JPS616424A - Bearing structure - Google Patents
Bearing structureInfo
- Publication number
- JPS616424A JPS616424A JP59125676A JP12567684A JPS616424A JP S616424 A JPS616424 A JP S616424A JP 59125676 A JP59125676 A JP 59125676A JP 12567684 A JP12567684 A JP 12567684A JP S616424 A JPS616424 A JP S616424A
- Authority
- JP
- Japan
- Prior art keywords
- support sleeve
- rotating shaft
- fixed bearing
- bearing body
- contact
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
- F01D25/16—Arrangement of bearings; Supporting or mounting bearings in casings
- F01D25/162—Bearing supports
- F01D25/164—Flexible supports; Vibration damping means associated with 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
- F16C19/04—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly
- F16C19/06—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly with a single row or balls
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2360/00—Engines or pumps
- F16C2360/23—Gas turbine engines
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Support Of The Bearing (AREA)
Abstract
Description
【発明の詳細な説明】
（産業上の利用分野）
この発明は、回転軸のラジアル方向の振動を減衰させる
軸受構造に関する。DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to a bearing structure that damps vibrations in the radial direction of a rotating shaft.
（従来技術）
たとえば、ガスタービンにおけるように、高速回転軸系
を有するものでは、高速回転する回転軸が、その常用回
転数の範囲に詔いて危険な回転状態（共振状態）となら
ないように、支持配性（ばね定数）を低く設定しておく
ことと、回転軸に発生する振動を減衰し、高速回転を常
に安定化することが必要である。(Prior art) For example, in a gas turbine that has a high-speed rotating shaft system, in order to prevent the high-speed rotating shaft from entering a dangerous rotational state (resonance state) within its normal rotational speed range, It is necessary to set the support arrangement (spring constant) low, damp vibrations generated in the rotating shaft, and always stabilize high-speed rotation.
こうした２つの条件を満足させるため、たとえば、第１
図に示す軸受構造をとるものがある。この方式は、回転
軸１８の外局に設けた軸受ベアリング１７と、回転軸１
８の外周に配した固定軸受体１１との間に、円筒形の支
持スリーブ２１を設け、その支持スリーブ２１を、固定
側に取り付けられ、片持状に延出する支持ケージ２１ａ
、の先端部に一体的に形成することによって、匹いばね
定数のもとで回転軸１８を支持するとともに、支持スリ
ーブ２１の外周に、周溝２５を形成しておき、その周溝
２５に、固定軸受体１１のオイル供給孔２６から給油し
て、支持スリーブ２１と固定軸受体１１との間に、油膜
ダンパを形成したものである。In order to satisfy these two conditions, for example, the first
Some bearings have the structure shown in the figure. This system uses a bearing 17 provided at the outer station of the rotating shaft 18 and a bearing 17 provided at the outer station of the rotating shaft 18.
A cylindrical support sleeve 21 is provided between the fixed bearing body 11 arranged on the outer periphery of the support cage 21a, which is attached to the fixed side and extends in a cantilevered manner.
, to support the rotating shaft 18 under a comparable spring constant, and a circumferential groove 25 is formed on the outer periphery of the support sleeve 21. , an oil film damper is formed between the support sleeve 21 and the fixed bearing body 11 by supplying oil from the oil supply hole 26 of the fixed bearing body 11.
この方式によれば、上記２つの条件は満足する５ Ｖ）
（Ｑ、支持スリーブ２１が支持ケージ２１ａつきの大
きいものとなるため、大きい組込スペースを必要とする
点で不利であるとともに、油膜ダンパのための油圧シス
テムを必要とする点でも不利である。According to this method, the above two conditions are satisfied (5 V)
(Q) Since the support sleeve 21 is large with a support cage 21a, it is disadvantageous in that it requires a large installation space, and it is also disadvantageous in that it requires a hydraulic system for the oil film damper.
