JPH1162953A - Bearing device - Google Patents
Bearing deviceInfo
- Publication number
- JPH1162953A JPH1162953A JP9227101A JP22710197A JPH1162953A JP H1162953 A JPH1162953 A JP H1162953A JP 9227101 A JP9227101 A JP 9227101A JP 22710197 A JP22710197 A JP 22710197A JP H1162953 A JPH1162953 A JP H1162953A
- Authority
- JP
- Japan
- Prior art keywords
- bearing
- housing
- retainer
- bearing device
- cylindrical member
- 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
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/30—Parts of ball or roller bearings
- F16C33/66—Special parts or details in view of lubrication
- F16C33/6637—Special parts or details in view of lubrication with liquid lubricant
- F16C33/6659—Details of supply of the liquid to the bearing, e.g. passages or nozzles
-
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/54—Systems consisting of a plurality of bearings with rolling friction
- F16C19/546—Systems with spaced apart rolling bearings including at least one angular contact bearing
- F16C19/547—Systems with spaced apart rolling bearings including at least one angular contact bearing with two angular contact rolling bearings
- F16C19/548—Systems with spaced apart rolling bearings including at least one angular contact bearing with two angular contact rolling bearings in O-arrangement
-
- 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
-
- 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
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/30—Parts of ball or roller bearings
- F16C33/58—Raceways; Race rings
- F16C33/583—Details of specific parts of races
- F16C33/586—Details of specific parts of races outside the space between the races, e.g. end faces or bore of inner ring
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Rolling 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、ガスタービンエン
ジンなどの軸受構造に適用して好ましい軸受装置に関
し、特にハウジングとアウターレースとの間にリテーナ
ベアリングが設けられ、これらの間にラジアル方向の振
動を吸収するためのスクイーズフィルムダンパ（Squeez
e film dumper ）が設けられた軸受装置に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a bearing device which is preferably applied to a bearing structure of a gas turbine engine or the like, and in particular, a retainer bearing is provided between a housing and an outer race, and radial vibration is provided between these. Film damper (Squeez
e film dumper).
【０００２】[0002]
【従来の技術】従来のガスタービンエンジンの軸受装置
としては、たとえば図５に示すようなものが知られてい
る（実開昭５５−９０，８１６号公報参照）。この構成
を組付け手順に従って説明すると、ガスタービンの高速
回転軸１は、ハウジング８に取り付けられた図示しない
軸受により、スラスト方向の動きを制限された状態で組
み付けられている。2. Description of the Related Art As a conventional bearing device for a gas turbine engine, for example, the one shown in FIG. 5 is known (see Japanese Utility Model Laid-Open No. 55-90,816). This configuration will be described according to an assembling procedure. The high-speed rotating shaft 1 of the gas turbine is assembled with a bearing (not shown) attached to the housing 8 in a state where movement in the thrust direction is restricted.
【０００３】この状態でハウジング８に、弾性体７、リ
テーナベアリング４と一体化されたアウタレース２ａ、
およびベアリング２を組み付け、ナット３にてインナレ
ース２ｂを回転軸１に締め込むことにより、軸受装置が
構成される。In this state, the outer race 2a integrated with the elastic body 7 and the retainer bearing 4 is provided on the housing 8,
And the bearing 2 are assembled, and the inner race 2b is fastened to the rotating shaft 1 with the nut 3, thereby forming a bearing device.
【０００４】リテーナベアリング４とハウジング８との
間には隙間５ａが形成され、またリテーナベアリング４
とアウタレース２ａとの間には隙間５ｂが形成されてお
り、潤滑オイル供給孔６から潤滑オイルを供給すること
により、これらの隙間５ａ，５ｂにスクイーズフィルム
ダンパーが形成され、このスクイーズフィルムダンパに
よって高速回転軸１の半径方向の振動が吸収される。[0004] A gap 5 a is formed between the retainer bearing 4 and the housing 8.
A gap 5b is formed between the outer race 2a and the outer race 2a. By supplying lubricating oil from the lubricating oil supply hole 6, a squeeze film damper is formed in the gaps 5a and 5b. Radial vibration of the rotating shaft 1 is absorbed.
【０００５】なお、弾性体７は、リテーナベアリング４
を介して軸受装置にスラスト方向の予荷重を与えてい
る。[0005] The elastic member 7 is provided with a retainer bearing 4.
A preload in the thrust direction is applied to the bearing device via the shaft.
【０００６】[0006]
【発明が解決しようとする課題】しかしながら、このよ
うな従来の軸受装置にあっては、リテーナベアリング４
が共振を起こした場合、スクイーズフィルムダンパーの
隙間５ａ，５ｂの範囲内でいわゆる振れまわりが生じて
ハウジング８と接触し、この部分が摩耗したりこの部分
から異音が発生するといった問題があった。However, in such a conventional bearing device, the retainer bearing 4 is required.
