JPH11141545A - Squeeze film damper bearing - Google Patents
Squeeze film damper bearingInfo
- Publication number
- JPH11141545A JPH11141545A JP9305687A JP30568797A JPH11141545A JP H11141545 A JPH11141545 A JP H11141545A JP 9305687 A JP9305687 A JP 9305687A JP 30568797 A JP30568797 A JP 30568797A JP H11141545 A JPH11141545 A JP H11141545A
- Authority
- JP
- Japan
- Prior art keywords
- damper
- pressure
- space
- oil film
- annular space
- 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.)
- Withdrawn
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C27/00—Elastic or yielding bearings or bearing supports, for exclusively rotary movement
- F16C27/04—Ball or roller bearings, e.g. with resilient rolling bodies
- F16C27/045—Ball or roller bearings, e.g. with resilient rolling bodies with a fluid film, e.g. squeeze film damping
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
- F16C19/04—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly
- F16C19/06—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly with a single row or balls
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2360/00—Engines or pumps
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Support Of The Bearing (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、ジェットエンジ
ン、高圧コンプレッサ、蒸気タービン又はガスタービン
等の高速回転機械の回転部分若しくは一般機械において
振動防止を必要とする回転部分に適用されるスクイーズ
フィルムダンパー軸受に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a squeeze film damper bearing which is applied to a rotating part of a high-speed rotating machine such as a jet engine, a high-pressure compressor, a steam turbine or a gas turbine, or a rotating part which requires vibration prevention in a general machine. About.
【０００２】[0002]
【従来の技術】図９および図１０に基づいて従来のスク
イーズフィルムダンパー軸受について説明する。2. Description of the Related Art A conventional squeeze film damper bearing will be described with reference to FIGS.
【０００３】図９はころがり軸受を用いた一例を示し、
軸１０のジャーナルに嵌められたころがり軸受１の外周
にはダンパ内輪２が装着され、同ダンパ内輪２の外周面
とその外側に配置されたダンパ外輪３との間には、軸方
向両端をＯリング４、４で閉塞されて環状空間９が形成
されている。FIG. 9 shows an example using a rolling bearing.
A damper inner ring 2 is mounted on the outer periphery of the rolling bearing 1 fitted to the journal of the shaft 10, and both ends in the axial direction are provided between the outer peripheral surface of the damper inner ring 2 and the damper outer ring 3 disposed outside thereof. An annular space 9 is formed closed by the rings 4 and 4.
【０００４】同ダンパ外輪３は、ダンパ内輪２に対峙す
る内面側で、軸方向ほぼ中央位置に、周方向に延びる給
油溝５を有し、かつ、同給油溝５に開放し、半径方向に
延びる給油口６を周方向に間隔をおいて複数個設けてい
る。The outer ring 3 of the damper has a lubrication groove 5 extending in the circumferential direction substantially at the center in the axial direction on the inner surface facing the inner ring 2 of the damper. A plurality of extending oil supply ports 6 are provided at intervals in the circumferential direction.
【０００５】そして図では略示しているが、前記給油口
６は給油ライン７に連通し、同給油ライン７から給油口
６、給油溝５を経て作動流体（本明細書においては、油
や水等の粘性流体を総称する）が環状空間９に供給され
る様になっている。Although schematically shown in the drawing, the oil supply port 6 communicates with an oil supply line 7, and from the oil supply line 7 through an oil supply port 6 and an oil supply groove 5, a working fluid (in this specification, oil or water). Etc.) are supplied to the annular space 9.
【０００６】従っていま、前記給油ライン７から環状空
間９に作動油が供給されている状態で軸１０が回転する
と、その際に軸振動を生じるが、その場合ころがり軸受
１の外周側リングと共にダンパ内輪２が半径方向に振動
し、同ダンパ内輪２で区画される環状空間９の半径方向
の間隔、換言すればダンパ内輪２とダンパ外輪３との隙
間が変化し、ここに供給された前記作動油がダンパ内輪
２につられて動くことにより同隙間内に油膜圧力Ｐ1 を
発生し、この油膜圧力Ｐ1 がダンピング効果をもたらす
ことになる。Therefore, if the shaft 10 rotates while the operating oil is being supplied from the oil supply line 7 to the annular space 9, axial vibration occurs at that time. In this case, the damper is formed together with the outer peripheral ring of the rolling bearing 1. The inner ring 2 vibrates in the radial direction, and the radial spacing of the annular space 9 defined by the damper inner ring 2, in other words, the gap between the damper inner ring 2 and the damper outer ring 3 changes. oil oil film pressure P 1 occurs in the same gap by moving hung on the damper inner ring 2, the oil film pressure P 1 will result in the damping effect.
【０００７】なお、図１０に示すものは、前記図９のこ
ろがり軸受１に換えてすべり軸受１ａを採用したもので
あり、この例ではすべり軸受１ａ自体の外周部がダンパ
内輪を兼用し、その余の構成および機能は前記図９のも
のと全く同一でるので、重複する説明を省略する。FIG. 10 shows an example in which a sliding bearing 1a is employed in place of the rolling bearing 1 of FIG. 9. In this example, the outer peripheral portion of the sliding bearing 1a itself also serves as a damper inner ring. The rest of the configuration and functions are exactly the same as those in FIG. 9 described above, and duplicate description will be omitted.