他の方式として、第２図のように、幅方向の両側部に、
Ｕ字切欠状の溝２７と、Ｌ字形の立上り突起２８とを、
交互に多数配列してなる支持スリーブ２１を、第８図に
示すように、軸受ベアリング１７と固定軸受体１１間に
嵌合したものもある。As another method, as shown in Figure 2, on both sides in the width direction,
The U-shaped notch-shaped groove 27 and the L-shaped rising protrusion 28,
In some cases, a plurality of support sleeves 21 arranged alternately are fitted between the bearing 17 and the fixed bearing body 11, as shown in FIG.
この方式では、組付スペースが、第１図の軸受構造によ
るものに比べて小さくてすみ、しかも、いわゆる機械式
ダンパによってｇ衰機構を構成する点で、油圧システム
も要らず、有利であるが、支持スリーブ２１と固定軸受
体１１とは、多数の立上り突起２８を介して互いに接触
すること、ならびに、支持スリーブ２１と軸受ベアリン
グ１７とが、支持スリーブ２１の内周全長にわたって形
成された突条リング２９を介して接触することにより、
減衰機能が今一つ効果的に果せない不利がある。This method requires less assembly space than the bearing structure shown in Fig. 1, and is advantageous in that the g-damping mechanism is composed of a so-called mechanical damper, and no hydraulic system is required. , the support sleeve 21 and the fixed bearing body 11 are in contact with each other via a number of rising protrusions 28, and the support sleeve 21 and the bearing 17 are in contact with each other through a protrusion formed over the entire inner circumference of the support sleeve 21. By contacting via ring 29,
There is a disadvantage that the damping function cannot be achieved very effectively.
（発明の目的）
この発明は、上記問題に艦みてなされたもので、回転軸
のラジアル方向の振動をより効果的に減衰させることを
目的とする。(Object of the Invention) The present invention was made in view of the above problem, and an object of the present invention is to more effectively damp vibrations in the radial direction of a rotating shaft.
（発明の構成）
上記目的を達成するため、この発明は、回転軸とその回
転軸を支持する固定軸受体との内外間に、回転軸のラジ
アル荷重に応じて弾性変形自在な支持スリーブを嵌合し
、上記支持スリーブと回転軸側、ならびに、支持スリー
ブと固定軸受体の各内外間が、それぞれ周方向に特定さ
れた８点以上の接触点において接触するとともに、支持
スリーブと回転軸側間の接触点に対し、支持スリーブと
固定軸受体間の接触点を、周方向の異なる角度位置に配
置することにより、支持スリーブが摩擦によるダンピン
グ機能を発揮して、上記振動を効果的に減衰するように
しである。(Structure of the Invention) In order to achieve the above object, the present invention provides a support sleeve that is elastically deformable according to the radial load of the rotating shaft and is fitted between the inner and outer sides of a rotating shaft and a fixed bearing body that supports the rotating shaft. The supporting sleeve and the rotating shaft side, and the supporting sleeve and the fixed bearing body are in contact at eight or more contact points specified in the circumferential direction, respectively, and the supporting sleeve and the rotating shaft side are in contact with each other at eight or more contact points specified in the circumferential direction. By arranging the contact points between the support sleeve and the fixed bearing body at different angular positions in the circumferential direction, the support sleeve exerts a damping function due to friction, effectively damping the vibrations mentioned above. That's how it is.
（実施例） 以下、この発明の実施例を図面にしたがって説明する。(Example) Embodiments of the present invention will be described below with reference to the drawings.
第４図はジェットエンジン内のタービンについての一例
であり、タービン出口路１の内周を形成する内周筒２の
前側には、タービン羽根８が回転自在に配置される一方
、内周筒２の内周部には、第１軸受ボデイ４が固定され
ている。この第１軸受ボデイ４のタービン羽根８側であ
る前端面には、環状のパツキン２５を介して第２軸受ボ
デイ６が止着具（ボルト）７によって取り付けられてい
る。FIG. 4 shows an example of a turbine in a jet engine. Turbine blades 8 are rotatably disposed on the front side of an inner cylinder 2 forming the inner periphery of the turbine outlet passage 1, while the inner cylinder 2 A first bearing body 4 is fixed to the inner peripheral portion of the bearing body 4 . A second bearing body 6 is attached to the front end surface of the first bearing body 4 on the turbine blade 8 side with a fastener (bolt) 7 via an annular packing 25 .
