JP2003148632A - Rotating shaft seal mechanism for rotary machine - Google Patents
Rotating shaft seal mechanism for rotary machineInfo
- Publication number
- JP2003148632A JP2003148632A JP2001346490A JP2001346490A JP2003148632A JP 2003148632 A JP2003148632 A JP 2003148632A JP 2001346490 A JP2001346490 A JP 2001346490A JP 2001346490 A JP2001346490 A JP 2001346490A JP 2003148632 A JP2003148632 A JP 2003148632A
- Authority
- JP
- Japan
- Prior art keywords
- storage chamber
- chamber
- rotating shaft
- fluid storage
- low
- 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
Landscapes
- Sealing Using Fluids, Sealing Without Contact, And Removal Of Oil (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は回転機械の回転軸シ
ール機構に関する。さらに詳細には２軸ターボファンエ
ンジンの回転軸シール機構に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rotary shaft seal mechanism for a rotary machine. More specifically, it relates to a rotary shaft seal mechanism for a two-axis turbofan engine.
【０００２】[0002]
【従来の技術】回転機械の回転軸シール機構として、例
えば、図２に示すような２軸ターボファンエンジン（ジ
ェットエンジンの一種）における空気圧縮機用のタービ
ン駆動軸とファン回転駆動軸との間のシールには、図３
に示す如き流体シール（Hydraulic Seal）機構が使用さ
れている。2. Description of the Related Art As a rotary shaft seal mechanism for a rotary machine, for example, a space between a turbine drive shaft and a fan rotary drive shaft for an air compressor in a two-axis turbofan engine (a kind of jet engine) as shown in FIG. The seal of Figure 3
The fluid seal (Hydraulic Seal) mechanism as shown in is used.
【０００３】図２に示すように、２軸ターボファンエン
ジン１０１は、エンジン外筒１０２内部に設けた空気圧
縮機１０３、燃焼室１０５および空気圧縮機用タービン
１０７などからなるターボジェット（コアエンジン）を
間にはさんで、空気圧縮機１０３の前に設けた大口径の
ファン１０９を後端のファンタービン１１１で回す構造
となっている。As shown in FIG. 2, a twin-screw turbofan engine 101 is a turbojet (core engine) including an air compressor 103, a combustion chamber 105, and an air compressor turbine 107 provided inside an engine outer cylinder 102. With a structure in which a large-diameter fan 109 provided in front of the air compressor 103 is rotated by a fan turbine 111 at the rear end with the fan turbine 111 interposed therebetween.
【０００４】エンジン外筒１０２の周囲にはファンケー
ス１１２を介してカウル１１４が設けてあり、このカウ
ル１１４とエンジン外筒１０２との間の空間をファン１
０９からの外気が流れると共に、外気の一部はエンジン
内部に取り込まれて空気圧縮機１０３に送られるように
なっている。A cowl 114 is provided around the engine outer cylinder 102 via a fan case 112. The space between the cowl 114 and the engine outer cylinder 102 is a fan 1.
While the outside air from 09 flows, a part of the outside air is taken into the engine and sent to the air compressor 103.
【０００５】空気圧縮機１０３を回転駆動するタービン
駆動軸（第２回転軸）１１３は、タービン１０７によっ
て高速度（15,000r.p.m程度）で回転駆動されており、
一方ファン回転駆動軸（第１回転軸）１１５は、ファン
タービン１１１によってタービン駆動軸１１３よりは低
速度（5,000r.p.m程度）で同一方向に回転駆動されてい
る。A turbine drive shaft (second rotary shaft) 113 for rotating the air compressor 103 is driven to rotate by a turbine 107 at a high speed (about 15,000 rpm).
On the other hand, the fan rotation drive shaft (first rotation shaft) 115 is rotationally driven in the same direction by the fan turbine 111 at a lower speed (about 5,000 rpm) than the turbine drive shaft 113.
【０００６】上述のタービン駆動軸（第２回転軸）１１
３は中空軸になっており、このタービン駆動軸（第２回
転軸）１１３の外周に空気圧縮機用の複数枚の動翼１１
７を備えている。前述のファン回転駆動軸（第１回転
軸）１１５はタービン駆動軸（第２回転軸）１１３の中
空軸部１１９を貫通するように設けてあり、その前端部
に前述のファン１０９が設けてある。The above-mentioned turbine drive shaft (second rotary shaft) 11
3 is a hollow shaft, and a plurality of moving blades 11 for an air compressor are provided on the outer circumference of the turbine drive shaft (second rotating shaft) 113.
