JPS62215124A - Bearing and sealing device for rotary machine - Google Patents
Bearing and sealing device for rotary machineInfo
- Publication number
- JPS62215124A JPS62215124A JP61053578A JP5357886A JPS62215124A JP S62215124 A JPS62215124 A JP S62215124A JP 61053578 A JP61053578 A JP 61053578A JP 5357886 A JP5357886 A JP 5357886A JP S62215124 A JPS62215124 A JP S62215124A
- Authority
- JP
- Japan
- Prior art keywords
- seal
- lubricating oil
- rotating body
- movable ring
- rotor
- 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
- 238000007789 sealing Methods 0.000 title description 11
- 239000010687 lubricating oil Substances 0.000 claims abstract description 34
- 230000002093 peripheral effect Effects 0.000 claims abstract description 9
- 238000004519 manufacturing process Methods 0.000 abstract description 4
- 238000000638 solvent extraction Methods 0.000 abstract 1
- 239000012530 fluid Substances 0.000 description 7
- 230000000694 effects Effects 0.000 description 4
- 239000003921 oil Substances 0.000 description 2
- 229910000897 Babbitt (metal) Inorganic materials 0.000 description 1
- 238000005452 bending Methods 0.000 description 1
- 238000007796 conventional method Methods 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 239000000314 lubricant Substances 0.000 description 1
- 238000005461 lubrication Methods 0.000 description 1
- 230000000149 penetrating effect Effects 0.000 description 1
- 230000035515 penetration Effects 0.000 description 1
- 230000003068 static effect Effects 0.000 description 1
Landscapes
- Sealing Of Bearings (AREA)
- Sliding-Contact Bearings (AREA)
- Support Of The Bearing (AREA)
Abstract
Description
【発明の詳細な説明】
（産業上の利用分野）
本発明は圧縮機、ガス膨張機等の回転機械に適用する軸
受兼シール装置に関するものである。DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to a bearing/seal device applied to rotating machines such as compressors and gas expanders.
（従来の技術）
従来の回転機械の軸受装置及びシール装置を第７．８図
により説明すると、第７図の（１０１）が回転体で、同
回転体（１０１）の両端部が軸受ユニット（１０２）
（１０２）により回転可能に支持され、上記回転体（ｌ
ｏｔ）が貫通するケーシング（１０５）の貫通部にケー
シング（ＩＯ２）内の作動流体を密封するシールユニッ
ト） （１０３） （１０３）が設けられている。また
上記軸受ユニット（１０２）は、第８図に示すように軸
受メタル（１１１）と回転体（１０１）との間に形成し
た油ＩＩＩ（１１５）により５回転体（１０１）の静荷
重及び動荷重を支持している。また上記ケーシング（１
０５）の回転体貫通部には、シールフランジ（１３４）
とシールフンジング（１３３） とが設けられ、上記シ
ールユニット（１０３）は１機内側シールリング（１３
１） と機外側シールリング（１３２） とを有し、同
各シールリング（１３１）８１３２）と回転体（１０１
）との間に微小な間隙が形成されており、上記ケーシン
グ（１０５）に設けられたシール流体供給孔（１０５ａ
）から上記微小な間隙へシール流体が供給されて、ケー
シング（１０５）内の作動流体が外部へ漏れ出ないよう
にしている。また上記機内側シールリング（１３１）と
機外側シールリング（１３２） とは回転体（１０１）
の振れ廻りに追従して半径方向に動きうるようになって
おり、シール流体が回転板（１０１）の自動振動を増長
させない特性をもっている。つまりシール部が回転板（
１０１）の振動に対して何等影響を与えないように配慮
されている。(Prior Art) A conventional bearing device and seal device for a rotating machine will be explained with reference to Fig. 7.8. (101) in Fig. 7 is a rotating body, and both ends of the rotating body (101) are bearing units 102)
(102), and is rotatably supported by the rotating body (l
A seal unit ) (103) (103) for sealing the working fluid in the casing (IO2) is provided in the penetrating portion of the casing (105) through which the casing (105) is penetrated. Furthermore, as shown in FIG. 8, the bearing unit (102) absorbs the static load and dynamic load of the 5-rotating body (101) by the oil III (115) formed between the bearing metal (111) and the rotating body (101). It supports the load. In addition, the above casing (1
05) has a seal flange (134) in the rotating body penetration part.
and a sealing ring (133), and the seal unit (103) has one inner sealing ring (133).