この第２軸受ボデイ６は、前部に取付フランジ８つきの
円錐部９を、また、後部に、円筒部１０を有するものと
されるとともに、上記円筒ｓ１０の内周に、断面り字形
で円筒状に形成した固定軸受体１１を嵌合するとともに
、この固定軸受体１１に、その前側から断面り字形の抑
えリング１２を当てつけて、抜止リング１８によって固
定軸受体１１を固定しである。また、固定軸受体１１の
内周には、アウタレース１４と、インナレース１５、お
よび、支持ローラ１６からなる軸受ベアリング１７が嵌
合され、この軸受ベアリング１７の内局を介して、ター
ビン羽根８の支持軸である回転軸１８が高速で回転され
るように支持されている。なお、１９は、スペーサ、２
ｏは、ナツトである。The second bearing body 6 has a conical part 9 with a mounting flange 8 at the front and a cylindrical part 10 at the rear. A fixed bearing body 11 formed as shown in FIG. Furthermore, a bearing 17 consisting of an outer race 14 , an inner race 15 , and a support roller 16 is fitted into the inner circumference of the fixed bearing body 11 . A rotating shaft 18, which is a supporting shaft, is supported to rotate at high speed. In addition, 19 is a spacer, 2
o is nut.
上記のように構成された軸受構造には、軸受ベアリング
（回転軸側）１７と、固定軸受体１１との間に、軸受ベ
アリング１７とほぼ同幅の支持スリーブ２１が嵌合され
てあり、この場合、支持スリーブ２１は、第５図に示す
ように、円筒部２２と、内側接点部２８、および、外側
接点ｓ２４とを有する。上記円筒ｓ２２は、第４図の回
転軸１８からのラジアル荷重に応じて弾性変形自在な薄
板製とされ、また、内側接点部２８と、外側接点部２４
とは、それぞれ４Ｉ！ｉｌ所づつ円筒部２２に突設され
、それらが周方向に４５度ごとに交互に内外をなして配
置されている。な＃、この支持スリーブ２１は、固定軸
受体１１に対して回り止めされているが、この場合の回
り止め手段は、ピンなどの回り止め部材によるものと、
外側接点部２４と固定軸受体１１との嵌合力を利用した
ものとがある。In the bearing structure configured as described above, a support sleeve 21 having approximately the same width as the bearing 17 is fitted between the bearing (rotating shaft side) 17 and the fixed bearing body 11. In this case, the support sleeve 21 has a cylindrical portion 22, an inner contact portion 28, and an outer contact point s24, as shown in FIG. The cylinder s22 is made of a thin plate that can be elastically deformed according to the radial load from the rotating shaft 18 in FIG.
Each of them is 4I! They project from the cylindrical portion 22 at different locations, and are arranged alternately inside and outside every 45 degrees in the circumferential direction. The support sleeve 21 is prevented from rotating with respect to the fixed bearing body 11, but the rotation preventing means in this case may be a rotation preventing member such as a pin,
There is one that utilizes the fitting force between the outer contact portion 24 and the fixed bearing body 11.
したがって、上記構成では、回転軸１８が回転した状態
に詔いて、ラジアル方向に振動がない場合には、第５図
に示すように、回転軸】８の中心０が、固定軸受体１１
の中心に！致しているが、回転軸１８がそのもつアンバ
ランスなどによって、ラジアル荷重（振動）を発生して
いる場合には、第６図に示すように、回転軸１８の中心
Ｏが、固定軸受体１１の中心からずれることになる。そ
の場合、たとえば、第６図矢印Ｒ方向に回転＃１１８が
ラジアル荷重を生じたとすると、その力は、支持スリー
ブ２１に作用し、その際、支持スリーブ２１は、内側接
点部２３と外側接点部２４とが互いに周方向においてず
れた配置とされているので、第６図２点鎖線で示すよう
に、外側接点部２４を支点として弾性変形し、その変形
にともなって、軸受ベアリング１７である回転軸１８側
の外周と、支持スリーブ２１の内側接点部２８とが、相
対的に微少のすべりが発生する。そうした作用は、回転
軸１８の１回転にともなって同様に生じ、つまり、上記
ラジアル荷重の方向が回転軸１８の回転にともなって変
化するとともに１上記すべりが繰り返し発生することに
より、振動エネルギが、すべり摩擦による発熱という形
で吸収される。もちろん、上記実施例のように、支持ス
リーブ２１に設りた内側接点部２８と外側接点部２４と
を周方向に互いにずらせつつ分散状に配置し、かつ、そ
れら両接点部２８．２４間を薄く形成しであるので、支
持スリーブ２１のばね定数が低くなって、回転軸１８の
危険速度が常用回転数範囲内に入らないこととなる。Therefore, in the above configuration, when the rotating shaft 18 is in a rotated state and there is no vibration in the radial direction, the center 0 of the rotating shaft 8 is located at the fixed bearing body 11, as shown in FIG.