【０００８】[0008]
【発明が解決しようとする課題】前記の様に構成された
従来のものにあっては、次の様な問題があった。先ず第
１に、装置の作動中にダンパ内輪２とダンパ外輪３は、
互いに偏心することがある。However, the prior art having the above-described structure has the following problems. First, during operation of the device, the damper inner ring 2 and the damper outer ring 3
May be eccentric to each other.
【０００９】ダンパ内輪２のダンパ外輪３に対する相対
偏心量をｅ、偏心時における同ダンパ内輪２とダンパ外
輪３との半径方向の隙間をｃとすると、偏心率：ｅ／ｃ
は図１１に示すように、それが大きくなるとダンピング
係数も大きく変化してダンピング効果の変動が大きくな
り、キャビテーション発生域に及ぶことになるので、同
ダンピング効果を一定に維持するために、偏心を一定に
保つことが必要不可欠となる。Assuming that the relative eccentricity of the damper inner ring 2 with respect to the damper outer ring 3 is e and the radial gap between the damper inner ring 2 and the damper outer ring 3 at the time of eccentricity is c, the eccentricity: e / c.
As shown in FIG. 11, when the damping coefficient increases, the damping coefficient also changes greatly, and the fluctuation of the damping effect increases, which extends to the cavitation generation area. It is essential to keep it constant.
【００１０】ここで軸方向圧力分布見ると、図１３に示
す様に、軸方向の油膜圧力Ｐ2 は環状空間９の中央に当
たる給油溝５を中心として、両端部のＯリング４、４に
向けて漸次大きくなる様に分布している。Looking at the pressure distribution in the axial direction, as shown in FIG. 13, the oil film pressure P 2 in the axial direction is directed toward the O-rings 4 at both ends with the oil supply groove 5 at the center of the annular space 9 as the center. Are distributed so as to gradually increase.
【００１１】また、第２には、ダンパ内輪２とダンパ外
輪３の偏心が大きい時、振動が大きい時、または動荷重
が大きい時には、図１２中の圧力振幅値Ｐmax が大きく
なるため、同図１２に示す様に周方向圧力分布を見る
と、０〜２πの間のうちの一定の角度幅の部分では、油
膜圧力Ｐ1 が給油溝圧力Ｐ0 を通り越してキャビテーシ
ョン発生圧力Ｐ3 より低くなり、キャビテーション発生
域Ｚに入り込んでしまうので、ここにキャビテーション
現象が発生し、これに伴ってダンピング特性のジャンプ
が起こり、突然ダンピングが減少してダンピング効果が
なくなることがある。Second, when the eccentricity of the damper inner ring 2 and the damper outer ring 3 is large, when the vibration is large, or when the dynamic load is large, the pressure amplitude value Pmax in FIG. looking at the circumferential pressure distribution as shown in FIG. 12, in the portion of constant angular width of between 0～2Pai, lower than the cavitation pressure P 3 oil film pressure P 1 is past the oil groove pressure P 0 In other words, since the cavitation occurs in the cavitation generation area Z, a cavitation phenomenon occurs here, and a jump in the damping characteristic occurs, and the damping is suddenly reduced and the damping effect may be lost.
【００１２】しかも、この現象はダンピングが一番効い
て欲しい大振動の時に発生するので、この問題を解決す
ることは回転機械の事故防止にとって極めて重要、かつ
必須の事項である。Moreover, since this phenomenon occurs at the time of a large vibration in which damping is desired to be most effective, solving this problem is extremely important and indispensable for preventing accidents of the rotating machine.
【００１３】しかしながら、この点に関する従来の技術
レベルは決して満足の行くものではなく、むしろこの問
題は解決不能と決めつけられ、関連部位の構成を余裕を
持たせた設計で対応するという以外に格別の妙案はな
く、適切な対策は取られていないというのが実情であっ
た。However, the state of the art in this regard has not been satisfactory at all, and rather, this problem has been determined to be unsolvable, and there is a special case other than the fact that the structure of the relevant parts is dealt with with a marginal design. The fact was that there were no special plans and no proper measures were taken.
【００１４】本発明はこのような状況を背景としてなさ
れ、前記キャビテーション現象の発生を抑制し、回転機
械の事故発生の防止を図るようにした好適なスクイーズ
フィルムダンパー軸受を提供することを課題とするもの
である。It is an object of the present invention to provide a squeeze film damper bearing suitable for suppressing the occurrence of the cavitation phenomenon and preventing the occurrence of an accident in a rotating machine. Things.
【００１５】[0015]
【課題を解決するための手段】本発明は、前記した課題
を解決すべくなされたもので、半径方向に振動する内輪
と固定した外輪との間に形成される環状空間に油膜圧力
を発生させてダンパーを形成するスクイーズフィルムダ
ンパー軸受において、前記環状空間の軸方向端部寄りに
油膜圧力を逃がす空間部を設けたスクイーズフィルムダ
ンパー軸受を提供するものである。SUMMARY OF THE INVENTION The present invention has been made to solve the above-mentioned problems, and it is intended to generate an oil film pressure in an annular space formed between a radially oscillating inner ring and a fixed outer ring. The present invention provides a squeeze film damper bearing in which a damper is formed to provide a space for releasing oil film pressure near an axial end of the annular space.
