側ダンパ間隙の端部で油膜
緩衝層の油膜が切れることが防止される。The lubricating oil supplied to the inner damper gap through the through hole is guided over the entire circumference of the inner damper gap via the inner annular groove formed in the inner oil film surface, and only the rotary shaft is slid. This prevents the oil film of the oil film buffer layer from breaking at the end of the inner damper gap.
【００２６】こうして転がり軸受はリテーナの内外周に
形成される二重の油膜緩衝層を介して浮動支持されるこ
とにより、転がり軸受に生じる振動が有効に吸収される
とともに、回転軸のみそすり運動が大きくなっても、転
がり軸受の近傍から異常振動や異音が発生することを防
止できる。In this way, the rolling bearing is floated and supported through the double oil film buffer layers formed on the inner and outer circumferences of the retainer, so that the vibration generated in the rolling bearing is effectively absorbed, and only the rotating shaft is slid. , The occurrence of abnormal vibration or abnormal noise from the vicinity of the rolling bearing can be prevented.
【００２７】請求項７に記載の高速回転軸の軸受構造に
おいて、転がり軸受はリテーナの内外周に形成される二
重の油膜緩衝層を介して浮動支持されるとともに、リテ
ーナの内外周に介装される各弾性球を介して弾性支持さ
れることにより、転がり軸受に生じる振動が有効に吸収
される。[0027] In the bearing structure for a high-speed rotating shaft according to claim 7, the rolling bearing is floatingly supported via a double oil film buffer layer formed on the inner and outer circumferences of the retainer, and is interposed on the inner and outer circumferences of the retainer. The vibration generated in the rolling bearing is effectively absorbed by being elastically supported through the respective elastic spheres.
【００２８】各弾性球は外側油膜面の中央に配置されて
いるため、運転時に回転軸の先端が円弧を描いて振れま
わるみそすり運動が発生しても、各弾性球の弾性変形量
を適正に維持し、径方向の振動を減衰する。Since the respective elastic spheres are arranged at the center of the outer oil film surface, the amount of elastic deformation of each of the elastic spheres can be adjusted properly even if the end of the rotary shaft draws an arc and oscillates during operation. To attenuate radial vibrations.
【００２９】[0029]
【発明の実施の形態】以下、本発明の実施形態を添付図
面に基づいて説明する。Embodiments of the present invention will be described below with reference to the accompanying drawings.
【００３０】図２に示すように、ガスタービン１は、大
気を吸入して必要な圧力まで圧縮するコンプレッサ２
と、内部で燃料を燃焼させこのコンプレッサ２から送ら
れる圧縮空気を加熱して高温ガスをつくる燃焼器３と、
燃焼器３から出た燃焼ガスのもつエネルギーを機械的な
仕事に変換するタービン４と、タービン４から排出され
る排気ガスの熱によりコンプレッサ２から燃焼器３に送
られる圧縮空気を加熱する熱交換器５とから基本的に構
成される。燃焼器３に送られる燃料供給量を調整するた
め、燃料調整弁６が設けられる。As shown in FIG. 2, a gas turbine 1 is provided with a compressor 2 which draws in air and compresses the air to a required pressure.
And a combustor 3 that burns fuel inside and heats compressed air sent from the compressor 2 to create a high-temperature gas;
A turbine 4 for converting the energy of the combustion gas discharged from the combustor 3 into mechanical work, and a heat exchange for heating the compressed air sent from the compressor 2 to the combustor 3 by the heat of the exhaust gas discharged from the turbine 4 And a container 5. A fuel regulating valve 6 is provided to regulate the amount of fuel supplied to the combustor 3.
【００３１】バックトゥバックタイプのガスタービン１
に備えられる回転軸８は、一対の転がり軸受９，１０を
介して回転可能に支持される。回転軸８の転がり軸受
９，１０を介して片持ち支持されるオーバーハング部３
２にタービン４が結合されるとともに、コンプレッサ２
がタービンロータ４と背中合わせに結合される。Back-to-back type gas turbine 1
Is rotatably supported via a pair of rolling bearings 9, 10. Overhang portion 3 that is supported at one end via rolling bearings 9 and 10 of rotating shaft 8
2 is connected to the turbine 4 and the compressor 2
Are coupled back-to-back with the turbine rotor 4.
【００３２】燃焼器３でつくられる高温ガスはタービン
４に導入され、タービン４を高速で回転駆動する。The high-temperature gas produced in the combustor 3 is introduced into the turbine 4, and drives the turbine 4 to rotate at high speed.
【００３３】ガスタービンエンジン１の回転軸８に発電
機３０のロータが直結される。回転軸８の発電機３０が
連結される部位は、一対の転がり軸受９，１０を介して
両持ち支持される。The rotor of the generator 30 is directly connected to the rotating shaft 8 of the gas turbine engine 1. A portion of the rotating shaft 8 to which the generator 30 is connected is supported at both ends via a pair of rolling bearings 9 and 10.
【００３４】図１に示すように、各転がり軸受９，１０
は、回転軸８に結合するインナーレース１１と、ベアリ
ングハウジング２０側に支持されるアウターレース１３
と、両者の間に介装されるボール１２とによって構成さ
れる。回転軸８は各転がり軸受９，１０により支承され
る。As shown in FIG. 1, each of the rolling bearings 9, 10
Are an inner race 11 connected to the rotating shaft 8 and an outer race 13 supported on the bearing housing 20 side.
And a ball 12 interposed therebetween. The rotating shaft 8 is supported by rolling bearings 9 and 10.
【００３５】ベアリングハウジング２０とアウターレー
ス１３の間に円筒状のリテーナ１５が介装される。A cylindrical retainer 15 is interposed between the bearing housing 20 and the outer race 13.
【００３６】リテーナ１５とベアリングハウジング２０
のハウジング内周面２１の間にダンパ間隙１６が画成さ
れる。Retainer 15 and bearing housing 20
A damper gap 16 is defined between the inner peripheral surfaces 21 of the housing.
【００３７】ベアリングハウジング２０にはダンパ間隙
１６に潤滑油を圧送する給油通路１７が形成される。図
示しないオイルポンプから圧送される潤滑油がこの給油
通路１７を通ってダンパ間隙１６に供給されることによ
り、リテーナ１５はハウジング内周面２１に対して油膜
緩衝層を介して浮動支持される。各転がり軸受９，１０
は油膜緩衝層を介して浮動支持されることにより、転が
り軸受９，１０に生じる振動が吸収される。An oil supply passage 17 for feeding lubricating oil to the damper gap 16 is formed in the bearing housing 20. By supplying lubricating oil fed from an oil pump (not shown) to the damper gap 16 through the oil supply passage 17, the retainer 15 is supported by the housing inner peripheral surface 21 in a floating manner via an oil film buffer layer. Rolling bearings 9, 10
Is supported by floating through the oil film buffer layer, so that vibrations generated in the rolling bearings 9 and 10 are absorbed.