Causes resonance, so-called whirling occurs within the gaps 5a and 5b of the squeeze film damper and comes into contact with the housing 8, and there is a problem that this portion is worn or noise is generated from this portion. .
【０００７】本発明は、このような従来技術の問題点に
鑑みてなされたものであり、リテーナベアリング周辺部
位の摩耗や異音の発生が防止できる軸受装置を提供する
ことを目的とする。SUMMARY OF THE INVENTION The present invention has been made in view of such problems of the prior art, and has as its object to provide a bearing device capable of preventing the occurrence of wear and abnormal noise around a retainer bearing.
【０００８】[0008]
【課題を解決するための手段】上記目的を達成するため
に、請求項１記載の軸受装置は、軸受のアウターレース
の外周に設けられたリテーナベアリングと、前記リテー
ナベアリングとハウジングとの間に形成されたスクイー
ズフィルムダンパーとを有し、軸受のスラスト方向の予
荷重を弾性体により発生させる軸受装置において、前記
リテーナベアリングと前記弾性体との間に、前記リテー
ナベアリングと当接しかつ前記ハウジングに嵌め合わさ
れた筒状部材が介在されていることを特徴とする。According to a first aspect of the present invention, there is provided a bearing device comprising: a retainer bearing provided on an outer periphery of an outer race of a bearing; and a retainer bearing formed between the retainer bearing and the housing. A squeeze film damper, and a preload in a thrust direction of the bearing is generated by an elastic body. In the bearing device, between the retainer bearing and the elastic body, the retainer bearing is in contact with the retainer bearing and is fitted to the housing. The combined tubular member is interposed.
【０００９】この請求項１記載の軸受装置では、リテー
ナベアリングと弾性体との間に、リテーナベアリングと
当接し、かつハウジングに嵌め合わされた筒状部材が介
在されているので、弾性体の弾性力は筒状部材を介して
リテーナベアリングからアウターレースに伝えられる。
また、筒状部材はハウジングに嵌め合わされているので
ラジアル方向の動きが規制されるが、この筒状部材にリ
テーナベアリングが当接しているので、当該リテーナベ
アリングもラジアル方向の動きが規制されることにな
る。したがって、回転軸が高速回転しても、リテーナベ
アリングの振れ廻りが筒状部材によって拘束され、これ
によりリテーナベアリングとハウジングとの接触が原因
で生じる異音の発生が防止される。また、リテーナベア
リングの振れ廻りが拘束されるので、スクイーズフィル
ムダンパの機能が適正に発揮されることにもなる。In the bearing device according to the first aspect of the present invention, since the cylindrical member abutting on the retainer bearing and being fitted into the housing is interposed between the retainer bearing and the elastic body, the elastic force of the elastic body is provided. Is transmitted from the retainer bearing to the outer race via the tubular member.
Further, since the cylindrical member is fitted in the housing, the movement in the radial direction is restricted. However, since the retainer bearing is in contact with the cylindrical member, the movement of the retainer bearing in the radial direction is also restricted. become. Therefore, even if the rotating shaft rotates at a high speed, the swirling of the retainer bearing is restrained by the cylindrical member, thereby preventing generation of abnormal noise caused by contact between the retainer bearing and the housing. In addition, since the swirling of the retainer bearing is restricted, the function of the squeeze film damper is properly exhibited.
【００１０】請求項１記載の軸受装置において、リテー
ナベアリングや筒状部材の具体的構造は特に限定されな
いが、請求項２記載の軸受装置は、前記リテーナベアリ
ングは回転軸に対して直角に形成された外周円盤部を有
し、前記ハウジングは前記回転軸と同軸に形成された円
筒部を有し、前記筒状部材は、前記リテーナベアリング
の外周円盤部に当接する円盤部と、前記ハウジングの円
筒部に嵌め合わされる円筒部とを有することを特徴とす
る。[0010] In the bearing device according to the first aspect, the specific structure of the retainer bearing and the cylindrical member is not particularly limited, but in the bearing device according to the second aspect, the retainer bearing is formed at right angles to a rotating shaft. The housing has a cylindrical portion formed coaxially with the rotating shaft, the cylindrical member has a disk portion that abuts against the outer peripheral disk portion of the retainer bearing, and a cylinder of the housing. And a cylindrical portion fitted to the portion.