1) and a seal ring (132) on the outside of the machine, and each of the seal rings (131) 8132) and a rotating body (101).
), and a seal fluid supply hole (105a) provided in the casing (105).
) is supplied to the minute gap to prevent the working fluid inside the casing (105) from leaking to the outside. In addition, the above-mentioned inboard seal ring (131) and outboard seal ring (132) are the rotating body (101).
The rotary plate (101) can move in the radial direction following the swing of the rotating plate (101), and the sealing fluid has a characteristic that does not increase the automatic vibration of the rotary plate (101). In other words, the seal part is a rotating plate (
101) so as not to have any influence on the vibrations.
（発明が解決しようとする問題点）
一般に回転機械では１回転機械の流体力学的な効率を向
上するために、細くて長い回転体を高速回転させようと
する要求が強い。ところが前記第７．８図に示すように
、細くて長い回転体（１０１）の両端部を軸受ユニッＩ
−（１０２）で支持した場合。(Problems to be Solved by the Invention) In general, in rotating machines, there is a strong demand for rotating thin and long rotating bodies at high speed in order to improve the hydrodynamic efficiency of single-rotation machines. However, as shown in Fig. 7.8, both ends of the long and thin rotating body (101) are connected to the bearing unit I.
- When supported by (102).
回転体（１０１）の曲げ剛性が低下して、ケーシング（
１，０５）内にある作動流体の作用により回転体（１０
１）に不安定振動が発生し易くなる。この不安定振動は
、自動的に成長して２回転体（１０１）がケーシング（
１０５）内の静止部材に接触したり２回転機械の運転に
支障を生じたりする。このような現象を防止するために
、従来は、効率を犠牲にして回転体（１０１）の長さを
短くしたり、ケーシング数を増やして効率を確保したり
しており、経済性が低い上に、取り扱いの困難な回転機
械になっていた。The bending rigidity of the rotating body (101) decreases, causing the casing (
The rotating body (10
1) Unstable vibration is likely to occur. This unstable vibration automatically grows and the two rotating bodies (101) move towards the casing (
105) or may interfere with the operation of the two-rotation machine. In order to prevent this phenomenon, conventional methods have been to shorten the length of the rotating body (101) at the expense of efficiency, or increase the number of casings to ensure efficiency, which is not only economically efficient but also This resulted in a rotating machine that was difficult to handle.
（問題点を解決するための手段）
本発明は前記の問題点に対処するもので２回転体が貫通
する静止部材の貫通孔内周面に環状溝を設け、同環状溝
両側の静止部材両側部と同回転体との間をシールリング
によりシールし、前記環状溝内に軸受用可動リングを収
容し、同可動リングを前記静止部材に半径方向の移動の
みを可能に取り付けて、同可動リングの外周面と前記環
状溝の内周面との間に外側の環状間隙を形成するととも
に、同可動リングの内孔内周面と同内孔を貫通する前記
回転体の外周面との間に内側の環状間隙を形成し、同内
側の環状間隙を複数の円弧状間隙部に区画するとともに
、同各円弧状間隙部を回転体の回転方向下流側に向かっ
て次第に狭くなる楔状にし、前記潤滑油供給孔からの潤
滑油を前記外側及び内側の環状間隙に潤滑油を供給する
潤滑油供給孔を前記前記静止部材に設けたことを特徴と
する回転機械の軸受兼シール装置に係わり、その目的と
する処は１回転機械の効率を犠牲にしたり。(Means for Solving the Problems) The present invention addresses the above-mentioned problems by providing an annular groove on the inner circumferential surface of a through hole of a stationary member through which two rotating bodies pass, and forming an annular groove on both sides of the stationary member on both sides of the annular groove. A seal ring is used to seal between the part and the rotating body, a movable ring for a bearing is housed in the annular groove, and the movable ring is attached to the stationary member so as to be movable only in the radial direction. an outer annular gap is formed between the outer circumferential surface of the movable ring and the inner circumferential surface of the annular groove, and between the inner circumferential surface of the inner hole of the movable ring and the outer circumferential surface of the rotating body passing through the inner hole. An inner annular gap is formed, the inner annular gap is divided into a plurality of arcuate gaps, and each of the arcuate gaps is shaped into a wedge that gradually narrows toward the downstream side in the rotational direction of the rotating body, and the lubrication The object of the present invention relates to a bearing-cum-sealing device for a rotating machine, characterized in that a lubricating oil supply hole is provided in the stationary member for supplying lubricating oil from an oil supply hole to the outer and inner annular gaps. In doing so, the efficiency of single-rotation machines may be sacrificed.