【００３８】各転がり軸受９，１０に向けて潤滑油を噴
射する噴口３５が形成される。噴口３５から供給される
潤滑油により各転がり軸受９，１０が潤滑され、高回転
域でも焼き付き等が発生することを防止できる。An injection port 35 for injecting lubricating oil toward each of the rolling bearings 9 and 10 is formed. Each of the rolling bearings 9 and 10 is lubricated by the lubricating oil supplied from the injection port 35, so that seizure or the like can be prevented from occurring even in a high rotation speed region.
【００３９】回転軸１の先端にはロックナット３３が螺
合し、このロックナット３３によりインナーレース１１
がカラー１４を介して締結される。A lock nut 33 is screwed into the end of the rotating shaft 1 and the inner race 11 is
Are fastened via the collar 14.
【００４０】本実施形態では、アウターレース１３の外
周面１８はリテーナ１５の内周面１９に圧入される。リ
テーナ１５にはアウターレース１３の右側面に当接する
スラスト受け部２４が環状に突出形成される。In this embodiment, the outer peripheral surface 18 of the outer race 13 is pressed into the inner peripheral surface 19 of the retainer 15. A thrust receiving portion 24 is formed in the retainer 15 so as to protrude annularly in contact with the right side surface of the outer race 13.
【００４１】リテーナ１５とベアリングハウジング２０
の間にはスプリング２３が介装される。スプリング２３
の付勢力によってリテーナ１５を介してアウターレース
１３は図１において左方向に付勢される。スプリング２
３の付勢力によってボール１２がインナーレース１１と
アウターレース１３に押し付けられることにより、高回
転域においてもボール１２が滑ることなく両者に転接し
て、フリクションが低く抑えられる。Retainer 15 and bearing housing 20
A spring 23 is interposed therebetween. Spring 23
The outer race 13 is urged leftward in FIG. 1 by the urging force via the retainer 15. Spring 2
When the ball 12 is pressed against the inner race 11 and the outer race 13 by the urging force of No. 3, the ball 12 rolls against the two without slipping even in a high rotation range, and the friction is suppressed low.
【００４２】回転軸８が図１において右方向に移動しよ
うとする場合、スプリング２３の付勢力によってリテー
ナ１５を介してアウターレース１３が左方向に付勢され
ているため、一方の転がり軸受９によってこのスラスト
力が受けられる。回転軸８が図１において左方向に移動
しようとする場合、別のスプリングと他方の転がり軸受
１０によってこのスラスト力が受けられる。When the rotating shaft 8 is to move rightward in FIG. 1, the outer race 13 is urged leftward by the urging force of the spring 23 via the retainer 15. This thrust force is received. When the rotating shaft 8 is to move to the left in FIG. 1, this thrust force is received by another spring and the other rolling bearing 10.
【００４３】ところで、運転時に回転軸８の各転がり軸
受９，１０を介して片持ち支持されるオーバーハング部
３２に曲げ変形が生じ、回転軸８の先端が図１に矢印で
示すように円弧を描いて振れまわるみそすり運動が発生
する可能性がある。In operation, bending deformation occurs in the overhang portion 32, which is cantilevered via the rolling bearings 9 and 10 of the rotating shaft 8, and the tip of the rotating shaft 8 is arcuate as shown by an arrow in FIG. And a swaying motion that swings around may occur.
【００４４】しかしながら、回転軸のオーバーハング部
から遠い先端側の転がり軸受において、ハウジング内周
面と転がり軸受間のダンパ間隙が軸方向に延びている従
来構造では、上記回転軸のみそすり運動が発生すると、
ダンパ間隙に形成される油膜緩衝層の端部で油膜が切れ
て、ダンパ間隙を画成するハウジング内周面に対して軸
受側外周面の両端部が接触し、異常振動や異音が発生す
る可能性がある。However, in the conventional structure in which the damper gap between the inner peripheral surface of the housing and the rolling bearing extends in the axial direction in the rolling bearing on the distal end side far from the overhang portion of the rotating shaft, only the rotating shaft slidably moves. When it occurs,
The oil film is cut off at the end of the oil film buffer layer formed in the damper gap, and both ends of the bearing-side outer peripheral surface come into contact with the inner peripheral surface of the housing that defines the damper gap, resulting in abnormal vibration and abnormal noise. there is a possibility.
【００４５】本発明はこれに対処して、回転軸８のオー
バーハング部３２から遠い先端側の転がり軸受９におい
て、ハウジング内周面２１に対峙するリテーナ１５の軸
受外周面２５にダンパ間隙１６を画成する外側油膜面２
６が環状に突出される。外側油膜面２６は給油通路１７
の出口３１に対峙する領域を含む環状に形成される。In view of this, the present invention provides a damper gap 16 in the bearing outer peripheral surface 25 of the retainer 15 facing the housing inner peripheral surface 21 in the rolling bearing 9 on the distal end far from the overhang portion 32 of the rotating shaft 8. Outer oil film surface 2 to be defined
6 protrudes annularly. The outer oil film surface 26 is connected to the oil supply passage 17.
Is formed in an annular shape including a region facing the outlet 31 of the first embodiment.
【００４６】軸受外周面２５とハウジング内周面２１の
間にはダンパ間隙１６から連続する間隙を拡大する一対
の逃げ空間２７が環状に画成される。A pair of clearance spaces 27 are formed between the bearing outer peripheral surface 25 and the housing inner peripheral surface 21 so as to extend from the damper gap 16 to a continuous gap.
【００４７】外側油膜面２６の中央部には１条の環状溝
２８が刻まれる。環状溝２８は給油通路１７の出口３１
に対峙する位置に形成される。A single annular groove 28 is formed in the center of the outer oil film surface 26. The annular groove 28 is the outlet 31 of the oil supply passage 17.
Is formed at a position facing the.
【００４８】回転軸８のオーバーハング部３２に近い側
の転がり軸受１０において、ハウジング内周面２１に対
峙するリテーナ１５の軸受外周面２５は直円筒面状に形
成され、ダンパ間隙１６を画成する外側油膜面が軸方向
について広い範囲にわたって形成される。In the rolling bearing 10 on the side close to the overhang portion 32 of the rotating shaft 8, the bearing outer peripheral surface 25 of the retainer 15 facing the housing inner peripheral surface 21 is formed in a straight cylindrical shape, and defines a damper gap 16. The outer oil film surface is formed over a wide range in the axial direction.