【００１１】この請求項２記載の軸受装置では、筒状部
材の円盤部は回転軸に直角に形成され、同じく回転軸に
直角に形成されたリテーナベアリングの外周円盤部に当
接する。すなわち、これらの当接面は回転軸に直角に位
置し、この当接面においてリテーナベアリングと筒状部
材は回転軸に直角方向にのみ摺動可能となる。したがっ
て、回転軸が高速回転しても、リテーナベアリングの振
れ廻りが筒状部材によって回転軸に直角な方向にのみ許
容され、これによりリテーナベアリングとハウジングと
の接触が原因で生じる異音の発生が防止される。また、
リテーナベアリングの振れ廻りが回転軸に直角な方向に
のみ許容されるので、スクイーズフィルムダンパの機能
が適正に発揮されることにもなる。In the bearing device according to the second aspect, the disk portion of the cylindrical member is formed at right angles to the rotating shaft, and abuts against the outer peripheral disk portion of the retainer bearing also formed at right angles to the rotating shaft. That is, these contact surfaces are located at right angles to the rotation axis, and the retainer bearing and the cylindrical member can slide on this contact surface only in the direction perpendicular to the rotation axis. Therefore, even if the rotating shaft rotates at a high speed, the swiveling of the retainer bearing is allowed only in a direction perpendicular to the rotating shaft by the cylindrical member, thereby generating abnormal noise caused by the contact between the retainer bearing and the housing. Is prevented. Also,
Since the swing of the retainer bearing is allowed only in the direction perpendicular to the rotation axis, the function of the squeeze film damper can be properly exhibited.
【００１２】請求項１記載の軸受装置において、筒状部
材とハウジングとの嵌め合い寸法は特に限定されない
が、請求項３記載の軸受装置は、前記筒状部材と前記ハ
ウジングとの嵌め合いは、前記リテーナベアリングと前
記ハウジングとの隙間よりも小さいことを特徴とする。
こうすることで、筒状部材とハウジングとの嵌め合い寸
法だけ共振しても、リテーナベアリングはハウジングに
接触することはなく、異音の発生がより防止される。In the bearing device according to the first aspect, the fitting dimension between the cylindrical member and the housing is not particularly limited. However, in the bearing device according to the third aspect, the fitting between the cylindrical member and the housing is: It is characterized by being smaller than a gap between the retainer bearing and the housing.
By doing so, even if the housing resonates by the fitting dimension of the cylindrical member and the housing, the retainer bearing does not contact the housing, and the generation of abnormal noise is further prevented.
【００１３】請求項４記載の軸受装置は、前記筒状部材
と前記ハウジングとの嵌め合い面に潤滑オイルを供給す
る通路を有することを特徴とする。こうすることで、筒
状部材とハウジングとの嵌め合い面の摩擦が低減される
ので、リテーナベアリングのラジアル方向およびスラス
ト方向の動きがスムーズになり、スクイーズフィルムダ
ンパの振動減衰効果がより顕著となる。また、筒状部材
とハウジングとの嵌め合い面のスティック（噛み込み）
が防止されるので、弾性体からのスラスト荷重が軸受に
正確に加わることになる。According to a fourth aspect of the present invention, the bearing device has a passage for supplying lubricating oil to a fitting surface between the cylindrical member and the housing. By doing so, the friction between the fitting surface of the cylindrical member and the housing is reduced, so that the radial and thrust movements of the retainer bearing become smooth, and the vibration damping effect of the squeeze film damper becomes more remarkable. . Also, a stick (biting) on the fitting surface of the cylindrical member and the housing
Therefore, the thrust load from the elastic body is accurately applied to the bearing.
【００１４】請求項５記載の軸受装置は、前記筒状部材
と前記リテーナベアリングとの当接面に潤滑オイルを供
給する通路を有することを特徴とする。こうすること
で、筒状部材とリテーナベアリングとの当接面の摩擦が
低減されるので、リテーナベアリングのラジアル方向の
動きがよりスムーズになり、スクイーズフィルムダンパ
の振動減衰効果がより顕著となる。According to a fifth aspect of the present invention, the bearing device has a passage for supplying lubricating oil to a contact surface between the cylindrical member and the retainer bearing. By doing so, the friction of the contact surface between the cylindrical member and the retainer bearing is reduced, so that the radial movement of the retainer bearing becomes smoother, and the vibration damping effect of the squeeze film damper becomes more remarkable.
【００１５】請求項６記載の軸受装置は、前記筒状部材
と前記ハウジングとの嵌め合い面を前記筒状部材の円筒
部の外周面とし、嵌め合い面のスラスト方向の長さを長
くしたことを特徴とする。筒状部材とハウジングとの嵌
め合い面のスラスト方向の長さを長くすることで、嵌め
合い寸法を多少大きく（緩く）しても筒状部材の振れ廻
りはさほど大きくならない。したがって、筒状部材の寸
法許容範囲を大きく設定することができ、当該筒状部材
の製作が容易となる。According to a sixth aspect of the present invention, in the bearing device, the fitting surface between the cylindrical member and the housing is an outer peripheral surface of the cylindrical portion of the cylindrical member, and the length of the fitting surface in the thrust direction is increased. It is characterized by. By increasing the length of the fitting surface between the tubular member and the housing in the thrust direction, the swirling of the tubular member does not increase so much even if the fitting dimension is slightly increased (loose). Therefore, the dimensional permissible range of the tubular member can be set large, and the production of the tubular member becomes easy.