ケーシング数の増やしたすせずに、不安定振動の発生を
抑制できる。また軸受ユニットを別途設ける必要がなく
て、製作コストを低減できる改良された回転機械の軸受
兼シール装置を供する点にある。Unstable vibration can be suppressed without increasing the number of casings. Another object of the present invention is to provide an improved bearing/seal device for a rotating machine that does not require a separate bearing unit and can reduce manufacturing costs.
（作用）
本発明の回転体の軸受兼シール装置は前記のように可動
リングの内孔内周面と同内孔を貫通する回転体の外周面
との間に形成される内側の環状間隙が複数の円弧状間隙
部に区画されるとともに。(Function) As described above, the bearing and sealing device for a rotating body of the present invention has an inner annular gap formed between the inner circumferential surface of the inner hole of the movable ring and the outer circumferential surface of the rotating body passing through the inner hole. It is divided into a plurality of arcuate gaps.
同各円弧状間隙部が回転体の回転方向下流側に向かって
次第に狭くなる楔状になっており１回転体の回転ととも
にこの部分の潤滑油が間隙挟小部に向かい流動し、同潤
滑油に模作用が発生して、同潤滑油が剛性の非常に高い
流体膜になる。一方。Each of the arcuate gaps has a wedge shape that gradually narrows toward the downstream side in the rotational direction of the rotating body, and as the rotating body rotates, the lubricating oil in these parts flows toward the narrowing gap, and the lubricating oil A mimetic effect occurs and the lubricant becomes a very stiff fluid film. on the other hand.
可動リングの外周面と環状溝の内周面との間に形成され
る外側の環状間隙には、スクイズ作用により回転体の振
動を減衰する潤滑油膜が形成されており３回転体の振動
が上記内側の環状間隙に形成される剛性の高い潤滑油膜
と半径方向に移動可能な可動リングとを介し上記外側の
環状間隙間に形成される潤滑油膜に伝えられて９回転体
の不安定振動が効果的に抑制される。A lubricating oil film is formed in the outer annular gap formed between the outer circumferential surface of the movable ring and the inner circumferential surface of the annular groove, which damps the vibrations of the rotating bodies through a squeezing action. The unstable vibration of the nine rotating bodies is transmitted to the lubricating oil film formed in the outer annular gap through the highly rigid lubricating oil film formed in the inner annular gap and the movable ring that is movable in the radial direction. is suppressed.
また本発明の軸受兼シール装置では、上記のように回転
体の不安定振動が効果的に抑制されるので、前記第７，
８図に示した従来装置のように軸受ユニットが不要で、
構造が簡単になって、製作コストが低減される。Further, in the bearing/seal device of the present invention, the unstable vibration of the rotating body is effectively suppressed as described above, so the seventh,
Unlike the conventional device shown in Figure 8, there is no need for a bearing unit.
The structure is simplified and manufacturing costs are reduced.