【００４９】以上のように構成され、次に作用について
説明する。The configuration is as described above, and the operation will now be described.
【００５０】回転軸８を各転がり軸受９，１０により支
承することにより、フリクションを低減することができ
る。リテーナ１５の軸受外周面２５はハウジング内周面
２１に対して油膜緩衝層を介して浮動支持されることに
より、各転がり軸受９，１０に生じる振動が吸収され
る。By supporting the rotating shaft 8 by the rolling bearings 9 and 10, friction can be reduced. The bearing outer peripheral surface 25 of the retainer 15 is floatingly supported on the housing inner peripheral surface 21 via the oil film buffer layer, so that vibrations generated in the rolling bearings 9 and 10 are absorbed.
【００５１】運転時に回転軸８の先端が図１に矢印で示
すように円弧を描いて振れまわるみそすり運動が発生す
ると、先端側の転がり軸受９において、ハウジング内周
面２１に対してリテーナ１５の軸受外周面２５が傾斜
し、両者間に画成されるダンパ間隙１６の断面が楔状に
なる。During operation, when the tip of the rotating shaft 8 moves in a circular motion as shown by the arrow in FIG. Of the bearing outer peripheral surface 25 is inclined, and the cross section of the damper gap 16 defined between them becomes wedge-shaped.
【００５２】本発明はこれに対処して、先端側の転がり
軸受９において、リテーナ１５の軸受外周面２５にダン
パ間隙１６を画成する外側油膜面２６を環状に突出させ
て、ダンパ間隙１６から連続する間隙を拡大する一対の
逃げ空間２７が環状に画成される構造のため、回転軸８
のみそすり運動が発生しても、ダンパ間隙１６の端部で
油膜緩衝層の油膜が切れてハウジング内周面２１に対し
て軸受外周面２５の両端部が接触することを防止でき
る。この結果、回転軸８のみそすり運動が発生しても、
転がり軸受９の近傍から異常振動や異音が発生すること
を防止できる。To cope with this, in the rolling bearing 9 on the distal end side, the outer oil film surface 26 defining the damper gap 16 is annularly protruded from the bearing outer peripheral surface 25 of the retainer 15 so as to extend from the damper gap 16. Due to the structure in which the pair of clearance spaces 27 for expanding the continuous gap are defined in a ring shape, the rotating shaft 8
Even if the rubbing motion occurs, it is possible to prevent the oil film of the oil film buffer layer from being cut off at the end of the damper gap 16, so that both ends of the bearing outer peripheral surface 25 are in contact with the housing inner peripheral surface 21. As a result, even if only the rotating shaft 8 generates the slewing motion,
It is possible to prevent abnormal vibration and abnormal noise from being generated from the vicinity of the rolling bearing 9.
【００５３】図示しないオイルポンプから圧送される潤
滑油がこの給油通路１７を通ってダンパ間隙１６に供給
される。ダンパ間隙１６に供給された潤滑油は、外側油
膜面２６に刻まれた環状溝２８を介してダンパ間隙１６
の全周にわたるように導かれ、ダンパ間隙１６の端部で
油膜緩衝層の油膜が切れることを防止できる。The lubricating oil fed from an oil pump (not shown) is supplied to the damper gap 16 through the oil supply passage 17. The lubricating oil supplied to the damper gap 16 is supplied to the damper gap 16 through an annular groove 28 formed in the outer oil film surface 26.
And the oil film of the oil film buffer layer can be prevented from being broken at the end of the damper gap 16.
【００５４】次に、図３に示す実施形態について説明す
る。なお、図１との対応部分には同一符号を付す。Next, the embodiment shown in FIG. 3 will be described. The parts corresponding to those in FIG. 1 are denoted by the same reference numerals.
【００５５】環状溝２８とハウジング内周面２１の間に
複数の弾性球４１が所定の間隔をもって介装される。弾
性球４１は樹脂からなる外皮によって鋼球が包まれてい
る。A plurality of elastic balls 41 are interposed at predetermined intervals between the annular groove 28 and the inner peripheral surface 21 of the housing. The elastic ball 41 has a steel ball wrapped by an outer shell made of resin.
【００５６】環状溝２８の底部には弾性球４１が嵌めら
れる凹部４２が形成される。凹部４２は弾性球４１の外
径より大きい開口径を持つ円柱状に形成される。A concave portion 42 into which the elastic ball 41 is fitted is formed at the bottom of the annular groove 28. The concave portion 42 is formed in a column shape having an opening diameter larger than the outer diameter of the elastic sphere 41.
【００５７】凹部４２の開口径は、環状溝２８の幅より
小さく設定され、環状溝２８に沿って流れる潤滑油が弾
性球４１のまわりを通って流れるようになっている。The opening diameter of the concave portion 42 is set smaller than the width of the annular groove 28 so that the lubricating oil flowing along the annular groove 28 flows around the elastic sphere 41.
【００５８】環状溝２８は外側油膜面２６の中央部に刻
まれ、弾性球４１は外側油膜面２６の中央に配置され
る。The annular groove 28 is cut in the center of the outer oil film surface 26, and the elastic sphere 41 is arranged at the center of the outer oil film surface 26.
【００５９】以上のように構成され、次に作用について
説明する。The operation will be described next.
【００６０】リテーナ１５の軸受外周面２５はハウジン
グ内周面２１に対して油膜緩衝層を介して浮動支持され
るとともに、弾性球４１を介して弾性支持されることに
より、転がり軸受９に生じる振動が吸収される。The bearing outer peripheral surface 25 of the retainer 15 is floatingly supported on the inner peripheral surface 21 of the housing via the oil film buffer layer, and is elastically supported via the elastic spheres 41, so that the vibration generated in the rolling bearing 9. Is absorbed.
【００６１】すなわち、ダンパ間隙１６を画成する外側
油膜面２６の軸方向の幅が短縮されるのに伴って油膜緩
衝層による負荷能力が低下する分を、弾性球４１の弾性
復元力が補い、径方向の振動を減衰する。That is, the elastic restoring force of the elastic ball 41 compensates for the load capacity of the oil film buffer layer which decreases as the axial width of the outer oil film surface 26 defining the damper gap 16 decreases. Attenuates radial vibrations.