【００１６】すなわち、本発明に於いては、油膜圧力が
発生する内輪と外輪との間の環状空間には、その軸方向
端部に寄せて空間部を設けているので、この端部に向け
てピーク圧となる環状空間に発生する油膜圧力は、前記
空間部により逃がされてそのピーク圧は低下することに
なる。That is, in the present invention, the annular space between the inner ring and the outer ring where the oil film pressure is generated is provided with a space near the axial end thereof. The oil film pressure generated in the annular space, which becomes the peak pressure, is released by the space portion, and the peak pressure decreases.
【００１７】また、本発明は、前記空間部は、前記環状
空間を外輪の外に開放する複数のダンパ孔で構成したス
クイーズフィルムダンパー軸受を提供するものである。Further, the present invention provides a squeeze film damper bearing in which the space portion includes a plurality of damper holes that open the annular space to the outside of the outer ring.
【００１８】すなわち、本発明に於いて、前記内輪と外
輪との間に形成された環状空間の軸方向端部に寄せて設
けた空間部は、環状空間を外輪の外に向けて開放する複
数のダンパ孔で形成されているので、同環状空間の端部
に向けてピーク圧となる油膜圧力は、同ダンパ孔を経て
環状空間から流出する作動流体と共に逃がされ、環状空
間内の油膜圧力のピークは低下することになる。That is, in the present invention, the space portion provided near the axial end of the annular space formed between the inner ring and the outer ring has a plurality of spaces that open the annular space toward the outside of the outer ring. The oil film pressure which becomes a peak pressure toward the end of the annular space is released together with the working fluid flowing out of the annular space through the damper hole, and the oil film pressure in the annular space is reduced. Will decrease.
【００１９】また、本発明は、前記空間部は、前記外輪
または内輪の少なくともいずれか一方に設けた円周溝で
構成したスクイーズフィルムダンパー軸受を提供するも
のである。Further, the present invention provides a squeeze film damper bearing in which the space portion is constituted by a circumferential groove provided in at least one of the outer ring and the inner ring.
【００２０】すなわち、本発明に於いて、前記内輪と外
輪との間に形成された環状空間の軸方向端部に寄せて設
けた空間部は、これを円周溝で形成したので、同環状空
間の端部に向けてピーク圧となる油膜圧力は、作動流体
が同円周溝に流入することにより逃がされ、ここに発生
する油膜圧力のピークは低下することになる。That is, according to the present invention, the space provided near the axial end of the annular space formed between the inner ring and the outer ring is formed by a circumferential groove. The oil film pressure that becomes the peak pressure toward the end of the space is released by the working fluid flowing into the circumferential groove, and the peak of the oil film pressure generated here decreases.
【００２１】さらにまた、本発明は、前記空間部は、軸
方向端部に向かって拡大するテーパ部または段差部で構
成したスクイーズフィルムダンパー軸受を提供するもの
である。Still further, the present invention provides a squeeze film damper bearing in which the space portion is constituted by a tapered portion or a step portion which expands toward an axial end.
【００２２】すなわち、本発明に於いて、前記内輪と外
輪との間に形成された環状空間の軸方向端部に寄せて設
けた空間部は、これを軸方向端部に向かって拡大するテ
ーパ部または段差部で形成したので、同環状空間の端部
に向けてピーク圧となる油膜圧力は、作動流体がこのテ
ーパ部または段差部に流入することにより逃がされ、こ
こに発生する油膜圧力のピークは低下することになる。That is, according to the present invention, the space provided near the axial end of the annular space formed between the inner ring and the outer ring has a taper that expands toward the axial end. The oil film pressure, which is a peak pressure toward the end of the annular space, is released by the working fluid flowing into the tapered portion or the step portion, and the oil film pressure generated there is formed. Will decrease.
【００２３】[0023]
【発明の実施の形態】本発明の実施の第１形態を図１お
よび図２に基づいて説明する。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A first embodiment of the present invention will be described with reference to FIGS.
【００２４】図１は、本実施の形態に係るスクイーズフ
ィルムダンパー軸受の断面形状を示し、図にはその要部
の応用変形例を示している。FIG. 1 shows a cross-sectional shape of a squeeze film damper bearing according to the present embodiment, and FIG. 1 shows an applied modification of a main part thereof.
【００２５】なお、本実施の形態においては、その多く
の構成部分が前記従来のものと同一であるので、同従来
のものと同一の部位については、図中に同一の符号を付
して示すことにより重複する説明は極力省略し、本実施
の形態の特徴とする部分を重点的に説明する。In this embodiment, since many of the components are the same as those of the conventional one, the same parts as those of the conventional one are denoted by the same reference numerals in the drawings. Therefore, redundant description will be omitted as much as possible, and the characteristic features of the present embodiment will be mainly described.
【００２６】本実施の形態においては、環状空間９の両
端部で同環状空間９を区画形成する左右のＯリング４、
４の近くに、ダンパ外輪３の内周面側から外周面側に貫
通する複数のダンパ孔８を設けている。In the present embodiment, the left and right O-rings 4 which define the annular space 9 at both ends of the annular space 9,
A plurality of damper holes 8 penetrating from the inner peripheral surface side to the outer peripheral surface side of the damper outer ring 3 are provided near the damper outer ring 3.
【００２７】従って、給油ライン７で送られて来て、給
油口６、給油溝５を経て環状空間９へ供給される作動流
体は、同環状空間９の両端部側に設けた各ダンパ孔８、
８を経て給油口６の上流側へ循環する流路が形成される
ことになる。Therefore, the working fluid sent through the oil supply line 7 and supplied to the annular space 9 through the oil supply port 6 and the oil supply groove 5 is supplied to each of the damper holes 8 provided at both ends of the annular space 9. ,
A flow path circulating to the upstream side of the refueling port 6 through the oil supply port 6 is formed.