【００１６】請求項７記載の軸受装置は、前記筒状部材
の材質と前記ハウジングの材質が同一であることを特徴
とする。こうすることで、暖機運転時において筒状部材
とハウジングとの間に熱膨張差がなくなり、その結果、
嵌め合い面の同軸度を維持することができ、ここからの
異音の発生が防止できる。According to a seventh aspect of the present invention, the material of the cylindrical member and the material of the housing are the same. This eliminates the difference in thermal expansion between the tubular member and the housing during the warm-up operation, and as a result,
The coaxiality of the fitting surfaces can be maintained, and the generation of abnormal noise can be prevented.
【００１７】[0017]
【発明の効果】請求項１乃至３記載の軸受装置によれ
ば、筒状部材によってリテーナベアリングの振れまわり
の自由度が拘束されるので、異音の発生を防止すること
ができる。また、スクイーズフィルムダンパをより効果
的に機能させることができ、回転軸の半径方向の振動吸
収効果がより高くなる。According to the bearing device of the first to third aspects, since the degree of freedom of the retainer bearing around the swing is restricted by the cylindrical member, generation of abnormal noise can be prevented. In addition, the squeeze film damper can function more effectively, and the effect of absorbing vibration in the radial direction of the rotating shaft can be further enhanced.
【００１８】請求項４および５記載の軸受装置によれ
ば、スクイーズフィルムダンパの振動減衰効果がより顕
著となり、また、弾性体からのスラスト荷重を軸受によ
り正確に加えることができる。According to the bearing device of the fourth and fifth aspects, the vibration damping effect of the squeeze film damper becomes more remarkable, and the thrust load from the elastic body can be more accurately applied to the bearing.
【００１９】請求項６記載の軸受装置によれば、筒状部
材の嵌め合い寸法の許容範囲を緩和でき、筒状部材の製
造が容易となる。According to the bearing device of the sixth aspect, the allowable range of the fitting dimension of the cylindrical member can be relaxed, and the manufacture of the cylindrical member becomes easy.
【００２０】請求項７記載の軸受装置によれば、暖機運
転時における筒状部材とハウジングとの嵌め合い面から
の異音の発生を防止することができる。According to the bearing device of the seventh aspect, it is possible to prevent the generation of abnormal noise from the fitting surface between the cylindrical member and the housing during the warm-up operation.
【００２１】[0021]
【発明の実施の形態】以下、本発明の実施形態を図面に
基づいて説明する。第１実施形態 図１は本発明の軸受装置の第１実施形態を示す半断面図
であり、本発明の軸受装置をガスタービンエンジンに適
用した具体例である。ガスタービンの高速回転軸１は、
ハウジング８に取り付けられた図示しない軸受により、
スラスト方向の動きを制限された状態で組み付けられて
いる。Embodiments of the present invention will be described below with reference to the drawings. First Embodiment FIG. 1 is a half sectional view showing a first embodiment of the bearing device of the present invention, and is a specific example in which the bearing device of the present invention is applied to a gas turbine engine. The high-speed rotating shaft 1 of the gas turbine
By a bearing (not shown) attached to the housing 8,
Assembled with limited movement in the thrust direction.
【００２２】ハウジング８には、コイルバネからなる弾
性体７、リテーナベアリング４と一体化されたアウタレ
ース２ａ、およびベアリング２が組み付けられ、ナット
３にてインナレース２ｂを回転軸１に締め込むことによ
り、軸受装置が構成される。An elastic body 7 composed of a coil spring, an outer race 2a integrated with a retainer bearing 4, and a bearing 2 are assembled to a housing 8, and the inner race 2b is tightened to the rotating shaft 1 by a nut 3, whereby A bearing device is configured.
【００２３】リテーナベアリング４とハウジング８との
間には隙間５ａが形成され、またリテーナベアリング４
とアウタレース２ａとの間には隙間５ｂが形成されてお
り、潤滑オイル供給孔６から潤滑オイルを供給すること
により、これらの隙間５ａ，５ｂにスクイーズフィルム
ダンパーが形成され、このスクイーズフィルムダンパに
よって高速回転軸１の半径方向の振動が吸収される。A gap 5 a is formed between the retainer bearing 4 and the housing 8.
A gap 5b is formed between the outer race 2a and the outer race 2a. By supplying lubricating oil from the lubricating oil supply hole 6, a squeeze film damper is formed in the gaps 5a and 5b. Radial vibration of the rotating shaft 1 is absorbed.
【００２４】なお、弾性体７は、リテーナベアリング４
を介して軸受装置にスラスト方向の予荷重を与えてい
る。Incidentally, the elastic body 7 is provided with the retainer bearing 4.
A preload in the thrust direction is applied to the bearing device via the shaft.