【００６２】弾性球４１は外側油膜面２６の中央に配置
されているため、運転時に回転軸８の先端が図３に矢印
で示すように円弧を描いて振れまわるみそすり運動が発
生しても、弾性球４１の弾性変形量を適正に維持し、径
方向の振動を減衰する。Since the elastic sphere 41 is arranged at the center of the outer oil film surface 26, even if the tip of the rotating shaft 8 draws an arc as shown by an arrow in FIG. The elastic deformation of the elastic sphere 41 is properly maintained, and the vibration in the radial direction is attenuated.
【００６３】次に、図４に示す実施形態について説明す
る。なお、図１との対応部分には同一符号を付す。Next, the embodiment shown in FIG. 4 will be described. The parts corresponding to those in FIG. 1 are denoted by the same reference numerals.
【００６４】回転軸８のオーバーハング部３２から遠い
先端側の転がり軸受９において、ハウジング内周面２１
に対峙するリテーナ１５の軸受外周面２５にダンパ間隙
１６を画成する外側油膜面２６が環状に突出形成され
る。In the rolling bearing 9 at the tip end far from the overhang portion 32 of the rotating shaft 8, the inner circumferential surface 21 of the housing
An outer oil film surface 26 defining a damper gap 16 is formed in a ring shape on an outer peripheral surface 25 of the bearing of the retainer 15 facing the outer oil film surface.
【００６５】外側油膜面２６は、環状溝２８を挟んで大
径外側油膜面部４５と、小径外側油膜面部４６を有す
る。大径外側油膜面部４５とハウジング内周面２１の間
に画成される。The outer oil film surface 26 has a large-diameter outer oil film surface 45 and a small-diameter outer oil film surface 46 with the annular groove 28 interposed therebetween. It is defined between the large-diameter outer oil film surface portion 45 and the housing inner peripheral surface 21.
【００６６】軸受外周面２５とハウジング内周面２１の
間にダンパ間隙１６のうち、大径外側油膜面部４５によ
って画成される間隙は小径外側油膜面部４６よって画成
される間隙より小さい。大径外側油膜面部４５は小径外
側油膜面部４６よりベアリングハウジング２０の内側に
配置される。In the damper gap 16 between the bearing outer peripheral surface 25 and the housing inner peripheral surface 21, the gap defined by the large-diameter outer oil film surface 45 is smaller than the gap defined by the small-diameter outer oil film surface 46. The large-diameter outer oil film surface portion 45 is disposed inside the bearing housing 20 with respect to the small-diameter outer oil film surface portion 46.
【００６７】以上のように構成され、次に作用について
説明する。The operation will be described next.
【００６８】図示しないオイルポンプから圧送される潤
滑油が給油通路１７を通ってダンパ間隙１６に供給され
ることにより、リテーナ１５はハウジング内周面２１に
対して油膜緩衝層を介して浮動支持される。When the lubricating oil fed from an oil pump (not shown) is supplied to the damper gap 16 through the oil supply passage 17, the retainer 15 is floatingly supported on the inner peripheral surface 21 of the housing via the oil film buffer layer. You.
【００６９】この場合、ダンパ間隙１６は大径外側油膜
面部４５によって画成される間隙は小径外側油膜面部４
６よって画成される間隙より小さいため、大径外側油膜
面部４５を経てベアリングハウジング２０の内側に流入
する潤滑油量を抑えられ、大部分の潤滑油が小径外側油
膜面部４６を経てベアリングハウジング２０の外側に流
出する。この結果、ベアリングハウジング２０の内部に
形成される図示しない戻り側油通路の断面積を小さくし
て、発電装置のコンパクト化がはかれる。In this case, the gap defined by the large-diameter outer oil film surface portion 45 is the small-diameter outer oil film surface portion 4.
6, the amount of lubricating oil flowing into the inside of the bearing housing 20 through the large-diameter outer oil film surface portion 45 can be suppressed, and most of the lubricating oil can pass through the small-diameter outer oil film surface portion 46 and be reduced. Spills out of the As a result, the cross-sectional area of a return side oil passage (not shown) formed inside the bearing housing 20 is reduced, and the power generation device is made compact.
【００７０】次に、図５に示す実施形態について説明す
る。なお、図１との対応部分には同一符号を付す。Next, the embodiment shown in FIG. 5 will be described. The parts corresponding to those in FIG. 1 are denoted by the same reference numerals.
【００７１】ベアリングハウジング２０とアウターレー
ス１３の間に円筒状のリテーナ１５が介装される。A cylindrical retainer 15 is interposed between the bearing housing 20 and the outer race 13.
【００７２】リテーナ１５とベアリングハウジング２０
のハウジング内周面２１の間にダンパ間隙１６が画成さ
れる。Retainer 15 and bearing housing 20
A damper gap 16 is defined between the inner peripheral surfaces 21 of the housing.
【００７３】リテーナ１５の軸受外周面２５にダンパ間
隙１６を画成する外側油膜面２６を環状に突出形成され
る。外側油膜面２６は給油通路１７の出口３１に対峙す
る領域を含む環状に形成される。An outer oil film surface 26 which defines the damper gap 16 is formed on the bearing outer peripheral surface 25 of the retainer 15 so as to project annularly. The outer oil film surface 26 is formed in an annular shape including a region facing the outlet 31 of the oil supply passage 17.
【００７４】軸受外周面２５とハウジング内周面２１の
間にはダンパ間隙１６から連続する間隙を拡大する一対
の逃げ空間２７が環状に画成される。A pair of clearance spaces 27 is formed between the bearing outer peripheral surface 25 and the housing inner peripheral surface 21 so as to extend from the damper gap 16 in a ring shape.
【００７５】外側油膜面２６の中央部には１条の環状溝
２８が刻まれる。環状溝２８は給油通路１７の出口３１
に対峙する位置に形成される。A single annular groove 28 is formed in the center of the outer oil film surface 26. The annular groove 28 is the outlet 31 of the oil supply passage 17.
Is formed at a position facing the.
【００７６】リテーナ１５とアウターレース１３の外周
面１８の間に内側ダンパ間隙５１が画成される。An inner damper gap 51 is defined between the retainer 15 and the outer peripheral surface 18 of the outer race 13.
【００７７】リテーナ１５の軸受内周面１９に内側ダン
パ間隙５１を画成する内側油膜面５２が環状に突出形成
される。外側油膜面２６は給油通路１７の出口３１に対
峙する領域を含む環状に形成される。An inner oil film surface 52 defining an inner damper gap 51 is formed in a ring shape on the bearing inner peripheral surface 19 of the retainer 15. The outer oil film surface 26 is formed in an annular shape including a region facing the outlet 31 of the oil supply passage 17.