（実施例）
次に本発明の回転体のシール装置を第１図乃至第５図に
示す一実施例により説明すると、第１図の（１）が回転
体、（３）が軸受兼シール装置、（５）がケーシングで
ある。また上記軸受兼シール装置（３）の詳細を示す第
２図乃至第６図において、（３４）が上記ケーシング（
５）に一体のシールフランジ（静止部材） 、 （３３
）が上記ケーシング（５）に一体のシールハウジング（
静止部材）で、こられのシールハウジング（３３）とシ
ールフランジ（３４）とで環状溝が形成されている。ま
た（３１）が機内側シールリング、 （３２）が機外側
シールリングで、これら環状溝両側のシールリング（３
１） （３２）により上記環状溝内が機内側及び機外側
に対してシールされている。また（５０）が上記ケーシ
ング（５）及び上記シールハウジング（３３）に設けた
潤滑油供給孔で、潤滑油が同潤滑油供給孔（５０）を経
て上記環状溝内へ供給されるようになっている。また（
４１）が上記環状溝内に収容した可動リング、第２．４
．５図の（４３）が上記可動リングク３１）に取付けた
廻り止めピンで、上記可動リング（４１）が同廻り止め
ビン（４３）により半径方向の移動のみを可能にシール
フランジ（３４）に支持されている。また（４６）が同
可動リング（４１）の外周面と上記環状溝の内周面との
間に形成した外側の環状間隙、 （４５）が同可動リン
グ（４１）の内孔内周面と同内孔を貫通する上記回転体
（１）の外周面との間に形成した内側の環状間隙、第３
図の（４７）が同内側の環状間隙（４５）の軸線を挟む
対称位置に設けた２つの軸方向溝で、同内側の環状間隙
（４５）が同各軸方向溝（４７）で２つの円弧状間隙部
に区画され、同各円弧状間隙部が回転体（１）の回転方
向（第３図の矢印参照）下流側に向かって次第に狭くな
る楔状になっている。また第２図の（４２） （４２）
が上記可動リング（４１）の両側部と上記シールハウジ
ング（３３）との間に介装した０リング、（４８）が上
記シールハウジング（３３）を貫通した潤滑油供給孔で
、同潤滑油供給孔（４８）が上記潤滑油供給孔（５０）
と上記外側の環状間隙（４６）とを連絡している。また
（４９）が潤滑油供給孔で、同潤滑油供給孔（４９）が
上記外側の環状間隙（４６）と上記機外側シールリング
（３２）内側のシール装置内とを連絡している。(Embodiment) Next, the sealing device for a rotating body according to the present invention will be explained using an embodiment shown in FIGS. 1 to 5. In FIG. , (5) is the casing. In addition, in FIGS. 2 to 6 showing details of the bearing/seal device (3), (34) is the casing (3).
5) integral seal flange (stationary member), (33
) is a seal housing (
The seal housing (33) and the seal flange (34) form an annular groove. Also, (31) is the inboard seal ring, (32) is the outboard seal ring, and the seal rings (3) on both sides of the annular groove are
1) The inside of the annular groove is sealed from the inside of the machine and the outside of the machine by (32). Further, (50) is a lubricating oil supply hole provided in the casing (5) and the seal housing (33), and lubricating oil is supplied into the annular groove through the lubricating oil supply hole (50). ing. Also(
41) is a movable ring housed in the annular groove, No. 2.4;
．． (43) in Fig. 5 is a rotation stop pin attached to the movable ring 31), and the movable ring (41) is supported by the seal flange (34) by the rotation stop pin (43) so that it can only move in the radial direction. has been done. Further, (46) is an outer annular gap formed between the outer peripheral surface of the movable ring (41) and the inner peripheral surface of the annular groove, and (45) is the outer annular gap formed between the inner peripheral surface of the inner hole of the movable ring (41). an inner annular gap formed between the outer circumferential surface of the rotating body (1) passing through the inner hole;
(47) in the figure are two axial grooves provided at symmetrical positions across the axis of the annular gap (45) on the same inner side, and the annular gap (45) on the same inner side has two axial grooves (47) in each axial direction. It is divided into arc-shaped gaps, and each arc-shaped gap has a wedge shape that gradually narrows toward the downstream side in the rotation direction of the rotating body (1) (see the arrow in FIG. 3). Also (42) (42) in Figure 2
is an O-ring interposed between both sides of the movable ring (41) and the seal housing (33), and (48) is a lubricating oil supply hole passing through the seal housing (33) for supplying the same lubricating oil. The hole (48) is the lubricating oil supply hole (50).
and the outer annular gap (46). Further, (49) is a lubricating oil supply hole, and the lubricating oil supply hole (49) communicates between the outer annular gap (46) and the inside of the seal device inside the outer side seal ring (32).