In the center of! However, if the rotating shaft 18 is generating a radial load (vibration) due to its unbalance, etc., the center O of the rotating shaft 18 will be aligned with the fixed bearing body 11, as shown in FIG. will be shifted from the center of In that case, for example, if rotation #118 generates a radial load in the direction of arrow R in FIG. 24 are arranged so as to be offset from each other in the circumferential direction, the outer contact portion 24 is elastically deformed using the outer contact portion 24 as a fulcrum, as shown by the two-dot chain line in FIG. A small amount of relative slippage occurs between the outer periphery on the shaft 18 side and the inner contact portion 28 of the support sleeve 21 . Such an effect occurs in the same way as the rotating shaft 18 rotates. In other words, the direction of the radial load changes with the rotation of the rotating shaft 18, and the above-mentioned slip occurs repeatedly, so that the vibration energy is It is absorbed in the form of heat generated by sliding friction. Of course, as in the above embodiment, the inner contact portion 28 and the outer contact portion 24 provided on the support sleeve 21 are arranged in a dispersed manner while being shifted from each other in the circumferential direction, and the contact portions 28 and 24 are arranged in a dispersed manner. Since it is formed thin, the spring constant of the support sleeve 21 becomes low, and the critical speed of the rotating shaft 18 does not fall within the normal rotational speed range.
なお、第７図に示すように、支持スリーブ２１を周方向
に波形の筒体とし、その波状谷部を、内側接点部２３と
し、波状山部を、外側接点部２４として形成してもよい
。また、上記では、内側。Incidentally, as shown in FIG. 7, the support sleeve 21 may be formed into a circumferentially corrugated cylindrical body, with the wavy troughs serving as the inner contact portions 23 and the wavy peaks serving as the outer contact portions 24. . Also, above, inside.
外側各接点［２８，２４を、支持スリーブ２１に形成し
たが、第８図に示すように、内側接点部２８を、軸受ベ
アリング１７に、外側接点部２４を、固定軸受体１１に
形成し・たものでもよい。この場合、いずれか一方の接
点部２８または２４を、支持スリーブ２１に形成するこ
ともある。さらに、上記実施例では、回転軸を中心に、
また、固定軸受体を外周に配したが、回転軸を筒体とし
て外周に配したものにもこの発明は適用される。The outer contacts [28, 24 were formed on the support sleeve 21, but as shown in FIG. It may also be something you have. In this case, either one of the contact portions 28 or 24 may be formed on the support sleeve 21. Furthermore, in the above embodiment, centering around the rotation axis,
Furthermore, although the fixed bearing body is arranged on the outer periphery, the present invention is also applicable to those in which the rotating shaft is arranged as a cylinder on the outer periphery.
（発明の効果）
以上説明したように、この発明によれば、支持スリーブ
が摩朧によるダンピング機能を発揮して、回転軸の振動
を効果的に減衰し、しかも、支持スリーブを、小スペー
スのもとに組み込む°ことができるだけでなく、摩擦に
よるダンピング機能を支持スリーブ自体が発揮するので
、油圧システムも不要となる。(Effects of the Invention) As explained above, according to the present invention, the support sleeve exhibits a damping function by damping, effectively damping vibrations of the rotating shaft, and moreover, the support sleeve can be installed in a small space. Not only can it be integrated into the original structure, but the support sleeve itself performs its own frictional damping function, eliminating the need for a hydraulic system.