Equipped with 7. The above-described fan rotation drive shaft (first rotation shaft) 115 is provided so as to penetrate the hollow shaft portion 119 of the turbine drive shaft (second rotation shaft) 113, and the above-described fan 109 is provided at the front end portion thereof. .
【０００７】図３に示すように、前記タービン駆動軸
（第２回転軸）１１３の中空軸部１１９の前端部（図３
において左側）は低圧流体室に連通しており、この低圧
流体室に連通する軸端部（前端部）に軸心方向に開口す
る環状の流体貯留室１２１を設け、前記ファン回転駆動
軸（第１回転軸）１１５には、この環状の流体貯留室１
２１の内部へ伸張するフランジ１２３を設け、このフラ
ンジ１２３により前記流体貯留室１２１に環状のＵ字形
流体貯留室１２５を形成してある。As shown in FIG. 3, the front end portion of the hollow shaft portion 119 of the turbine drive shaft (second rotary shaft) 113 (see FIG. 3).
On the left side) communicates with the low-pressure fluid chamber, and an annular fluid storage chamber 121 that opens in the axial direction is provided at the shaft end (front end) that communicates with the low-pressure fluid chamber. One rotation shaft) 115 has an annular fluid storage chamber 1
21 is provided with a flange 123 that extends to the inside, and the flange 123 forms an annular U-shaped fluid storage chamber 125 in the fluid storage chamber 121.
【０００８】上述の環状のＵ字形流体貯留室１２５に
は、タービンの起動と同時に水または油などのシール液
体（水または油）１２７が注入手段１２９から注入され
る。このシール液体１２７はタービン駆動軸１１３の回
転による遠心力によりＵ字形流体貯留室１２５の底面
（円周面）に保持されると共に、前記中空軸部１１９に
連通する高圧流体室内の高温の高圧流体（約４００℃の
空気）側と、中空軸部１１９を介して連通する前記高圧
流体室の外側空間にある低圧流体室（約１８０℃の空
気）側との圧力差により液面差Ｈでバランスして高温の
高圧流体が低圧室側へ流れないようにシールする。A sealing liquid 127 such as water or oil (water or oil) 127 is injected into the above-mentioned annular U-shaped fluid storage chamber 125 from the injection means 129 at the same time when the turbine is started. The seal liquid 127 is retained on the bottom surface (circumferential surface) of the U-shaped fluid storage chamber 125 by the centrifugal force generated by the rotation of the turbine drive shaft 113, and at the same time, the high temperature high pressure fluid in the high pressure fluid chamber communicating with the hollow shaft portion 119. The liquid level difference H is balanced by the pressure difference between the (air of about 400 ° C.) side and the low pressure fluid chamber (air of about 180 ° C.) side in the outer space of the high pressure fluid chamber that communicates via the hollow shaft 119. Then, the high temperature high pressure fluid is sealed so as not to flow to the low pressure chamber side.
【０００９】なお、上述のシール液体１２７はＵ字形流
体貯留室１２５の側方の低圧室側から継続的に注入さ
れ、注入されたシール液体１２７は矢印のような経路に
そって注入側へ排出されるようになっている。The above-mentioned sealing liquid 127 is continuously injected from the side of the U-shaped fluid storage chamber 125 from the low-pressure chamber side, and the injected sealing liquid 127 is discharged to the injection side along the path indicated by the arrow. It is supposed to be done.
【００１０】[0010]
【発明が解決しようとする課題】上述の如き流体シール
機構においては、タービン駆動軸１１３とファン回転駆
動軸１１５との回転速度の差に起因して、シール液体１
２７とフランジ１２３との間に摩擦を生じてシール液体
１２７が発熱する。また、シール液体１２７は液体（水
または油）であり沸点または気化温度が低いため、シー
ル液体１２７の気化により残査（RESIDUE）Ｒを生じ、
長時間（数年または数千時間）の使用に伴い残査ＲがＵ
字形流体貯留室１２５内の底面（円周面）に溜まりシー
ル性能を劣化させる。In the fluid sealing mechanism as described above, the sealing liquid 1 is caused by the difference in rotation speed between the turbine drive shaft 113 and the fan rotation drive shaft 115.