次に前記第１図乃至第５図に示す回転体の軸受兼シール
装置の作用を具体的に説明する。可動リング（４１）の
内孔内周面と同内孔を貫通する回転体（１）の外周面と
の間に形成される内側の環状間隙（４５）が複数の円弧
状間隙部に区画されるとともに。Next, the operation of the bearing/seal device for the rotating body shown in FIGS. 1 to 5 will be specifically explained. An inner annular gap (45) formed between the inner peripheral surface of the inner hole of the movable ring (41) and the outer peripheral surface of the rotating body (1) passing through the inner hole is divided into a plurality of arc-shaped gaps. Along with.
同各円弧状間隙部が回転体（１）の回転方向下流側に向
かって次第に狭くなる楔状になっており１回転体（１）
の回転とともにこの部分の潤滑油が間隙挟小部に向かい
流動し、同潤滑油に楔作用が発生して、同潤滑油が剛性
の非常に高い流体膜になる。Each of the arc-shaped gaps has a wedge shape that gradually narrows toward the downstream side in the rotational direction of the rotating body (1).
As the lubricating oil rotates, the lubricating oil in this part flows toward the gap narrowing part, a wedge action occurs in the lubricating oil, and the lubricating oil becomes a very rigid fluid film.
一方、可動リング（４１）の外周面と環状溝の内周面と
の間に形成される外側の環状間隙（４６）には、スクイ
ズ作用により回転体（１，）の振動を減衰する潤滑油膜
が形成されており９回転体（１）の振動が上記内側の環
状間隙（４５）に形成される剛性の高い潤滑油膜と半径
方向に移動可能な可動リング（４１）とを介し上記外側
の環状間隙間（４６）に形成される潤滑油膜に伝えられ
て１回転体（１）の不安定振動が効果的に抑制される。On the other hand, in the outer annular gap (46) formed between the outer circumferential surface of the movable ring (41) and the inner circumferential surface of the annular groove, there is a lubricating oil film that damps vibrations of the rotating body (1,) by a squeezing action. The vibration of the rotating body (1) is transmitted through the highly rigid lubricating oil film formed in the inner annular gap (45) and the radially movable movable ring (41) to the outer annular gap (45). The unstable vibrations of the rotating body (1) are effectively suppressed by being transmitted to the lubricating oil film formed in the gap (46).
第６図は、上記内側め環状間隙（４５）を４つの軸方向
溝（４７）で４つの円弧状間隙部に区画した以外。In FIG. 6, the inner annular gap (45) is divided into four arcuate gap parts by four axial grooves (47).
第１図乃至第５図の実施例と同様に構成した他の実施例
で、この実施でも同様の作用が達成される。Another embodiment is constructed similarly to the embodiment of FIGS. 1-5, and similar effects are achieved in this implementation.
（発明の効果）
本発明の回転体の軸受兼シール装置は前記のように可動
リングの内孔内周面と同内孔を貫通する回転体の外周面
との間に形成される内側の環状間隙が複数の円弧状間隙
部に区画されるとともに。(Effects of the Invention) As described above, the bearing and sealing device for a rotating body of the present invention has an inner annular shape formed between the inner circumferential surface of the inner hole of the movable ring and the outer circumferential surface of the rotating body passing through the inner hole. The gap is divided into a plurality of arcuate gap parts.