【００２５】特に本実施形態では、高速回転軸１に対し
て軸対称な形状をなす筒状部材９が、弾性体７とリテー
ナベアリング４との間に設けられている。この筒状部材
９は、回転軸１に対して直角な面をもつ円盤部９ａと、
回転軸１に対して同心状の円筒部９ｂとから構成され、
円盤部９ａがリテーナベアリング４の外周円盤部４ａと
当接し、円筒部９ｂがハウジング８の円筒部８ａに嵌め
合わされている。In particular, in the present embodiment, a cylindrical member 9 having an axisymmetric shape with respect to the high-speed rotating shaft 1 is provided between the elastic body 7 and the retainer bearing 4. The cylindrical member 9 includes a disk portion 9 a having a surface perpendicular to the rotation axis 1,
A cylindrical portion 9b concentric with the rotating shaft 1;
The disk portion 9a contacts the outer peripheral disk portion 4a of the retainer bearing 4, and the cylindrical portion 9b is fitted to the cylindrical portion 8a of the housing 8.
【００２６】円盤部９ａとリテーナベアリング４の外周
円盤部４ａとの当接面はそれぞれ研磨加工され、これに
より、両者４，９は相対的に、回転軸１に対して直角な
方向に容易に移動することができるようになっている。
また、筒状部材９のハウジング８への嵌め合い面９ｃと
なる隙間は、スクイーズフィルムダンパーを構成する隙
間５ａ、５ｂよりも小さい寸法で構成され、筒状部材９
はハウジング８に対して回転軸１の軸方向に移動可能と
されている。The contact surfaces of the disc portion 9a and the outer disc portion 4a of the retainer bearing 4 are respectively polished so that the two 4 and 9 can be relatively easily moved in a direction perpendicular to the rotating shaft 1. You can move.
Further, the gap that forms the fitting surface 9c of the tubular member 9 to the housing 8 has a smaller size than the gaps 5a and 5b that constitute the squeeze film damper.
Is movable in the axial direction of the rotary shaft 1 with respect to the housing 8.
【００２７】次に作用を説明する。軸受のアウターレー
ス２ａに組み付けられたリテーナベアリング４は、当該
リテーナベアリング４の外周円盤部４ａと筒状部材９の
円盤部９ａとの当接構造によって、回転軸１のラジアル
方向の動きが当接面に沿った方向、すなわち回転軸１に
直角な方向に制限され、回転軸１のスラスト方向の動き
が筒状部材９とハウジング８との嵌め合い面９ｃに沿う
方向に制限されている。Next, the operation will be described. The radial movement of the rotary shaft 1 of the retainer bearing 4 mounted on the outer race 2a of the bearing is abutted by the contact structure between the outer peripheral disk portion 4a of the retainer bearing 4 and the disk portion 9a of the cylindrical member 9. The direction along the surface, that is, the direction perpendicular to the rotating shaft 1 is limited, and the movement of the rotating shaft 1 in the thrust direction is limited to the direction along the fitting surface 9c between the cylindrical member 9 and the housing 8.
【００２８】したがって、回転軸１の高速回転によって
リテーナベアリング４が共振しても、当該リテーナベア
リング４の振れ廻りが強制的に押えられる。これによ
り、共振時にリテーナベアリング４がハウジング８に接
触するのが防止され、接触による摩耗や異音の発生が防
止される。Therefore, even if the retainer bearing 4 resonates due to the high-speed rotation of the rotating shaft 1, the swing of the retainer bearing 4 is forcibly suppressed. This prevents the retainer bearing 4 from coming into contact with the housing 8 at the time of resonance, thereby preventing wear and abnormal noise due to the contact.
【００２９】また従来の軸受装置においては、弾性体７
の両端面の平行度が出ていないと、スクイーズフィルム
ダンパの隙間を回転軸１に対して同芯状に維持すること
ができなかったが、本実施形態では、筒状部材９の円筒
部９ｂとハウジング８の円筒部８ａとの嵌め合い寸法、
筒状部材９およびリテーナベアリング４の製造精度を確
保すれば、スクイーズフィルムダンパの隙間の同芯を保
つことができるため、従来に比べ、スクイーズフィルム
ダンパの振動減衰効果をより向上させることができ、回
転軸１の振動抑制がより高くなる。In the conventional bearing device, the elastic member 7
If the degree of parallelism of the both end faces is not sufficient, the gap of the squeeze film damper cannot be maintained concentric with the rotating shaft 1. However, in the present embodiment, the cylindrical portion 9b of the cylindrical member 9 is not provided. Fitting dimension between the cylindrical portion 8a of the housing 8 and
If the manufacturing accuracy of the tubular member 9 and the retainer bearing 4 is ensured, the concentricity of the gap of the squeeze film damper can be maintained, so that the vibration damping effect of the squeeze film damper can be further improved as compared with the related art. Vibration suppression of the rotating shaft 1 becomes higher.