【００７８】リテーナ１５の内周面２５とアウターレー
ス１３の外周面１８の間には内側ダンパ間隙５１から連
続する間隙を拡大する一対の逃げ空間５３が環状に画成
される。Between the inner peripheral surface 25 of the retainer 15 and the outer peripheral surface 18 of the outer race 13, a pair of clearance spaces 53 extending from the inner damper gap 51 to extend the gap are formed in an annular shape.
【００７９】内側油膜面５２の中央部には１条の内側環
状溝５４が刻まれる。内側環状溝５４は複数の通孔５５
を介して外側油膜面２６に刻まれた環状溝２８に連通す
る。A single inner annular groove 54 is formed in the center of the inner oil film surface 52. The inner annular groove 54 has a plurality of through holes 55.
Through an annular groove 28 formed in the outer oil film surface 26.
【００８０】以上のように構成され、次に作用について
説明する。The structure is as described above. Next, the operation will be described.
【００８１】図示しないオイルポンプから圧送される潤
滑油が給油通路１７を通ってダンパ間隙１６に供給され
ることにより、リテーナ１５はハウジング内周面２１に
対して油膜緩衝層を介して浮動支持される。The lubricating oil fed from an oil pump (not shown) is supplied to the damper gap 16 through the oil supply passage 17 so that the retainer 15 is floatingly supported on the housing inner peripheral surface 21 via the oil film buffer layer. You.
【００８２】ダンパ間隙１６に供給された潤滑油は、外
側油膜面２６に刻まれた環状溝２８を介してダンパ間隙
１６の全周にわたるように導かれ、ダンパ間隙１６の端
部で油膜緩衝層の油膜が切れることが防止される。The lubricating oil supplied to the damper gap 16 is guided over the entire periphery of the damper gap 16 through an annular groove 28 cut in the outer oil film surface 26, and the oil film buffer layer is formed at the end of the damper gap 16. This prevents the oil film from breaking.
【００８３】ダンパ間隙１６に圧送される潤滑油の一部
が各通孔５５を通って内側ダンパ間隙５１に供給される
ことにより、アウターレース１３はリテーナ１５に対し
て油膜緩衝層を介して浮動支持される。When a part of the lubricating oil fed to the damper gap 16 is supplied to the inner damper gap 51 through each through hole 55, the outer race 13 floats on the retainer 15 via the oil film buffer layer. Supported.
【００８４】内側ダンパ間隙５１に供給された潤滑油
は、内側油膜面５２に刻まれた内側環状溝５４を介して
内側ダンパ間隙５１の全周にわたるように導かれ、内側
ダンパ間隙５１の端部で油膜緩衝層の油膜が切れること
が防止される。The lubricating oil supplied to the inner damper gap 51 is guided over the entire circumference of the inner damper gap 51 via the inner annular groove 54 formed on the inner oil film surface 52, and the end of the inner damper gap 51 This prevents the oil film of the oil film buffer layer from breaking.
【００８５】転がり軸受９はリテーナ１５の内外周に形
成される二重の油膜緩衝層を介して浮動支持されること
により、転がり軸受９に生じる振動が有効に吸収され
る。The rolling bearing 9 is floated and supported via a double oil film buffer layer formed on the inner and outer circumferences of the retainer 15, so that the vibration generated in the rolling bearing 9 is effectively absorbed.
【００８６】運転時に回転軸８の先端が図１に矢印で示
すように円弧を描いて振れまわるみそすり運動が発生す
ると、先端側の転がり軸受９において、ハウジング内周
面２１に対してリテーナ１５の軸受外周面２５が傾斜す
るとともに、リテーナ軸受内周面１９に対してアウター
レース１３の外周面１８が傾斜する。During operation, when the end of the rotating shaft 8 moves in an arc as shown by the arrow in FIG. The outer peripheral surface 18 of the outer race 13 is inclined with respect to the inner peripheral surface 19 of the retainer bearing.
【００８７】先端側の転がり軸受９において、リテーナ
１５の内外周には、各ダンパ間隙１６，５１から連続す
る間隙を拡大する逃げ空間２７，５３が二重に画成され
る構造のため、回転軸８のみそすり運動が大きくなって
も、各ダンパ間隙１６，５１の端部で油膜緩衝層の油膜
が切れることを防止できる。この結果、回転軸８のみそ
すり運動が大きくなっても、転がり軸受９の近傍から異
常振動や異音が発生することを防止できる。In the rolling bearing 9 on the distal end side, since the clearance spaces 27 and 53 which enlarge the gaps continuous from the damper gaps 16 and 51 are formed on the inner and outer circumferences of the retainer 15, the rotation is made. Even if the slewing motion of the shaft 8 is large, it is possible to prevent the oil film of the oil film buffer layer from being broken at the end of each of the damper gaps 16 and 51. As a result, even if the rotation motion of only the rotating shaft 8 increases, it is possible to prevent abnormal vibration and abnormal noise from being generated in the vicinity of the rolling bearing 9.
【００８８】次に、図６に示す実施形態について説明す
る。なお、図５との対応部分には同一符号を付す。Next, the embodiment shown in FIG. 6 will be described. Parts corresponding to those in FIG. 5 are denoted by the same reference numerals.
【００８９】環状溝２８とハウジング内周面２１の間に
複数の弾性球４１が所定の間隔をもって介装されるとと
もに、環状溝６２とアウターレース１３の外周面１８の
間に複数の内側弾性球６１が所定の間隔をもって介装さ
れる。弾性球４１，６１は樹脂からなる外皮によって鋼
球が包まれている。A plurality of elastic spheres 41 are interposed at predetermined intervals between the annular groove 28 and the housing inner peripheral surface 21, and a plurality of inner elastic spheres are provided between the annular groove 62 and the outer peripheral surface 18 of the outer race 13. 61 are interposed at predetermined intervals. The steel balls are wrapped in the elastic balls 41 and 61 by an outer cover made of resin.
【００９０】環状溝２８の底部には弾性球４１が嵌めら
れる凹部４２が形成される。凹部４２は弾性球４１の外
径より大きい開口径を持つ円柱状に形成される。凹部４
２の開口径は、環状溝２８の幅より小さく設定され、環
状溝２８に沿って流れる潤滑油が弾性球４１のまわりを
通って流れるようになっている。At the bottom of the annular groove 28, a concave portion 42 into which the elastic ball 41 is fitted is formed. The concave portion 42 is formed in a column shape having an opening diameter larger than the outer diameter of the elastic sphere 41. Recess 4
The opening diameter of 2 is set smaller than the width of the annular groove 28 so that the lubricating oil flowing along the annular groove 28 flows around the elastic sphere 41.