同各円弧状間隙部が回転体の回転方向下流側に向かって
次第に狭くなる楔状になっており９回転体の回転ととも
にこの部分の潤滑油が間隙挟小部に向かい流動し、同潤
滑油に楔作用が発生して、同潤滑油が剛性の非常に高い
流体膜になる。一方。Each of the arc-shaped gaps has a wedge shape that gradually narrows toward the downstream side in the rotational direction of the rotating body, and as the rotating body rotates, the lubricating oil in this area flows toward the narrowing gap, and the lubricating oil A wedge action occurs, causing the lubricating oil to form a very stiff fluid film. on the other hand.
可動リングの外周面と環状溝の内周面との間に形成され
る外側の環状間隙には、スクイズ作用により回転体の振
動を減衰する潤滑油膜が形成されており１回転体の振動
が上記内側の環状間隙に形成される剛性の高い潤滑油膜
と半径方向に移動可能な可動リングとを介し上記外側の
環状間隙間に形成される潤滑油膜に伝えられて１回転体
の不安定振動を効果的に抑制できる。A lubricating oil film is formed in the outer annular gap formed between the outer circumferential surface of the movable ring and the inner circumferential surface of the annular groove, which damps the vibrations of the rotating body through a squeezing action. The unstable vibration of the rotating body is transmitted to the lubricating oil film formed in the outer annular gap through the highly rigid lubricating oil film formed in the inner annular gap and the movable ring that is movable in the radial direction. can be suppressed.
また本発明の軸受兼シール装置では、上記のように回転
体の不安定振動が効果的に抑制されるので、前記第７，
８図に示した従来装置のように軸受ユニットが不要で、
構造を簡単化できて、製作コストを低減できる効果があ
る。Further, in the bearing/seal device of the present invention, the unstable vibration of the rotating body is effectively suppressed as described above, so the seventh,
Unlike the conventional device shown in Figure 8, there is no need for a bearing unit.
This has the effect of simplifying the structure and reducing manufacturing costs.
以上本発明を実施例により説明したが、勿論本発明はこ
のような実施例だけに局限されるものでなく５本発明の
精神を逸脱しない範囲で種々の設計の改変を施しうるち
のである。Although the present invention has been described above with reference to embodiments, it goes without saying that the present invention is not limited to these embodiments, and can be modified in various ways without departing from the spirit of the present invention.
第１図は本発明に係わる回転機械の軸受兼シール装置の
一実施例を示す縦断側面図、第２図はその要部を拡大し
て示す縦断側面図、第３図は第２図矢視ｍ−ｍ線に沿う
縦断正面図、第４図は廻り止めピン部分の拡大縦断側面
図、第５図は第４図矢視Ｖ−Ｖ線に沿う縦断背面図、第
６図は他の実施例を示す縦断側面図、第７図は従来の回
転機械のシール装置及び軸受装置を示す縦断側面図、第
８図は他の従来例を示す縦断側面図である。
（１）・・・回転体、（３）・・・軸受兼シール装置。
（５） （３４） （３５） ・・・静止部材、 （
３１）（３２）・・・シールリング、 （４１）・・・
可動リング、 （４５）・・・内側の環状間隙、 （４
６）・・・外側の環状間隙、（４７）・・・内側の環状
間隙（４５）を複数の円弧状間隙部に区画する軸方向溝
。（５０）・・・潤滑油供給孔。
復代理人弁理士岡本重文外２名
地口慮
蝕
洒９凶
第６図Fig. 1 is a longitudinal side view showing an embodiment of a bearing/seal device for a rotating machine according to the present invention, Fig. 2 is a longitudinal side view showing an enlarged view of the main parts thereof, and Fig. 3 is a view taken from the arrow in Fig. 2. Fig. 4 is an enlarged longitudinal sectional side view of the rotation stopper pin portion, Fig. 5 is a longitudinal rear view taken along the arrow V-V line in Fig. 4, and Fig. 6 is another implementation. FIG. 7 is a vertical side view showing an example of a sealing device and bearing device of a conventional rotary machine, and FIG. 8 is a vertical side view showing another conventional example. (1)...Rotating body, (3)...Bearing/sealing device. (5) (34) (35) ...stationary member, (
31) (32)... Seal ring, (41)...