The seal liquid 127 generates heat by generating friction between the seal liquid 127 and the flange 123. Further, since the seal liquid 127 is a liquid (water or oil) and has a low boiling point or vaporization temperature, vaporization of the seal liquid 127 causes a residue (RESIDUE) R,
Residual R is U due to use for a long time (several years or thousands of hours)
It accumulates on the bottom surface (circumferential surface) inside the letter-shaped fluid storage chamber 125 and deteriorates the sealing performance.
【００１１】すなわち、残査ＲがＵ字形流体貯留室１２
５内の底面（円周面）に溜まることで、シール液体１２
７からの放熱が阻害され、シール液体１２７が益々高温
になり易くなる。また、シール液体１２７の流れが変化
してシール性能が低下し、最終的には高圧／低圧間のバ
ランスがとれなくなり、突然低圧側に流入（SEAL BREA
K）し、シール機能を果たさなくなることがある。That is, the residual R is a U-shaped fluid storage chamber 12
By collecting on the bottom surface (circumferential surface) within 5, the sealing liquid 12
The heat radiation from 7 is hindered, and the sealing liquid 127 is likely to become even hotter. In addition, the flow of the seal liquid 127 changes and the sealing performance deteriorates, and eventually the high pressure / low pressure is not balanced and suddenly flows into the low pressure side (SEAL BREAK).
K), and the sealing function may not be fulfilled.
【００１２】Ｕ字形流体貯留室１２５内に溜まった残査
を除くため、定期的な清掃をすればよいが、ジェットエ
ンジン全体の分解が必要で、短期（約1〜5年または1000
〜5000時間）ごとの清掃はコスト的に困難である。[0012] To remove the residue accumulated in the U-shaped fluid storage chamber 125, periodical cleaning may be performed, but it is necessary to disassemble the entire jet engine, and it is necessary to disassemble the jet engine for a short period (about 1 to 5 years or 1000 times).
Cleaning every ~ 5000 hours is difficult in terms of cost.
【００１３】また、シール液体１２７の注入は、構造的
に注入側から排出されるので、Ｕ字形流体貯留室１２５
内で充分に循環されずシール液体１２７の冷却が不十分
となる。さらに、タービン駆動軸１１３は高速で回転し
ているので注入口で飛散してＵ字形流体貯留室１２５内
に入りにくいという問題がある。Since the seal liquid 127 is structurally discharged from the injection side, the U-shaped fluid storage chamber 125 is used.
It is not sufficiently circulated in the inside, and the sealing liquid 127 is insufficiently cooled. Further, since the turbine drive shaft 113 rotates at a high speed, there is a problem that it is difficult to scatter at the inlet and enter the U-shaped fluid storage chamber 125.
【００１４】本発明は上述の如き問題を解決するために
なされたものであり、本発明の課題は、シール液体を低
温度に維持可能な、かつシール液体の気化を抑制した回
転機械の回転軸シール機構を提供することである。The present invention has been made to solve the above problems, and an object of the present invention is to provide a rotary shaft of a rotary machine capable of maintaining the seal liquid at a low temperature and suppressing vaporization of the seal liquid. It is to provide a sealing mechanism.