【００２８】なお、このダンパ孔８の数と直径は具体的
な装置に求められる特性によって決められるが、数につ
いては、ダンパ外輪３の両端部側それぞれ周方向に４〜
３２個程度穿孔されるのがよい。The number and diameter of the damper holes 8 are determined according to the characteristics required for a specific device.
Preferably, about 32 holes are drilled.
【００２９】また、同ダンパ孔８の、ダンパ外輪３内周
面入口側と外周面出口側におけるそれぞれの形状は、図
２（ａ）に示す様に、入口側をシャープエッジ８ａと
し、出口側はＲ形状丸め加工８ｂとするか、または、図
２（ｂ）に示す様に、入口側はそのままシャープエッジ
８ａとし、出口側はテーパ形状８ｃとすることが望まし
い。As shown in FIG. 2A, the shape of the damper hole 8 on the inlet side of the inner peripheral surface and the outlet side of the outer peripheral surface of the damper outer ring 3 is such that the entrance side is a sharp edge 8a and the exit side is a sharp edge 8a. It is desirable that the shape be a round shape 8b or, as shown in FIG. 2B, the entrance side be the sharp edge 8a as it is and the exit side be the tapered shape 8c.
【００３０】この様に構成された本実施の形態において
は、軸１０の振動によりころがり軸受１が振動すると、
ダンパ内輪２とダンパ外輪３の間、即ち環状空間９の油
膜には、図７〜図８に示す様な圧力分布が生じ、その結
果として図６に示す様なダンピング特性が得られる。In the present embodiment configured as described above, when the rolling bearing 1 vibrates due to the vibration of the shaft 10,
A pressure distribution as shown in FIGS. 7 and 8 is generated between the damper inner ring 2 and the damper outer ring 3, that is, in the oil film in the annular space 9, and as a result, a damping characteristic as shown in FIG. 6 is obtained.
【００３１】なお、図６〜図８の表示は、本実施の形態
の理解を容易にすることを狙って、本実施の形態に於け
る特性を実線で示し、これに対比させて前記図１１〜図
１３に説明した従来のものに於ける特性を破線で示して
いる。6 to 8 show the characteristics of the present embodiment by solid lines in order to facilitate understanding of the present embodiment, and in contrast to FIG. The characteristics of the conventional device described in FIGS.
【００３２】すなわち、前記ダンパ孔８を設けたことに
より、その小孔を通して作動流体の出入りが生じ、図８
に破線Ｂの従来例と実線Ａの本実施の形態を対比して示
した様に、軸方向において圧力分布がなだらかとなり、
ピーク圧力が小さくなる。That is, the provision of the damper hole 8 allows the working fluid to enter and exit through the small hole.
As shown by comparing the conventional example of the broken line B with the present embodiment of the solid line A, the pressure distribution becomes gentle in the axial direction,
Peak pressure decreases.
【００３３】また、ダンパ孔８の入口および出口形状を
前記図２（ａ）、（ｂ）において説明した様に形成した
ことにより、作動流体は、シャープエッジ８ａの入口側
からは入りにくく、Ｒ形状丸め加工８ｂまたはテーパ形
状８ｃの出口側からは入り易くなるので、正のピーク圧
の減少よりも負のピーク圧の減少が大きくなる。Further, since the shape of the inlet and outlet of the damper hole 8 is formed as described with reference to FIGS. 2A and 2B, the working fluid hardly enters from the inlet side of the sharp edge 8a. Since it is easy to enter from the exit side of the rounding 8b or the tapered shape 8c, the decrease in the negative peak pressure is larger than the decrease in the positive peak pressure.
【００３４】これを図７に破線Ｂの従来例と実線Ａの本
実施の形態を対比して示すと、本実施の形態の円周方向
に於ける油膜圧力Ｐ1 は、給油溝圧力Ｐ0 を基準として
正の方向で破線Ｂの従来例より低下してピークがなだら
かとなるが、前記給油溝圧力Ｐ0 を基準として負の方向
では、このなだらかさが一段と進み、ピークがより小さ
くなり、従来のものと異なってキャビテーション発生圧
Ｐ3 以下に低下しにくくなることになる。FIG. 7 shows a comparison between the conventional example of the dashed line B and the present embodiment of the solid line A. The oil film pressure P 1 in the circumferential direction of the present embodiment is equal to the oil supply groove pressure P 0. , The peak becomes gentler in the positive direction than in the conventional example of the broken line B in the positive direction, but in the negative direction based on the oil supply groove pressure P 0 , the gentleness further advances, and the peak becomes smaller. It will be less likely to drop different from that of conventional below cavitation pressure P 3.
【００３５】従って図６に於いては、大偏心率において
も図１２に示すようなキャビテーション発生域が存在し
なくなる。Therefore, in FIG. 6, the cavitation occurrence area as shown in FIG. 12 does not exist even at a large eccentricity.
【００３６】要するに本実施の形態においては、図６〜
図８に纏められて表示されるように偏心の大きい範囲で
の特性の変化が大きく生じなくなると共に、油膜内の負
圧の発生も小孔からの作動流体の出入りにより大幅に緩
和されるため、キャビテーションの発生を広い範囲で防
止できる。In short, in this embodiment, FIGS.