【００９１】内側環状溝５４の底部には内側弾性球６１
が嵌められる凹部６２が形成される。凹部６２は内側弾
性球６１の外径より大きい開口径を持つ円柱状に形成さ
れる。凹部６２の開口径は、内側環状溝５４の幅より小
さく設定され、内側環状溝５４に沿って流れる潤滑油が
内側弾性球６１のまわりを通って流れるようになってい
る。At the bottom of the inner annular groove 54, an inner elastic ball 61 is provided.
A concave portion 62 into which is fitted is formed. The concave portion 62 is formed in a column shape having an opening diameter larger than the outer diameter of the inner elastic sphere 61. The opening diameter of the concave portion 62 is set smaller than the width of the inner annular groove 54 so that the lubricating oil flowing along the inner annular groove 54 flows around the inner elastic sphere 61.
【００９２】以上のように構成され、次に作用について
説明する。The operation is as described above. Next, the operation will be described.
【００９３】転がり軸受９はリテーナ１５の内外周に形
成される二重の油膜緩衝層を介して浮動支持されるとと
もに、リテーナ１５の内外周に設けられる弾性球４１，
６１を介して弾性支持されることにより、回転軸８のみ
そすり運動が大きくなっても、各ダンパ間隙１６，５１
の端部で油膜緩衝層の油膜が切れることを防止でき、転
がり軸受９に生じる振動が有効に吸収される。The rolling bearing 9 is floated and supported via a double oil film buffer layer formed on the inner and outer circumferences of the retainer 15, and has elastic balls 41, provided on the inner and outer circumferences of the retainer 15.
Due to the elastic support via the shaft 61, even if the rotation motion of only the rotating shaft 8 increases, the damper gaps 16, 51
The oil film of the oil film buffer layer can be prevented from being cut at the end of the shaft, and the vibration generated in the rolling bearing 9 is effectively absorbed.
【００９４】すなわち、各ダンパ間隙１６，５１を画成
する外側油膜面２６，５２の軸方向の幅が短縮されるの
に伴って油膜緩衝層による負荷能力が低下する分を、各
弾性球４１，６１の弾性復元力が補い、径方向の振動を
減衰する。That is, as the axial width of the outer oil film surfaces 26, 52 defining the damper gaps 16, 51 is reduced, the load capacity of the oil film buffer layer decreases as the elastic ball 41 reduces. , 61 compensate for the elastic restoring force and attenuate radial vibration.
【００９５】各弾性球４１，６１は外側油膜面２６，５
２の中央に配置されているため、運転時に回転軸８の先
端が図６に矢印で示すように円弧を描いて振れまわるみ
そすり運動が発生しても、各弾性球４１，６１の弾性変
形量を適正に維持し、径方向の振動を減衰する。Each of the elastic spheres 41, 61 has an outer oil film surface 26, 5
2, the elastic balls 41 and 61 are elastically deformed even when the tip of the rotating shaft 8 oscillates in an arc as shown by an arrow in FIG. Maintain the proper amount and dampen radial vibrations.
【００９６】[0096]
【発明の効果】以上説明したように請求項１に記載の高
速回転軸の軸受構造によれば、先端側の転がり軸受にお
いて、リテーナの軸受外周面からダンパ間隙を画成する
外側油膜面を環状に突出させて、ダンパ間隙から連続す
る間隙を拡大する逃げ空間を画成する構造のため、回転
軸のみそすり運動が発生しても、ダンパ間隙の端部で油
膜緩衝層の油膜が切れてハウジング内周面に軸受外周面
の両端部が接触することを防止でき、転がり軸受の近傍
から異常振動や異音が発生することを防止できる。As described above, according to the bearing structure of the high-speed rotating shaft according to the first aspect, in the rolling bearing on the tip end side, the outer oil film surface defining the damper gap from the bearing outer peripheral surface of the retainer is annular. And a relief space that expands the gap that continues from the damper gap, so that even if the rotating shaft only rubs, the oil film of the oil film buffer layer breaks at the end of the damper gap. It is possible to prevent both ends of the outer peripheral surface of the bearing from contacting the inner peripheral surface of the housing, and to prevent abnormal vibration and abnormal noise from being generated in the vicinity of the rolling bearing.
【００９７】請求項２に記載の高速回転軸の軸受構造に
よれば、給油通路を通ってダンパ間隙に供給された潤滑
油は、外側油膜面に刻まれた環状溝を介してダンパ間隙
の全周にわたるように導かれ、回転軸のみそすり運動が
発生しても、ダンパ間隙の端部で油膜緩衝層の油膜が切
れることが防止され、転がり軸受の近傍から異常振動や
異音が発生することを防止できる。According to the bearing structure of the high-speed rotating shaft according to the second aspect, the lubricating oil supplied to the damper gap through the oil supply passage is entirely filled in the damper gap via the annular groove formed in the outer oil film surface. Even when the rotary shaft is guided so as to extend over the circumference, the oil film of the oil film buffer layer is prevented from being cut off at the end of the damper gap, and abnormal vibration and abnormal noise are generated near the rolling bearing Can be prevented.
【００９８】請求項３に記載の高速回転軸の軸受構造に
よれば、軸受外周面はハウジング内周面に対して油膜緩
衝層を介して浮動支持されるとともに、弾性球を介して
弾性支持されることにより、転がり軸受に生じる振動が
吸収され、回転軸のみそすり運動が発生しても、転がり
軸受の近傍から異常振動や異音が発生することを防止で
きる。According to the bearing structure of the high-speed rotating shaft according to the third aspect, the outer peripheral surface of the bearing is floatingly supported on the inner peripheral surface of the housing via the oil film buffer layer and elastically supported via the elastic ball. Accordingly, the vibration generated in the rolling bearing is absorbed, and even if the rotating shaft generates the slewing motion, abnormal vibration and abnormal noise can be prevented from being generated in the vicinity of the rolling bearing.
【００９９】請求項４に記載の高速回転軸の軸受構造に
よれば、ダンパ間隙は大径外側油膜面部によって画成さ
れる間隙は小径外側油膜面部よって画成される間隙より
小さいため、大径外側油膜面部を経てハウジングの内側
に流入する潤滑油量を抑えられ、大部分の潤滑油が小径
外側油膜面部を経てハウジングの外側に流出する。この
結果、ハウジングの内部に形成される戻り側油通路の断
面積を小さくして、装置のコンパクト化がはかれる。According to the bearing structure of the high-speed rotating shaft according to the fourth aspect, the gap defined by the large-diameter outer oil film surface portion is smaller than the gap defined by the small-diameter outer oil film surface portion. The amount of lubricating oil flowing into the inside of the housing through the outer oil film surface is reduced, and most of the lubricating oil flows out of the housing through the small-diameter outer oil film surface. As a result, the cross-sectional area of the return-side oil passage formed inside the housing is reduced, and the device is made compact.