【００１５】[0015]
【課題を解決するための手段】上述の課題を解決する手
段として請求項１に記載の回転機械の回転軸シール機構
は、第１回転軸と該第１回転軸の外側に同軸に設けた第
１回転軸より高速に回転する第２回転軸とを備え、該第
２回転軸の中空軸部の一側に連通する高圧流体室と、前
記中空軸部の他側に連通する低圧流体室との間をシール
する回転機械の回転軸シール機構にして、前記第２回転
軸の中空軸部が前記低圧流体室に連通する側の軸端部に
軸心方向に開口する環状の流体貯留室を設け、該流体貯
留室内部へ伸張するフランジを前記第１回転軸に設け、
該流体貯留室内に環状のＵ字形流体貯留室を形成し、前
記第１回転軸と第２回転軸の回転時に前記低圧流体室側
から前記Ｕ字形流体貯留室内へシール液体を連続的に注
入し、前記Ｕ字形流体貯留室内に高圧側と低圧側の圧力
差でバランス保持されたシール液体により前記高圧流体
室と前記低圧流体室間の流体の流通を遮断すると共に、
前記Ｕ字形流体貯留室内に注入したシール液体を前記Ｕ
字形流体貯留室側方の前記低圧流体室へ排出させる排出
手段を設けたことを要旨とするものである。According to a first aspect of the present invention, there is provided a rotary shaft sealing mechanism for a rotary machine, comprising: a first rotary shaft and a first rotary shaft coaxially provided outside the first rotary shaft. A second rotary shaft rotating at a higher speed than the first rotary shaft; a high-pressure fluid chamber communicating with one side of the hollow shaft portion of the second rotary shaft; and a low-pressure fluid chamber communicating with the other side of the hollow shaft portion. A rotary shaft sealing mechanism for a rotary machine that seals the space between the second rotary shaft and an annular fluid storage chamber that opens in the axial direction at the shaft end on the side where the hollow shaft portion of the second rotary shaft communicates with the low pressure fluid chamber. And a flange extending to the inside of the fluid storage chamber is provided on the first rotating shaft,
An annular U-shaped fluid storage chamber is formed in the fluid storage chamber, and a seal liquid is continuously injected into the U-shaped fluid storage chamber from the low pressure fluid chamber side when the first rotating shaft and the second rotating shaft rotate. , Blocking the flow of fluid between the high-pressure fluid chamber and the low-pressure fluid chamber by a seal liquid balanced in the U-shaped fluid storage chamber by a pressure difference between the high-pressure side and the low-pressure side,
The seal liquid injected into the U-shaped fluid storage chamber
The gist of the present invention is to provide a discharge means for discharging to the low pressure fluid chamber on the side of the letter-shaped fluid storage chamber.
【００１６】請求項２に記載の回転機械の回転軸シール
機構は、請求項１に記載の回転機械の回転軸シール機構
において、前記高圧流体および低圧流体が気体であり、
前記シール液体が水または油であることを要旨とするも
のである請求項３に記載の回転機械の回転軸シール機構
は、請求項１または請求項２に記載の回転機械の回転軸
シール機構において、前記排出手段は、前記第１回転軸
と第２回転軸の回転時に前記Ｕ字形流体貯留室にバラン
ス保持されたシール液体の低圧側の液面より高い液面を
有するドレイン室を前記Ｕ字形流体貯留室に隣接して設
けたことを要旨とするものである。A rotary shaft sealing mechanism for a rotary machine according to a second aspect is the rotary shaft sealing mechanism for a rotary machine according to the first aspect, wherein the high pressure fluid and the low pressure fluid are gases,
The rotary shaft seal mechanism for a rotary machine according to claim 3, wherein the seal liquid is water or oil. The rotary shaft seal mechanism for a rotary machine according to claim 1 or 2, The drain means has a U-shaped drain chamber having a liquid level higher than a low-pressure side liquid level of the seal liquid balanced in the U-shaped fluid storage chamber when the first rotary shaft and the second rotary shaft rotate. The gist is that it is provided adjacent to the fluid storage chamber.
【００１７】[0017]
【発明の実施の形態】以下本発明の実施の形態を図面に
よって説明する。BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of the present invention will be described below with reference to the drawings.
【００１８】図１は本発明に係わる回転機械の回転軸シ
ール機構の例として、２軸ターボファンエンジン（ジェ
ットエンジンの一種）における空気圧縮機用のタービン
駆動軸とファン回転駆動軸との間に設けた流体シール
（Hydraulic Seal）機構を示したものであり、図３で説
明した流体シール機構の一部を改良したものである。な
お図３と同一の構成要素には同一の参照符号を付してあ
る。FIG. 1 shows, as an example of a rotary shaft sealing mechanism for a rotary machine according to the present invention, between a turbine drive shaft and a fan rotary drive shaft for an air compressor in a two-shaft turbofan engine (a type of jet engine). 4 is a view showing a provided fluid seal (Hydraulic Seal) mechanism, which is an improvement of a part of the fluid seal mechanism described in FIG. 3. The same components as those in FIG. 3 are designated by the same reference numerals.