As shown in FIG. 8, the characteristics do not greatly change in the range of large eccentricity, and the generation of the negative pressure in the oil film is greatly reduced by the inflow and outflow of the working fluid from the small holes. Cavitation can be prevented in a wide range.
【００３７】その結果、スクイーズフィルムダンパー軸
受としての効果を振動の大振幅まで保つことができ、回
転機械の信頼性を大幅に高めることができるようになっ
たものである。As a result, the effect as a squeeze film damper bearing can be maintained up to a large amplitude of vibration, and the reliability of the rotating machine can be greatly improved.
【００３８】次に本発明の実施の第２形態について図３
に基づいて説明する。本実施の形態は基本的な構成部分
が前記実施の第１形態と同一であるので、本実施の形態
の主要部で前記実施の第１形態と異なる部分のみを図示
し、説明も図面の表示も重複する部分は大幅に省略し
た。Next, a second embodiment of the present invention will be described with reference to FIG.
It will be described based on. In this embodiment, since the basic components are the same as those of the first embodiment, only the parts different from those of the first embodiment are shown in the main parts of the present embodiment, and the description is also shown in the drawings. Also, the overlapping part has been largely omitted.
【００３９】すなわち、本実施の形態においては、前記
実施の第１形態におけるダンパ孔８に換えて、ダンパ外
輪３の該当する位置に内周面に沿って延びる円周溝１１
を設けたものである。That is, in the present embodiment, instead of the damper hole 8 in the first embodiment, a circumferential groove 11 extending along the inner peripheral surface at a corresponding position of the damper outer ring 3 is provided.
Is provided.
【００４０】そしてこの円周溝１１が前記ダンパ孔８と
同様に機能して、ピーク圧力の低減と、負圧発生の軽減
を行い、同ダンパ孔８を主要な構成とする前記実施の第
１形態のものと同等の効果を奏するものである。The circumferential groove 11 functions in the same manner as the damper hole 8 to reduce the peak pressure and the generation of the negative pressure. An effect equivalent to that of the embodiment can be obtained.
【００４１】なお、本実施の形態において、ここで図示
したものでは、円周溝１１をダンパ外輪３に設けている
が、同円周溝１１はダンパ内輪２に設けてもよく、また
は、ダンパ外輪３とダンパ内輪２のいずれか一方ではな
く、両方に設けてもよいものである。In the present embodiment, the circumferential groove 11 is provided in the damper outer ring 3 in the drawing shown here, but the circumferential groove 11 may be provided in the damper inner ring 2 or the damper inner ring 2 may be provided. The outer ring 3 and the damper inner ring 2 may be provided not on either one but on both.
【００４２】次に本発明の実施の第３形態について図
４、図５に基づいて説明する。前記実施の第２形態と同
様に、本実施の形態も基本的な構成部分が前記実施の第
１形態と同一であるので、本実施の形態の主要部で前記
実施の第１形態と異なる部分のみを図示し、説明も図面
の表示も重複する部分は大幅に省略した。Next, a third embodiment of the present invention will be described with reference to FIGS. As in the second embodiment, the basic configuration of the present embodiment is the same as that of the first embodiment. Therefore, the main part of the second embodiment is different from the first embodiment. Only the parts that are the same in the description and the display of the drawings are largely omitted.
【００４３】すなわち、図４に示した本実施の形態にお
いては、前記実施の第１形態におけるダンパ孔８に換え
て、ダンパ外輪３の該当する位置の内周面を、軸方向端
部に配置したＯリング４に向かって拡大するテーパ部１
２で構成したものである。That is, in the present embodiment shown in FIG. 4, instead of the damper hole 8 in the first embodiment, the inner peripheral surface of the damper outer ring 3 at the corresponding position is disposed at the axial end. Tapered portion 1 expanding toward the O-ring 4
2.
【００４４】また、図５には、この変形例として、前記
テーパ部１２に換えてダンパ外輪３の該当する位置の内
周面を、軸方向端部に配置したＯリング４に向かって拡
大する段差部１３で構成したものをしめしている。FIG. 5 shows a modified example in which the inner peripheral surface of the damper outer ring 3 at a corresponding position is enlarged toward the O-ring 4 disposed at the axial end instead of the tapered portion 12. The structure constituted by the step portion 13 is shown.
【００４５】そしてこのテーパ部１２または段差部１３
が前記実施の第１形態におけるダンパ孔８と同様に機能
して、ピーク圧力の低減と、負圧発生の軽減を行い、前
記実施の第１形態のものと同等の効果を奏するものであ
る。The tapered portion 12 or the stepped portion 13
Functions in the same manner as the damper hole 8 in the first embodiment, reduces the peak pressure and reduces the generation of the negative pressure, and has the same effect as that of the first embodiment.
【００４６】以上、本発明を図示の実施の形態について
説明したが、本発明はかかる実施の形態に限定されず、
本発明の範囲内でその具体的構造に種々の変更を加えて
よいことはいうまでもない。Although the present invention has been described with reference to the illustrated embodiment, the present invention is not limited to such an embodiment.
It goes without saying that various changes may be made to the specific structure within the scope of the present invention.