【００３０】第２実施形態 図２は本発明の軸受装置の第２実施形態を示す半断面図
であり、上述した第１実施形態に比べ、リテーナベアリ
ング４の外周円盤部４ａと筒状部材９の円盤部９ａとの
当接面に潤滑オイルを供給するための通路１１、および
筒状部材９の円筒部９ｂとハウジング８の円筒部８ａと
の嵌め合い面９ｃに潤滑オイルを供給する通路１０を有
する点が相違している。これらの通路１０，１１は、潤
滑オイル供給孔６に連通されている。 Second Embodiment FIG. 2 is a half sectional view showing a bearing device according to a second embodiment of the present invention. Compared with the first embodiment described above, the outer peripheral disk portion 4a and the cylindrical member 9 of the retainer bearing 4 are different from each other. A passage 11 for supplying lubricating oil to a contact surface of the cylindrical member 9 with the disc portion 9a, and a passage 10 for supplying lubricating oil to a fitting surface 9c of the cylindrical portion 9b of the cylindrical member 9 and the cylindrical portion 8a of the housing 8. Is different. These passages 10 and 11 communicate with the lubricating oil supply hole 6.
【００３１】通路１１から潤滑オイルを供給すること
で、リテーナベアリング４と筒状部材９との当接面の摩
擦が低減され、また、通路１０から潤滑オイルを供給す
ることで、筒状部材９とハウジング８との嵌め合い面９
ｃの摩擦が低減される。これにより、リテーナベアリン
グ４の半径方向および軸方向の動きがスムーズになり、
スクイーズフィルムダンパの振動減衰効果がより効果的
に発揮され、しかも嵌め合い面スティックが防止される
ので弾性体７によるスラスト荷重がより正確に加えられ
ることになる。By supplying the lubricating oil from the passage 11, the friction of the contact surface between the retainer bearing 4 and the cylindrical member 9 is reduced, and by supplying the lubricating oil from the passage 10, the cylindrical member 9 is supplied. Mating surface 9 between housing and housing 8
c is reduced. Thereby, the radial and axial movements of the retainer bearing 4 become smooth,
Since the vibration damping effect of the squeeze film damper is more effectively exerted, and the fitting surface stick is prevented, the thrust load by the elastic body 7 is more accurately applied.
【００３２】第３実施形態 図３は本発明の軸受装置の第３実施形態を示す半断面図
であり、上述した第１実施形態に比べ、筒状部材９とハ
ウジング８との嵌め合い面９ｃを筒状部材９の外周側９
ｃとし、かつ嵌め合い面９ｃの軸方向の長さを長くした
点が相違している。 Third Embodiment FIG. 3 is a half sectional view showing a bearing device according to a third embodiment of the present invention. Compared with the first embodiment described above, a fitting surface 9c of the cylindrical member 9 and the housing 8 is provided. To the outer peripheral side 9 of the cylindrical member 9
c, and the length of the fitting surface 9c in the axial direction is different.
【００３３】その他の構成は第１実施形態と同様である
ためその説明は省略するが、筒状部材９とハウジング８
との嵌め合い面９ｃの軸方向の長さを長くすることによ
り、嵌め合い面９ｃの隙間寸法を大きく（緩く）して
も、嵌め合い面９ｃの軸方向の長さが長い分だけ筒状部
材９の振れ廻りが抑えるられる。したがって、筒状部材
９およびハウジング８の嵌め合い面９ｃに対する製造許
容誤差を大きくすることができ、筒状部材９および／ま
たはハウジング８の製作が容易になる。The other structure is the same as that of the first embodiment, and the description thereof is omitted.
By increasing the length of the fitting surface 9c in the axial direction, even if the clearance dimension of the fitting surface 9c is increased (loosely), the cylindrical shape is increased by the length of the fitting surface 9c in the axial direction. The whirling of the member 9 is suppressed. Therefore, the manufacturing tolerance for the fitting surface 9c of the tubular member 9 and the housing 8 can be increased, and the fabrication of the tubular member 9 and / or the housing 8 becomes easy.
【００３４】第４実施形態 図４は本発明の軸受装置の第４実施形態を示す半断面図
であり、上述した第３実施形態に比べ、リテーナベアリ
ング４の外周円盤部４ａと筒状部材９の円盤部９ａとの
当接面に潤滑オイルを供給するための通路１１、および
筒状部材９の円筒部９ｂとハウジング８の円筒部８ａと
の嵌め合い面９ｃに潤滑オイルを供給する通路１０を有
する点が相違している。これらの通路１０，１１は、潤
滑オイル供給孔６に連通されている。 Fourth Embodiment FIG. 4 is a half sectional view showing a bearing device according to a fourth embodiment of the present invention. In comparison with the above-described third embodiment, the outer peripheral disk portion 4a and the cylindrical member 9 of the retainer bearing 4 are different from each other. A passage 11 for supplying lubricating oil to a contact surface of the cylindrical member 9 with the disc portion 9a, and a passage 10 for supplying lubricating oil to a fitting surface 9c of the cylindrical portion 9b of the cylindrical member 9 and the cylindrical portion 8a of the housing 8. Is different. These passages 10 and 11 communicate with the lubricating oil supply hole 6.