【００１９】図１を参照するに、前述のように空気圧縮
機（図示省略）を回転駆動するタービン駆動軸（第２回
転軸）１１３の中空軸部１１９の軸端部（図１において
左側端部）は低圧流体室１に連通しており、この軸端部
に軸心方向に開口する環状の流体貯留室１２１を設けて
ある。また、タービン駆動軸（第２回転軸）１１３の中
空軸部１１９の他端部（図１において右側端部）は高圧
流体室３に連通している。Referring to FIG. 1, a shaft end portion (a left end in FIG. 1) of a hollow shaft portion 119 of a turbine drive shaft (second rotary shaft) 113 that rotationally drives an air compressor (not shown) as described above. Part) communicates with the low-pressure fluid chamber 1, and an annular fluid storage chamber 121 that opens in the axial direction is provided at the end of this shaft. Further, the other end portion (the right end portion in FIG. 1) of the hollow shaft portion 119 of the turbine drive shaft (second rotating shaft) 113 communicates with the high pressure fluid chamber 3.
【００２０】ファン回転駆動軸（第１回転軸）１１５に
は、環状の流体貯留室１２１の内部へ伸張するフランジ
１２３を設け、このフランジ１２３により前記流体貯留
室１２１に環状のＵ字形流体貯留室１２５を形成すると
共に、流体貯留室１２１の右側面に軸心方向に開口した
環状のドレイン室５を設け、このドレイン室５と環状の
流体貯留室１２１との間を連通孔７で連結してある。The fan rotation drive shaft (first rotation shaft) 115 is provided with a flange 123 extending into the annular fluid storage chamber 121, and the flange 123 allows the fluid storage chamber 121 to have an annular U-shaped fluid storage chamber. In addition to forming 125, an annular drain chamber 5 opened in the axial direction is provided on the right side surface of the fluid storage chamber 121, and the drain chamber 5 and the annular fluid storage chamber 121 are connected by a communication hole 7. is there.
【００２１】上述のドレイン室５の側壁９の高さＫは、
Ｕ字形流体貯留室１２５内部のシール液体１２７の液面
高さＪより高く設定してある。なお、ここでいう高さと
は、軸心ＣＬを基準とする高さである。The height K of the side wall 9 of the drain chamber 5 is
It is set higher than the liquid level height J of the seal liquid 127 inside the U-shaped fluid storage chamber 125. The height referred to here is a height based on the axial center CL.
【００２２】なお、前記高圧流体室３には約４００℃の
空気が存在し、前記低圧流体室１には約１８０℃の空気
が存在している。Air of about 400 ° C. is present in the high pressure fluid chamber 3, and air of about 180 ° C. is present in the low pressure fluid chamber 1.
【００２３】上記構成のシール機構において、始めにＵ
字形流体貯留室１２５内にシールに必要な量のシール液
体１２７がＵ字形流体貯留室１２５内に注入手段１２９
から注入されており、さらにジェットエンジンの起動と
同時に循環冷却に必要とする適宜な量のシール液体１２
７が注入手段１２９から連続的に注入される。In the seal mechanism having the above structure, first, U
An amount of the sealing liquid 127 required for sealing is filled in the U-shaped fluid storage chamber 125, and the injection means 129 is injected into the U-shaped fluid storage chamber 125.
And the appropriate amount of the seal liquid 12 required for circulation cooling at the same time when the jet engine is started.
7 is continuously injected from the injection means 129.
【００２４】ジェットエンジンの運転中には、前述のよ
うに、タービン駆動軸（第２回転軸）１１３は高速度
（15,000r.p.m程度）で回転しており、一方ファン回転
駆動軸（第１回転軸）１１５は、ファンタービン（図示
省略）によってタービン駆動軸１１３よりは低速度（5,
000r.p.m程度）で同一方向に回転駆動されている。During operation of the jet engine, as described above, the turbine drive shaft (second rotary shaft) 113 is rotating at a high speed (about 15,000 rpm), while the fan rotary drive shaft (first rotary shaft) is rotating. ) 115 is lower than the turbine drive shaft 113 by the fan turbine (not shown) (5,
It is driven to rotate in the same direction at about 000r.pm).