【００４７】[0047]
【発明の効果】以上説明したように本発明によれば、半
径方向に振動する内輪と固定した外輪との間に形成され
る環状空間に油膜圧力を発生させてダンパーを形成する
スクイーズフィルムダンパー軸受において、前記環状空
間の軸方向端部寄りに油膜圧力を逃がす空間部を設けた
構成としているので、本発明に於いては、油膜圧力が発
生する内輪と外輪との間の環状空間の端部に向けてピー
ク圧となる油膜圧力は、前記空間部により逃がされてそ
のピーク圧は低下して大幅に緩和されるため、キャビテ
ーションの発生を広い範囲で防止できる。As described above, according to the present invention, a squeeze film damper bearing for forming a damper by generating an oil film pressure in an annular space formed between an inner ring vibrating in the radial direction and a fixed outer ring. In the present invention, since the space portion for releasing the oil film pressure is provided near the axial end of the annular space, in the present invention, the end portion of the annular space between the inner ring and the outer ring where the oil film pressure is generated is provided. The oil film pressure, which becomes the peak pressure toward, is relieved by the space portion and the peak pressure is reduced and greatly reduced, so that cavitation can be prevented in a wide range.
【００４８】その結果、スクイーズフィルムダンパー軸
受としての効果を振動の大振幅まで保つことができ、回
転機械の信頼性を大幅に高めることができるようになっ
たものである。As a result, the effect as a squeeze film damper bearing can be maintained up to a large amplitude of vibration, and the reliability of the rotating machine can be greatly improved.
【００４９】また、請求項２に記載の発明によれば、前
記空間部は、前記環状空間を外輪の外に開放する複数の
ダンパ孔で構成しているので、本発明に於いては、前記
内輪と外輪との間に形成された環状空間を外輪の外に向
けて開放する複数のダンパ孔により、同環状空間の端部
に向けてピーク圧となる油膜圧力を作動流体と共に逃が
し、環状空間内の油膜圧力のピークを低下して大幅に緩
和し、キャビテーションの発生を広い範囲で防止でき
る。According to the second aspect of the present invention, the space portion is constituted by a plurality of damper holes which open the annular space to the outside of the outer ring. With a plurality of damper holes that open the annular space formed between the inner ring and the outer ring to the outside of the outer ring, the oil film pressure, which becomes the peak pressure toward the end of the annular space, is released together with the working fluid, and the annular space is released. The peak of the oil film pressure in the inside is reduced and greatly reduced, and the occurrence of cavitation can be prevented in a wide range.
【００５０】その結果、前記の発明と同様に、スクイー
ズフィルムダンパー軸受としての効果を振動の大振幅ま
で保つことができ、回転機械の信頼性を大幅に高めるこ
とができるようになったものである。As a result, similarly to the above-described invention, the effect as the squeeze film damper bearing can be maintained up to a large amplitude of vibration, and the reliability of the rotating machine can be greatly improved. .
【００５１】また、請求項３に記載の発明によれば、前
記空間部は、前記外輪または内輪の少なくともいずれか
一方に設けた円周溝で構成しているので、本発明に於い
ては、前記内輪と外輪との間に形成された環状空間の軸
方向端部に寄せて設けた円周溝により、同環状空間の端
部に向けてピーク圧となる油膜圧力を逃がし、環状空間
内の油膜圧力のピークを低下して大幅に緩和し、キャビ
テーションの発生を広い範囲で防止できる。According to the third aspect of the present invention, the space is formed by a circumferential groove provided in at least one of the outer ring and the inner ring. By a circumferential groove provided at an axial end of the annular space formed between the inner ring and the outer ring, an oil film pressure which becomes a peak pressure toward the end of the annular space is released, and the inside of the annular space is released. The peak of the oil film pressure is reduced and greatly reduced, and the occurrence of cavitation can be prevented in a wide range.
【００５２】その結果、前記の各発明と同様に、スクイ
ーズフィルムダンパー軸受としての効果を振動の大振幅
まで保つことができ、回転機械の信頼性を大幅に高める
ことができるようになったものである。As a result, as in the above-described inventions, the effect of the squeeze film damper bearing can be maintained up to a large amplitude of vibration, and the reliability of the rotating machine can be greatly improved. is there.
【００５３】さらにまた、請求項４に記載の発明によれ
ば、前記空間部は、軸方向端部に向かって拡大するテー
パ部または段差部で構成しているので、本発明に於いて
は、前記内輪と外輪との間に形成された環状空間の軸方
向端部に寄せて設けたテーパ部または段差部により、同
環状空間の端部に向けてピーク圧となる油膜圧力を逃が
し、環状空間内の油膜圧力のピークを低下して大幅に緩
和し、キャビテーションの発生を広い範囲で防止でき
る。Further, according to the fourth aspect of the present invention, since the space portion is constituted by a tapered portion or a step portion which expands toward the axial end, the present invention provides: By a tapered portion or a stepped portion provided near the axial end of the annular space formed between the inner ring and the outer ring, an oil film pressure which becomes a peak pressure toward the end of the annular space is released, and the annular space is released. The peak of the oil film pressure in the inside is reduced and greatly reduced, and the occurrence of cavitation can be prevented in a wide range.
【００５４】そして本発明もまた前記の各発明と同様
に、スクイーズフィルムダンパー軸受としての効果を振
動の大振幅まで保つことができ、回転機械の信頼性を大
幅に高めることができるようになったものである。Also, in the present invention, similarly to the above-mentioned inventions, the effect as a squeeze film damper bearing can be maintained up to a large amplitude of vibration, and the reliability of the rotating machine can be greatly improved. Things.
【図１】本発明の実施の第１形態に係るスクイーズフィ
ルムダンパー軸受の断面形状を示す説明図である。FIG. 1 is an explanatory diagram showing a cross-sectional shape of a squeeze film damper bearing according to a first embodiment of the present invention.