【００３５】通路１１から潤滑オイルを供給すること
で、リテーナベアリング４と筒状部材９との当接面の摩
擦が低減され、また、通路１０から潤滑オイルを供給す
ることで、筒状部材９とハウジング８との嵌め合い面９
ｃの摩擦が低減される。これにより、リテーナベアリン
グ４の半径方向および軸方向の動きがスムーズになり、
スクイーズフィルムダンパの振動減衰効果がより効果的
に発揮され、しかも嵌め合い面スティックが防止される
ので弾性体７によるスラスト荷重がより正確に加えられ
ることになる。By supplying the lubricating oil from the passage 11, the friction of the contact surface between the retainer bearing 4 and the cylindrical member 9 is reduced, and by supplying the lubricating oil from the passage 10, the cylindrical member 9 is supplied. Mating surface 9 between housing and housing 8
c is reduced. Thereby, the radial and axial movements of the retainer bearing 4 become smooth,
Since the vibration damping effect of the squeeze film damper is more effectively exerted, and the fitting surface stick is prevented, the thrust load by the elastic body 7 is more accurately applied.
【００３６】なお、以上説明した実施形態は、本発明の
理解を容易にするために記載されたものであって、本発
明を限定するために記載されたものではない。したがっ
て、上記の実施形態に開示された各要素は、本発明の技
術的範囲に属する全ての設計変更や均等物をも含む趣旨
である。The embodiments described above are described for facilitating the understanding of the present invention, and are not described for limiting the present invention. Therefore, each element disclosed in the above embodiment is intended to include all design changes and equivalents belonging to the technical scope of the present invention.
【００３７】たとえば、上述した各実施形態において、
筒状部材９の材質とハウジング８の材料とを同一とすれ
ば、これら筒状部材９とハウジング８の暖気運転時の熱
膨張差がなくなるので、嵌め合い面９ｃの同軸度が保た
れ、異音の発生がより防止される。For example, in each of the above embodiments,
If the material of the tubular member 9 and the material of the housing 8 are the same, there is no difference in thermal expansion between the tubular member 9 and the housing 8 during the warm-up operation, so that the coaxiality of the fitting surface 9c is maintained, The generation of sound is further prevented.
【図１】本発明の軸受装置の第１実施形態を示す半断面
図である。FIG. 1 is a half sectional view showing a first embodiment of a bearing device of the present invention.
【図２】本発明の軸受装置の第２実施形態を示す半断面
図である。FIG. 2 is a half sectional view showing a second embodiment of the bearing device of the present invention.
【図３】本発明の軸受装置の第３実施形態を示す半断面
図である。FIG. 3 is a half sectional view showing a third embodiment of the bearing device of the present invention.
【図４】本発明の軸受装置の第４実施形態を示す半断面
図である。FIG. 4 is a half sectional view showing a fourth embodiment of the bearing device of the present invention.
【図５】従来のガスタービンエンジン用軸受装置を示す
半断面図である。FIG. 5 is a half sectional view showing a conventional bearing device for a gas turbine engine.
１…回転軸 ２…ベアリング ２ａ…アウターレース ２ｂ…インナレース ３…ナット ４…リテーナベアリング ４ａ…外周円盤部 ５ａ，５ｂ…スクイーズフィルムダンパ ６…潤滑オイル供給孔 ７…弾性体 ８…ハウジング ８ａ…円筒部 ９…筒状部材 ９ａ…円盤部 ９ｂ…円筒部 ９ｃ…嵌め合い面 １０，１１…通路 DESCRIPTION OF SYMBOLS 1 ... Rotating shaft 2 ... Bearing 2a ... Outer race 2b ... Inner race 3 ... Nut 4 ... Retainer bearing 4a ... Peripheral disk part 5a, 5b ... Squeeze film damper 6 ... Lubricating oil supply hole 7 ... Elastic body 8 ... Housing 8a ... Cylindrical Part 9: cylindrical member 9a: disk part 9b: cylindrical part 9c: fitting surface 10, 11: passage
Claims (7)
リテーナベアリングと、前記リテーナベアリングとハウ
ジングとの間に形成されたスクイーズフィルムダンパー
とを有し、軸受のスラスト方向の予荷重を弾性体により
発生させる軸受装置において、 前記リテーナベアリングと前記弾性体との間に、前記リ
テーナベアリングと当接しかつ前記ハウジングに嵌め合
わされた筒状部材が介在されていることを特徴とする軸
受装置。1. A bearing having a retainer bearing provided on the outer periphery of an outer race of a bearing, and a squeeze film damper formed between the retainer bearing and a housing. In the bearing device to be generated, a cylindrical member that is in contact with the retainer bearing and fitted to the housing is interposed between the retainer bearing and the elastic body.
直角に形成された外周円盤部を有し、前記ハウジングは
前記回転軸と同軸に形成された円筒部を有し、 前記筒状部材は、前記リテーナベアリングの外周円盤部
に当接する円盤部と、前記ハウジングの円筒部に嵌め合
わされる円筒部とを有することを特徴とする請求項１記
載の軸受装置。2. The retainer bearing has an outer peripheral disk portion formed at right angles to a rotating shaft, the housing has a cylindrical portion formed coaxially with the rotating shaft, and the tubular member has 2. The bearing device according to claim 1, further comprising: a disk portion that contacts an outer peripheral disk portion of the retainer bearing; and a cylindrical portion that is fitted into the cylindrical portion of the housing. 3.