【００２５】その結果、シール液体１２７は、第２回転
軸１１３と第１回転軸との中間程度の速度でＵ字形流体
貯留室１２５内を回転すると同時に、遠心力によりＵ字
形流体貯留室１２５の底面（円周面）に保持され、前記
中空軸部１１９に連通する高圧流体室３内の高温の高圧
流体（空気）側と、中空軸部１１９を介して連通する前
記高圧流体室３の外側空間にある低圧流体室１側との圧
力差により液面差Ｈでバランスして高温の高圧流体（空
気）が低圧室１側へ流れないようにシールする。As a result, the sealing liquid 127 is rotated in the U-shaped fluid storage chamber 125 at a speed about the intermediate speed between the second rotary shaft 113 and the first rotary shaft, and at the same time, centrifugal force causes the U-shaped fluid storage chamber 125 to move. The high pressure fluid (air) side of the high pressure fluid chamber 3 held in the bottom surface (circumferential surface) and communicating with the hollow shaft portion 119 and the outside of the high pressure fluid chamber 3 communicating with the hollow shaft portion 119. The pressure difference with the low pressure fluid chamber 1 side in the space balances the liquid level difference H to seal the high temperature high pressure fluid (air) from flowing to the low pressure chamber 1 side.
【００２６】また、ドレイン室５内のシール液体１２７
は、タービン駆動軸（第２回転軸）１１３と同じ高速度
で回転しているため大きな遠心力が作用し前記液面差Ｈ
を小さくするように働く。Further, the seal liquid 127 in the drain chamber 5
Is rotating at the same high speed as the turbine drive shaft (second rotating shaft) 113, a large centrifugal force acts on the liquid level difference H.
Work to reduce.
【００２７】シール液体１２７の冷却用にＵ字形流体貯
留室１２５に注入手段１２９から注入されたシール液体
１２７は、矢印で示すように、Ｕ字形流体貯留室１２５
から連通孔７を経てドレイン室５に入り、このドレイン
室５の高さＫの側壁９をオーバーフローして低圧流体室
１に排出される。The seal liquid 127 injected from the injection means 129 into the U-shaped fluid storage chamber 125 for cooling the seal liquid 127 is, as indicated by the arrow, the U-shaped fluid storage chamber 125.
Through the communication hole 7 into the drain chamber 5, the side wall 9 of the height K of the drain chamber 5 overflows and is discharged to the low pressure fluid chamber 1.
【００２８】また、ドレイン室５の側壁９の高さＫを適
宜に設定することにより、Ｕ字形流体貯留室１２５内の
低圧側の液面高さＪをＵ字形流体貯留室１２５の壁面高
さＬより高く設定することが可能であるため、冷却用シ
ール液体１２７の外部への飛散を防止して注入効率を改
善することができる。なお、上述のシール液体１２７に
は通常水または油が使用される。Further, by appropriately setting the height K of the side wall 9 of the drain chamber 5, the liquid level height J on the low pressure side in the U-shaped fluid storage chamber 125 is set to the wall surface height of the U-shaped fluid storage chamber 125. Since it can be set higher than L, it is possible to prevent the cooling seal liquid 127 from scattering to the outside and improve the injection efficiency. Water or oil is usually used as the above-mentioned seal liquid 127.
【００２９】[0029]
【発明の効果】請求項１または請求項２の発明によれ
ば、シール液体の冷却用にＵ字形流体貯留室に注入され
たシール液体は、Ｕ字形流体貯留室に隣接して設けたド
レイン室から低圧流体室に排出されるので、Ｕ字形流体
貯留室内のシール液体を充分に冷却することができる。According to the first or second aspect of the present invention, the seal liquid injected into the U-shaped fluid storage chamber for cooling the seal liquid is the drain chamber provided adjacent to the U-shaped fluid storage chamber. Since it is discharged from the low pressure fluid chamber to the low pressure fluid chamber, the seal liquid in the U-shaped fluid storage chamber can be sufficiently cooled.
【００３０】シール液体を低温に維持できるため、シー
ル液体の気化による残査の発生を低減させることが可能
となり、短期（約1〜5年または1000〜5000時間）毎の清
掃省略することが可能となる。また、突然のSEAL BREAK
の危険性が低下しジェットエンジンの信頼性が向上す
る。Since the seal liquid can be maintained at a low temperature, it is possible to reduce the generation of residuals due to vaporization of the seal liquid, and it is possible to omit cleaning every short period (about 1 to 5 years or 1000 to 5000 hours). Becomes Also, sudden SEAL BREAK
The risk of the jet engine is reduced and the reliability of the jet engine is improved.