【図２】図１のものに於ける要部を拡大して示し、
（ａ）は一例を、（ｂ）は他の例をそれぞれ示す説明図
である。FIG. 2 is an enlarged view of a main part in FIG.
(A) is an explanatory view showing an example, and (b) is an explanatory view showing another example.
【図３】本発明の実施の第２形態に係るスクイーズフィ
ルムダンパー軸受の主要部を拡大して示す説明図であ
る。FIG. 3 is an explanatory diagram showing an enlarged main part of a squeeze film damper bearing according to a second embodiment of the present invention.
【図４】本発明の実施の第３形態に係るスクイーズフィ
ルムダンパー軸受の主要部を拡大して示す説明図であ
る。FIG. 4 is an explanatory diagram showing an enlarged main part of a squeeze film damper bearing according to a third embodiment of the present invention.
【図５】図４のものに於ける変形例を示す説明図であ
る。FIG. 5 is an explanatory view showing a modified example of the one shown in FIG. 4;
【図６】本発明の各実施の形態におけるダンパ内外輪の
偏心状況を示す説明図である。FIG. 6 is an explanatory diagram showing an eccentric state of the damper inner and outer rings in each embodiment of the present invention.
【図７】本発明の各実施の形態における円周方向圧力分
布を示す説明図である。FIG. 7 is an explanatory diagram showing a circumferential pressure distribution in each embodiment of the present invention.
【図８】本発明の各実施の形態における軸方向圧力分布
を示す説明図である。FIG. 8 is an explanatory diagram showing an axial pressure distribution in each embodiment of the present invention.
【図９】従来のスクイーズフィルムダンパー軸受の一例
の断面形状を示す説明図である。FIG. 9 is an explanatory diagram showing a cross-sectional shape of an example of a conventional squeeze film damper bearing.
【図１０】従来のスクイーズフィルムダンパー軸受の他
の例の断面形状を示す説明図である。FIG. 10 is an explanatory diagram showing a cross-sectional shape of another example of the conventional squeeze film damper bearing.
【図１１】従来のスクイーズフィルムダンパー軸受にお
けるダンパ内外輪の偏心状況を示す説明図である。FIG. 11 is an explanatory view showing an eccentric state of damper inner and outer rings in a conventional squeeze film damper bearing.
【図１２】従来のスクイーズフィルムダンパー軸受にお
ける円周方向圧力分布を示す説明図である。FIG. 12 is an explanatory diagram showing a circumferential pressure distribution in a conventional squeeze film damper bearing.
【図１３】従来のスクイーズフィルムダンパー軸受にお
ける軸方向圧力分布を示す説明図である。FIG. 13 is an explanatory diagram showing an axial pressure distribution in a conventional squeeze film damper bearing.
１ ころがり軸受 １ａ すべり軸受 ２ ダンパ内輪 ３ ダンパ外輪 ４ Ｏリング ５ 給油溝 ６ 給油口 ７ 給油ライン ８ ダンパ孔 ８ａ シャープエッジ ８ｂ Ｒ形状丸め加工 ８ｃ テーパ形状 ９ 環状空間 １０ 軸 １１ 円周溝 １２ テーパ部 １３ 段差部 Ｐ0 給油溝圧力 Ｐ1 油膜圧力 Ｐ2 油膜圧力 Ｐ3 キャビテーション発生圧 Ｚ キャビテーション発生域DESCRIPTION OF SYMBOLS 1 Rolling bearing 1a Sliding bearing 2 Damper inner ring 3 Damper outer ring 4 O-ring 5 Oil supply groove 6 Oil supply port 7 Oil supply line 8 Damper hole 8a Sharp edge 8b R shape rounding 8c Tapered 9 Annular space 10 Shaft 11 Circular groove 12 Tapered portion 13 Steps P 0 Oil groove pressure P 1 Oil film pressure P 2 Oil film pressure P 3 Cavitation pressure Z Cavitation pressure
Claims (4)
との間に形成される環状空間に油膜圧力を発生させてダ
ンパーを形成するスクイーズフィルムダンパー軸受にお
いて、前記環状空間の軸方向端部寄りに油膜圧力を逃が
す空間部を設けたことを特徴とするスクイーズフィルム
ダンパー軸受。1. A squeeze film damper bearing in which an oil film pressure is generated in an annular space formed between a radially oscillating inner ring and a fixed outer ring to form a damper, the squeeze film damper bearing being closer to an axial end of the annular space. A squeeze film damper bearing characterized by having a space for releasing oil film pressure.
に開放する複数のダンパ孔で構成したことを特徴とする
請求項１に記載のスクイーズフィルムダンパー軸受。2. The squeeze film damper bearing according to claim 1, wherein the space portion includes a plurality of damper holes that open the annular space to the outside of the outer ring.
なくともいずれか一方に設けた円周溝で構成したことを
特徴とする請求項１に記載のスクイーズフィルムダンパ
ー軸受。3. The squeeze film damper bearing according to claim 1, wherein the space is formed by a circumferential groove provided in at least one of the outer ring and the inner ring.