Movable ring, (45)...inner annular gap, (4
6)...Outer annular gap, (47)...An axial groove that divides the inner annular gap (45) into a plurality of arcuate gap parts. (50)...Lubricating oil supply hole. Sub-representative Patent Attorney Okamoto's 2 Famous Locations, Considerations, and Punishments Figure 6
Claims (1)
け、同環状溝両側の静止部材両側部と同回転体との間を
シールリングによりシールし、前記環状溝内に軸受用可
動リングを収容し、同可動リングを前記静止部材に半径
方向の移動のみを可能に取り付けて、同可動リングの外
周面と前記環状溝の内周面との間に外側の環状間隙を形
成するとともに、同可動リングの内孔内周面と同内孔を
貫通する前記回転体の外周面との間に内側の環状間隙を
形成し、同内側の環状間隙を複数の円弧状間隙部に区画
するとともに、同各円弧状間隙部を回転体の回転方向下
流側に向かって次第に狭くなる楔状にし、前記潤滑油供
給孔からの潤滑油を前記外側及び内側の環状間隙に潤滑
油を供給する潤滑油供給孔を前記前記静止部材に設けた
ことを特徴とする回転機械の軸受兼シール装置。An annular groove is provided on the inner peripheral surface of the through hole of the stationary member through which the rotating body passes, a seal ring is used to seal between both sides of the stationary member on both sides of the annular groove and the rotating body, and a movable groove for a bearing is provided in the annular groove. a ring, the movable ring is attached to the stationary member so as to be movable only in the radial direction, and an outer annular gap is formed between the outer peripheral surface of the movable ring and the inner peripheral surface of the annular groove; , an inner annular gap is formed between the inner circumferential surface of the inner hole of the movable ring and the outer circumferential surface of the rotating body passing through the inner hole, and the inner annular gap is divided into a plurality of arc-shaped gaps. At the same time, each arcuate gap is formed into a wedge shape that gradually narrows toward the downstream side in the rotational direction of the rotating body, and lubricating oil is supplied from the lubricating oil supply hole to the outer and inner annular gaps. A bearing/seal device for a rotating machine, characterized in that a supply hole is provided in the stationary member.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP61053578A JPS62215124A (en) | 1986-03-13 | 1986-03-13 | Bearing and sealing device for rotary machine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP61053578A JPS62215124A (en) | 1986-03-13 | 1986-03-13 | Bearing and sealing device for rotary machine |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS62215124A true JPS62215124A (en) | 1987-09-21 |
Family
ID=12946714
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP61053578A Pending JPS62215124A (en) | 1986-03-13 | 1986-03-13 | Bearing and sealing device for rotary machine |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS62215124A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2015083697A1 (en) * | 2013-12-04 | 2015-06-11 | 三菱重工業株式会社 | Squeeze film damper, bearing unit, and turbine |
| JP2015124871A (en) * | 2013-12-27 | 2015-07-06 | 三菱重工業株式会社 | Bearing device |
| JP2015124870A (en) * | 2013-12-27 | 2015-07-06 | 三菱重工業株式会社 | Bearing device |
-
1986
- 1986-03-13 JP JP61053578A patent/JPS62215124A/en active Pending
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2015083697A1 (en) * | 2013-12-04 | 2015-06-11 | 三菱重工業株式会社 | Squeeze film damper, bearing unit, and turbine |
| JPWO2015083697A1 (en) * | 2013-12-04 | 2017-03-16 | 三菱重工業株式会社 | Squeeze film damper, bearing unit and turbine |
| US9890810B2 (en) | 2013-12-04 | 2018-02-13 | Mitsubishi Heavy Industries, Ltd. | Squeeze film damper, bearing unit, and turbine |
| JP2015124871A (en) * | 2013-12-27 | 2015-07-06 | 三菱重工業株式会社 | Bearing device |
| JP2015124870A (en) * | 2013-12-27 | 2015-07-06 | 三菱重工業株式会社 | Bearing device |
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