第１図はケージ型支持機構を有する従来の軸受構造を示
す断面図、第２図は支持スリーブを示す斜視図、第３図
は機械式ダンパを有する軸受構造を示す断面図、第４図
はこの発明の一実施例を示す装置要部の断面図、第５図
は第４図ｖ−ｖ線断面図、第６図は摩擦によるダンピン
グ機能を示す断面図、第７図は波形支持スリーブの一例
を示す断面図、第８図は内側接点部と外側接点部を支持
スリーブ以外の個所に形成した他の一例を示す断面図で
ある。
１１・・・固定軸受体、１８・・・回転軸、２１・・・
支持スリーブ、２３・・内側接点部、２４・・・外側接
点部。Fig. 1 is a sectional view showing a conventional bearing structure with a cage type support mechanism, Fig. 2 is a perspective view showing a support sleeve, Fig. 3 is a sectional view showing a bearing structure with a mechanical damper, and Fig. 4 is a sectional view showing a conventional bearing structure with a cage type support mechanism. FIG. 5 is a sectional view taken along the line v-v in FIG. 4, FIG. 6 is a sectional view showing the damping function by friction, and FIG. FIG. 8 is a sectional view showing another example in which the inner contact portion and the outer contact portion are formed in a location other than the support sleeve. 11... Fixed bearing body, 18... Rotating shaft, 21...
Support sleeve, 23...inner contact portion, 24...outer contact portion.
Claims (1)
外間に、回転軸のラジアル荷重に応じて弾性変形自在な
支持スリーブを嵌合し、上記支持スリーブと回転軸側、
ならびに、支持スリーブと固定軸受体の各内外間が、そ
れぞれ周方向に特定された３点以上の接触点において接
触するとともに、支持スリーブと回転軸側間の接触点に
対し、支持スリーブと固定軸受体間の接触点を周方向の
異なる角度位置に配置してなる軸受構造。(1) A supporting sleeve that can be elastically deformed according to the radial load of the rotating shaft is fitted between the inner and outer sides of the rotating shaft and a fixed bearing body that supports the rotating shaft, and the support sleeve and the rotating shaft side are
In addition, the support sleeve and the fixed bearing body are in contact with each other at three or more contact points specified in the circumferential direction, and the support sleeve and the fixed bearing are in contact with each other at the contact points between the support sleeve and the rotating shaft side. A bearing structure in which contact points between bodies are placed at different angular positions in the circumferential direction.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP59125676A JPS616424A (en) | 1984-06-18 | 1984-06-18 | Bearing structure |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP59125676A JPS616424A (en) | 1984-06-18 | 1984-06-18 | Bearing structure |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS616424A true JPS616424A (en) | 1986-01-13 |
Family
ID=14915901
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP59125676A Pending JPS616424A (en) | 1984-06-18 | 1984-06-18 | Bearing structure |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS616424A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6323063A (en) * | 1986-07-15 | 1988-01-30 | Fuji Hensokuki Kk | Method of resiliently supporting internal gear |
| JP2004308901A (en) * | 2003-04-07 | 2004-11-04 | Luk Lamellen & Kupplungsbau Beteiligungs Kg | Sound insulating device to be used for device supporting shaft on base body as well as radial waveform spring |
| JP2013515938A (en) * | 2009-12-29 | 2013-05-09 | ロールス−ロイス・コーポレーション | Rotating machine with damping system |
-
1984
- 1984-06-18 JP JP59125676A patent/JPS616424A/en active Pending
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6323063A (en) * | 1986-07-15 | 1988-01-30 | Fuji Hensokuki Kk | Method of resiliently supporting internal gear |
| JPH0514132B2 (en) * | 1986-07-15 | 1993-02-24 | Fuji Hensokuki Kk | |
| JP2004308901A (en) * | 2003-04-07 | 2004-11-04 | Luk Lamellen & Kupplungsbau Beteiligungs Kg | Sound insulating device to be used for device supporting shaft on base body as well as radial waveform spring |
| JP2013515938A (en) * | 2009-12-29 | 2013-05-09 | ロールス−ロイス・コーポレーション | Rotating machine with damping system |
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