いは、前記リテーナベアリングと前記ハウジングとの隙
間よりも小さいことを特徴とする請求項１または２記載
の軸受装置。3. The bearing device according to claim 1, wherein the fitting between the tubular member and the housing is smaller than a gap between the retainer bearing and the housing.
い面に潤滑オイルを供給する通路を有することを特徴と
する請求項１〜３の何れかに記載の軸受装置。4. The bearing device according to claim 1, further comprising a passage for supplying lubricating oil to a fitting surface between the cylindrical member and the housing.
の当接面に潤滑オイルを供給する通路を有することを特
徴とする請求項１〜４の何れかに記載の軸受装置。5. The bearing device according to claim 1, further comprising a passage for supplying lubricating oil to a contact surface between said cylindrical member and said retainer bearing.
い面を前記筒状部材の円筒部の外周面とし、嵌め合い面
のスラスト方向の長さを長くしたことを特徴とする請求
項１〜５の何れかに記載の軸受装置。6. A fitting surface between the tubular member and the housing is an outer peripheral surface of a cylindrical portion of the tubular member, and a length of the fitting surface in a thrust direction is increased. The bearing device according to any one of claims 1 to 5.
質が同一であることを特徴とする請求項１〜６の何れか
に記載の軸受装置。7. The bearing device according to claim 1, wherein the material of the cylindrical member and the material of the housing are the same.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP9227101A JPH1162953A (en) | 1997-08-08 | 1997-08-08 | Bearing device |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP9227101A JPH1162953A (en) | 1997-08-08 | 1997-08-08 | Bearing device |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH1162953A true JPH1162953A (en) | 1999-03-05 |
Family
ID=16855508
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP9227101A Pending JPH1162953A (en) | 1997-08-08 | 1997-08-08 | Bearing device |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH1162953A (en) |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6809898B1 (en) * | 2000-01-13 | 2004-10-26 | Maxtor Corporation | Disk drive rocking mode vibration damper |
| US7798720B1 (en) * | 2006-11-16 | 2010-09-21 | Florida Turbine Technologies, Inc. | Squeeze film damper with highly variable support stiffness |
| US9470262B2 (en) | 2014-03-19 | 2016-10-18 | Rolls-Royce Plc | Bearing arrangement and method |
| EP2978954A4 (en) * | 2013-03-28 | 2016-11-30 | United Technologies Corp | Rear bearing sleeve for gas turbine auxiliary power unit |
| EP3284918A1 (en) * | 2016-08-18 | 2018-02-21 | United Technologies Corporation | Resilient bearing mount with integral damper fluid passage for a geared turbofan engine |
| EP3401514A1 (en) * | 2017-05-11 | 2018-11-14 | United Technologies Corporation | Fluid damping structure ring and method of fluid damping |
| EP3597946A1 (en) * | 2018-07-20 | 2020-01-22 | United Technologies Corporation | Axially spaced restricted damper |
-
1997
- 1997-08-08 JP JP9227101A patent/JPH1162953A/en active Pending
Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6809898B1 (en) * | 2000-01-13 | 2004-10-26 | Maxtor Corporation | Disk drive rocking mode vibration damper |
| US7798720B1 (en) * | 2006-11-16 | 2010-09-21 | Florida Turbine Technologies, Inc. | Squeeze film damper with highly variable support stiffness |
| EP2978954A4 (en) * | 2013-03-28 | 2016-11-30 | United Technologies Corp | Rear bearing sleeve for gas turbine auxiliary power unit |
| US10329953B2 (en) | 2013-03-28 | 2019-06-25 | United Technologies Corporation | Rear bearing sleeve for gas turbine auxiliary power unit |
| US9470262B2 (en) | 2014-03-19 | 2016-10-18 | Rolls-Royce Plc | Bearing arrangement and method |
| US9658132B2 (en) | 2014-03-19 | 2017-05-23 | Rolls-Royce Plc | Bearing arrangement and method |
| EP3284918A1 (en) * | 2016-08-18 | 2018-02-21 | United Technologies Corporation | Resilient bearing mount with integral damper fluid passage for a geared turbofan engine |
| US10436065B2 (en) | 2016-08-18 | 2019-10-08 | United Technologies Corporation | Resilient bearing mount with integral damper fluid passage for a geared turbofan engine |
| EP3401514A1 (en) * | 2017-05-11 | 2018-11-14 | United Technologies Corporation | Fluid damping structure ring and method of fluid damping |
| US10662811B2 (en) | 2017-05-11 | 2020-05-26 | Raytheon Technologies Corporation | Fluid damping structure ring and method of fluid damping |
| EP3597946A1 (en) * | 2018-07-20 | 2020-01-22 | United Technologies Corporation | Axially spaced restricted damper |
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