大するテーパ部または段差部で構成したことを特徴とす
る請求項１に記載のスクイーズフィルムダンパー軸受。4. The squeeze film damper bearing according to claim 1, wherein said space portion is constituted by a tapered portion or a stepped portion expanding toward an axial end.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP9305687A JPH11141545A (en) | 1997-11-07 | 1997-11-07 | Squeeze film damper bearing |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP9305687A JPH11141545A (en) | 1997-11-07 | 1997-11-07 | Squeeze film damper bearing |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH11141545A true JPH11141545A (en) | 1999-05-25 |
Family
ID=17948159
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP9305687A Withdrawn JPH11141545A (en) | 1997-11-07 | 1997-11-07 | Squeeze film damper bearing |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH11141545A (en) |
Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2007023702A1 (en) * | 2005-08-24 | 2007-03-01 | Ihi Corporation | Damper element of bearing, method of manufacturing damper element, bearing, and gas turbine engine |
| DE102010004870A1 (en) * | 2010-01-18 | 2011-07-21 | Bosch Mahle Turbo Systems GmbH & Co. KG, 70376 | Pivot bearing arrangement for rotor of turbocharger, has inner ring and outer ring between rotor and housing body, particularly between rotor shaft and housing body of turbocharger |
| CN102705427A (en) * | 2012-06-12 | 2012-10-03 | 中国科学院工程热物理研究所 | Squeeze film damper |
| JP2017150484A (en) * | 2016-02-25 | 2017-08-31 | ゼネラル・エレクトリック・カンパニイ | Core differential bearing with centering spring and squeeze film damper |
| EP3260718A1 (en) * | 2016-05-23 | 2017-12-27 | United Technologies Corporation | Squeeze film damper for a rolling bearing of a gas turbine engine with a check-valve in the supply passage |
| JP2018138806A (en) * | 2017-02-24 | 2018-09-06 | 本田技研工業株式会社 | Squeeze film damper bearing device |
| JP2019132391A (en) * | 2018-02-01 | 2019-08-08 | 本田技研工業株式会社 | Bearing device |
| WO2020160734A1 (en) | 2019-02-07 | 2020-08-13 | Gea Process Engineering A/S | Rotary bearing with a damper, a motor and a rotary atomizer comprising such bearing, and the use of such bearing |
| CN111637188A (en) * | 2019-03-02 | 2020-09-08 | 超级涡轮技术有限公司 | Fluid damping system for a traction drive |
| WO2021256372A1 (en) * | 2020-06-15 | 2021-12-23 | 川崎重工業株式会社 | Damper |
| CN114810892A (en) * | 2021-01-28 | 2022-07-29 | 中国航发商用航空发动机有限责任公司 | Squeeze film damper and aircraft engine |
-
1997
- 1997-11-07 JP JP9305687A patent/JPH11141545A/en not_active Withdrawn
Cited By (19)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2007023702A1 (en) * | 2005-08-24 | 2007-03-01 | Ihi Corporation | Damper element of bearing, method of manufacturing damper element, bearing, and gas turbine engine |
| DE102010004870A1 (en) * | 2010-01-18 | 2011-07-21 | Bosch Mahle Turbo Systems GmbH & Co. KG, 70376 | Pivot bearing arrangement for rotor of turbocharger, has inner ring and outer ring between rotor and housing body, particularly between rotor shaft and housing body of turbocharger |
| CN102705427A (en) * | 2012-06-12 | 2012-10-03 | 中国科学院工程热物理研究所 | Squeeze film damper |
| CN102705427B (en) * | 2012-06-12 | 2013-12-04 | 中国科学院工程热物理研究所 | Squeeze film damper |
| JP2017150484A (en) * | 2016-02-25 | 2017-08-31 | ゼネラル・エレクトリック・カンパニイ | Core differential bearing with centering spring and squeeze film damper |
| EP3260718A1 (en) * | 2016-05-23 | 2017-12-27 | United Technologies Corporation | Squeeze film damper for a rolling bearing of a gas turbine engine with a check-valve in the supply passage |
| US10077713B2 (en) | 2016-05-23 | 2018-09-18 | United Technologies Corporation | Self-pressurizing film damper |
| JP2018138806A (en) * | 2017-02-24 | 2018-09-06 | 本田技研工業株式会社 | Squeeze film damper bearing device |
| JP2019132391A (en) * | 2018-02-01 | 2019-08-08 | 本田技研工業株式会社 | Bearing device |
| WO2020160734A1 (en) | 2019-02-07 | 2020-08-13 | Gea Process Engineering A/S | Rotary bearing with a damper, a motor and a rotary atomizer comprising such bearing, and the use of such bearing |
| 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 |
| 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 |
| CN113348309B (en) * | 2019-02-07 | 2024-06-14 | 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 |
| CN111637188A (en) * | 2019-03-02 | 2020-09-08 | 超级涡轮技术有限公司 | Fluid damping system for a traction drive |
| CN111637188B (en) * | 2019-03-02 | 2023-02-24 | 超级涡轮技术有限公司 | Fluid damping system for traction drive |
| WO2021256372A1 (en) * | 2020-06-15 | 2021-12-23 | 川崎重工業株式会社 | Damper |
| JP2021195996A (en) * | 2020-06-15 | 2021-12-27 | 川崎重工業株式会社 | damper |
| CN114810892A (en) * | 2021-01-28 | 2022-07-29 | 中国航发商用航空发动机有限责任公司 | Squeeze film damper and aircraft engine |
| CN114810892B (en) * | 2021-01-28 | 2024-04-05 | 中国航发商用航空发动机有限责任公司 | Extrusion oil film damper and aeroengine |
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| A300 | Withdrawal of application because of no request for examination |
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