【０１００】請求項５に記載の高速回転軸の軸受構造に
よれば、潤滑油が給油通路を通ってダンパ間隙に供給さ
れることにより、リテーナはハウジング内周面に対して
油膜緩衝層を介して浮動支持され、転がり軸受の近傍か
ら異常振動や異音が発生することを防止できる。According to the bearing structure of the high-speed rotating shaft according to the fifth aspect, the lubricating oil is supplied to the damper gap through the oil supply passage, so that the retainer is disposed on the inner peripheral surface of the housing via the oil film buffer layer. The floating bearing is supported to prevent abnormal vibration and abnormal noise from being generated in the vicinity of the rolling bearing.
【０１０１】請求項６に記載の高速回転軸の軸受構造に
よれば、転がり軸受はリテーナの内外周に形成される二
重の油膜緩衝層を介して浮動支持されることにより、転
がり軸受に生じる振動が有効に吸収され、回転軸のみそ
すり運動が大きくなっても転がり軸受の近傍から異常振
動や異音が発生することを防止できる。According to the bearing structure of the high-speed rotating shaft according to the sixth aspect, the rolling bearing is floated and supported by the double oil film buffer layers formed on the inner and outer circumferences of the retainer, thereby generating the rolling bearing. Even if the vibration is effectively absorbed and the slewing motion of only the rotary shaft is increased, it is possible to prevent the occurrence of abnormal vibration or abnormal noise near the rolling bearing.
【０１０２】請求項７に記載の高速回転軸の軸受構造に
よれば、転がり軸受はリテーナの内外周に形成される二
重の油膜緩衝層を介して浮動支持されるとともに、リテ
ーナの内外周に介装される各弾性球を介して弾性支持さ
れることにより、転がり軸受に生じる振動が有効に吸収
され、回転軸のみそすり運動が大きくなっても、転がり
軸受の近傍から異常振動や異音が発生することを防止で
きる。According to the bearing structure of the high-speed rotating shaft according to the seventh aspect, the rolling bearing is floated and supported via the double oil film buffer layers formed on the inner and outer circumferences of the retainer, and is supported on the inner and outer circumferences of the retainer. By being elastically supported through the interposed elastic spheres, vibrations generated in the rolling bearings are effectively absorbed, and even if the rotating shaft only has large slewing motion, abnormal vibrations and abnormal noise can be seen from near the rolling bearings. Can be prevented from occurring.
【図１】本発明の実施形態を示す断面図。FIG. 1 is a sectional view showing an embodiment of the present invention.
【図２】同じくガスタービン発電装置の構成図。FIG. 2 is a configuration diagram of a gas turbine power generator.
【図３】他の実施形態を示す断面図。FIG. 3 is a cross-sectional view showing another embodiment.
【図４】さらに他の実施形態を示す断面図。FIG. 4 is a sectional view showing still another embodiment.
【図５】さらに他の実施形態を示す断面図。FIG. 5 is a sectional view showing still another embodiment.
【図６】さらに他の実施形態を示す断面図。FIG. 6 is a sectional view showing still another embodiment.
８ 回転軸 ９ 転がり軸受 １１ インナーレース １２ ボール １３ アウターレース １６ ダンパ間隙 １８ アウターレース外周面 １９ リテーナ内周面 ２０ ベアリングハウジング ２１ ハウジング内周面 ２５ 軸受外周面 ２６ 外側油膜面 ２７ 逃げ空間 ２８ 環状溝 ４１ 弾性球 ４２ 凹部 ４５ 大径外側油膜面部 ４６ 小径外側油膜面部 ５１ 内側ダンパ間隙 ５２ 内側油膜面 ５３ 逃げ空間 ５４ 内側環状溝 ５５ 通孔 ６１ 内側弾性球 ６２ 凹部 Reference Signs List 8 rotary shaft 9 rolling bearing 11 inner race 12 ball 13 outer race 16 damper gap 18 outer race outer peripheral surface 19 retainer inner peripheral surface 20 bearing housing 21 housing inner peripheral surface 25 bearing outer peripheral surface 26 outer oil film surface 27 relief space 28 annular groove 41 Elastic sphere 42 Recess 45 Large-diameter outer oil film surface 46 Small-diameter outer oil film surface 51 Inner damper gap 52 Inner oil film surface 53 Escape space 54 Inner annular groove 55 Through hole 61 Inner elastic ball 62 recess
Claims (7)
回転軸を備え、 回転軸は各転がり軸受に片持ち支持されるオーバーハン
グ部を有し、 各転がり軸受けを支持するハウジング内周面を備え、 各転がり軸受の軸受外周面とハウジング内周面の間に油
膜緩衝層を形成するダンパ隙間を画成し、 ダンパ隙間に潤滑油を圧送する給油通路を備える高速回
転軸の軸受構造において、 前記オーバーハング部から最も離れた先端側に設けられ
る軸受外周面にダンパ間隙を画成する外側油膜面を回転
軸の径方向に環状に突出させ、 ダンパ間隙から連続してその間隙を拡大する逃げ空間を
備えたことを特徴とする高速回転軸の軸受構造。An inner peripheral surface of a housing that has a rotating shaft rotatably supported by a plurality of rolling bearings, the rotating shaft has an overhang portion that is cantilevered by each rolling bearing, and supports each rolling bearing. A high-speed rotating shaft bearing structure that defines a damper gap that forms an oil film buffer layer between the bearing outer peripheral surface and the housing inner peripheral surface of each rolling bearing, and that has an oil supply passage that feeds lubricating oil to the damper gap. An outer oil film surface defining a damper gap is annularly projected in the radial direction of the rotating shaft on a bearing outer peripheral surface provided on a distal end side furthest from the overhang portion, and the gap is continuously enlarged from the damper gap. A bearing structure for a high-speed rotating shaft, characterized by having a clearance space.
を特徴とする請求項１に記載の高速回転軸の軸受構造。2. The bearing structure for a high-speed rotating shaft according to claim 1, wherein an annular groove is formed in the outer oil film surface, and the annular groove is arranged so as to face an outlet of the oil supply passage.
の弾性球を介装し、 各弾性球を外側油膜面の中央に配置したことを特徴とす
る請求項２に記載の高速回転軸の軸受構造。3. The high-speed rotation according to claim 2, wherein a plurality of elastic spheres are interposed between the annular groove and the inner peripheral surface of the housing, and each elastic sphere is arranged at the center of the outer oil film surface. Shaft bearing structure.
違する大径外側油膜面部と小径外側油膜面部を形成し、 大径外側油膜面部を小径外側油膜面部よりハウジング内
周面の奥部に対峙するように配置したことを特徴とする
請求項１または２に記載の高速回転軸の軸受構造。4. A large-diameter outer oil film surface portion and a small-diameter outer oil film surface portion having outer diameters different from each other with an annular groove interposed therebetween on said outer oil film surface. The bearing structure for a high-speed rotating shaft according to claim 1, wherein the bearing structure is arranged so as to face a deep portion.
ハウジング内周面の間に円筒状をしたリテーナを介装
し、 リテーナの軸受外周面にダンパ間隙を画成する外側油膜
面を回転軸の径方向に環状に突出させたことを特徴とす
る請求項１から４のいずれか一つに記載の高速回転軸の
軸受構造。5. A cylindrical retainer is interposed between the outer peripheral surface of the outer race of the rolling bearing and the inner peripheral surface of the housing, and an outer oil film surface defining a damper gap on the outer peripheral surface of the bearing of the retainer is provided on the rotating shaft. The bearing structure for a high-speed rotating shaft according to any one of claims 1 to 4, wherein the bearing structure is annularly projected in a radial direction.
ハウジング内周面の間に円筒状をしたリテーナを介装
し、 リテーナの軸受外周面と軸受内周面にダンパ間隙を画成
する油膜面をそれぞれ回転軸の径方向に環状に突出さ
せ、 各ダンパ間隙から連続してその間隙を拡大する逃げ空間
を備え、 内外の各油膜面に環状溝を形成し、 内外の各環状溝を連通する通孔を形成したことを特徴と
する請求項１から５のいずれか一つに記載の高速回転軸
の軸受構造。6. An oil film surface in which a cylindrical retainer is interposed between an outer race outer peripheral surface of the rolling bearing and an inner peripheral surface of the housing, and a damper gap is formed between the outer peripheral surface of the retainer and the inner peripheral surface of the bearing. Are protruded annularly in the radial direction of the rotating shaft, and a clearance space is provided from each of the damper gaps so as to continuously expand the gaps. 6. The bearing structure for a high-speed rotating shaft according to claim 1, wherein a through hole is formed.
はアウターレース外周面の間に複数の弾性球を介装し、 各弾性球を内外の各油膜面の中央に配置したことを特徴
とする請求項６に記載の高速回転軸の軸受構造。7. A plurality of elastic spheres are interposed between the inner and outer annular grooves and the inner peripheral surface of the housing or the outer peripheral surface of the outer race, and each elastic sphere is arranged at the center of the inner and outer oil film surfaces. The bearing structure for a high-speed rotating shaft according to claim 6.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP8161952A JPH109268A (en) | 1996-06-21 | 1996-06-21 | Bearing structure of high speed rotational shaft |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP8161952A JPH109268A (en) | 1996-06-21 | 1996-06-21 | Bearing structure of high speed rotational shaft |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH109268A true JPH109268A (en) | 1998-01-13 |
Family
ID=15745181
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP8161952A Pending JPH109268A (en) | 1996-06-21 | 1996-06-21 | Bearing structure of high speed rotational shaft |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH109268A (en) |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2013011839A1 (en) * | 2011-07-15 | 2013-01-24 | 三菱重工業株式会社 | Electric supercharger, method for assembling same, and internal combustion engine |
| CN106907355A (en) * | 2017-04-28 | 2017-06-30 | 中国航发湖南动力机械研究所 | A kind of elastic bearing squeeze film damper |
| EP3372840A1 (en) * | 2017-03-06 | 2018-09-12 | Panasonic Intellectual Property Management Co., Ltd. | Turbo compressor |
| CN113348309A (en) * | 2019-02-07 | 2021-09-03 | 基伊埃工程技术股份有限公司 | Rotary bearing with damper, motor and rotary atomizer comprising such a bearing, and use of such a bearing |
| CN113472125A (en) * | 2020-03-31 | 2021-10-01 | 日本电产株式会社 | Drive device |
-
1996
- 1996-06-21 JP JP8161952A patent/JPH109268A/en active Pending
Cited By (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2013011839A1 (en) * | 2011-07-15 | 2013-01-24 | 三菱重工業株式会社 | Electric supercharger, method for assembling same, and internal combustion engine |
| JP2013024059A (en) * | 2011-07-15 | 2013-02-04 | Mitsubishi Heavy Ind Ltd | Electric supercharge compressor, method for assembling the same, and internal combustion engine |
| CN103649545A (en) * | 2011-07-15 | 2014-03-19 | 三菱重工业株式会社 | Electric supercharger, method for assembling same, and internal combustion engine |
| US9470140B2 (en) | 2011-07-15 | 2016-10-18 | Mitsubishi Heavy Industries, Ltd. | Electric supercharger, assembling method of the same, and internal combustion engine |
| EP3372840A1 (en) * | 2017-03-06 | 2018-09-12 | Panasonic Intellectual Property Management Co., Ltd. | Turbo compressor |
| JP2018145969A (en) * | 2017-03-06 | 2018-09-20 | パナソニックＩｐマネジメント株式会社 | Turbo compressor |
| CN106907355A (en) * | 2017-04-28 | 2017-06-30 | 中国航发湖南动力机械研究所 | A kind of elastic bearing squeeze film damper |
| CN106907355B (en) * | 2017-04-28 | 2019-03-05 | 中国航发湖南动力机械研究所 | A kind of elastic bearing squeeze film damper |
| CN113348309A (en) * | 2019-02-07 | 2021-09-03 | 基伊埃工程技术股份有限公司 | Rotary bearing with damper, motor and rotary atomizer comprising such a bearing, and use of such a bearing |
| US20220099141A1 (en) * | 2019-02-07 | 2022-03-31 | Gea Process Engineering A/S | Rotary Bearing with a Damper and a Motor and a Rotary Atomizer with Such Bearing, and Use Thereof |
| US11788577B2 (en) * | 2019-02-07 | 2023-10-17 | Gea Process Engineering A/S | Rotary bearing with a damper and a motor and a rotary atomizer with such bearing, and use thereof |
| CN113472125A (en) * | 2020-03-31 | 2021-10-01 | 日本电产株式会社 | Drive device |
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