【００３１】請求項３の発明によれば、Ｕ字形流体貯留
室内の低圧側液面高さＪをＵ字形流体貯留室の壁面高さ
Ｌより高く設定することが可能であるため、注入する冷
却用シール液体の外部への飛散を防止して注入効率を改
善することができる。According to the third aspect of the invention, since the low-pressure side liquid level height J in the U-shaped fluid storage chamber can be set higher than the wall surface height L of the U-shaped fluid storage chamber, the cooling to be injected is performed. It is possible to prevent the sealing liquid for use from scattering to the outside and improve the injection efficiency.
【図１】本発明に係わる回転機械の回転軸シール機構の
説明図。FIG. 1 is an explanatory view of a rotary shaft seal mechanism of a rotary machine according to the present invention.
【図２】回転機械の回転軸シール機構の従来例として、
２軸ターボファンエンジンにおける流体シール（Hydrau
lic Seal）機構の説明図。FIG. 2 shows a conventional example of a rotary shaft sealing mechanism of a rotary machine.
Fluid seal for 2-axis turbofan engine (Hydrau
An illustration of the lic seal mechanism.
【図３】図２におけるＰ部の拡大説明図。FIG. 3 is an enlarged explanatory view of a P portion in FIG.
１ 低圧流体室 ３ 高圧流体室 ５ ドレイン室 ７ 連通孔 ９ 側壁 １１３ タービン駆動軸（第２回転軸） １１５ ファン回転駆動軸（第１回転軸） １１９ 中空軸部 １２１ 環状の流体貯留室 １２３ フランジ １２５ Ｕ字形流体貯留室 １２７ シール液体 1 Low pressure fluid chamber 3 High pressure fluid chamber 5 drain chamber 7 communication holes 9 Side wall 113 Turbine drive shaft (second rotary shaft) 115 Fan rotation drive shaft (first rotation shaft) 119 Hollow shaft 121 annular fluid storage chamber 123 flange 125 U-shaped fluid storage chamber 127 seal liquid
Claims (3)
に設けた第１回転軸より高速に回転する第２回転軸とを
備え、該第２回転軸の中空軸部の一側に連通する高圧流
体室と、前記中空軸部の他側に連通する低圧流体室との
間をシールする回転機械の回転軸シール機構にして、前
記第２回転軸の中空軸部が前記低圧流体室に連通する側
の軸端部に軸心方向に開口する環状の流体貯留室を設
け、該流体貯留室内部へ伸張するフランジを前記第１回
転軸に設け、該流体貯留室内に環状のＵ字形流体貯留室
を形成し、前記第１回転軸と第２回転軸の回転時に前記
低圧流体室側から前記Ｕ字形流体貯留室内へシール液体
を連続的に注入し、前記Ｕ字形流体貯留室内に高圧側と
低圧側の圧力差でバランス保持されたシール液体により
前記高圧流体室と前記低圧流体室間の流体の流通を遮断
すると共に、前記Ｕ字形流体貯留室内に注入したシール
液体を前記Ｕ字形流体貯留室側方の前記低圧流体室へ排
出させる排出手段を設けたことを特徴とする回転機械の
回転軸シール機構。1. A hollow shaft portion of the second rotating shaft, comprising: a first rotating shaft; and a second rotating shaft that is coaxial with the first rotating shaft and that rotates faster than the first rotating shaft. Side of the hollow shaft portion and a low pressure fluid chamber that communicates with the other side of the hollow shaft portion to form a rotary shaft sealing mechanism of a rotary machine. An annular fluid storage chamber that opens in the axial direction is provided at the shaft end on the side that communicates with the fluid chamber, a flange that extends to the inside of the fluid storage chamber is provided on the first rotating shaft, and an annular fluid storage chamber is provided inside the fluid storage chamber. A U-shaped fluid storage chamber is formed, and a seal liquid is continuously injected into the U-shaped fluid storage chamber from the low-pressure fluid chamber side when the first rotating shaft and the second rotating shaft rotate, and the U-shaped fluid storing chamber is formed. And the high pressure fluid chamber and the high pressure side by the seal liquid balanced by the pressure difference between the high pressure side and the low pressure side. Discharging means is provided for blocking the flow of fluid between the low-pressure fluid chambers and discharging the sealing liquid injected into the U-shaped fluid storage chamber to the low-pressure fluid chamber on the side of the U-shaped fluid storage chamber. Rotating shaft seal mechanism for rotating machinery.
ル機構において、前記高圧流体および低圧流体が気体で
あり、前記シール液体が水または油であることを特徴と
する回転機械の回転軸シール機構。2. The rotary shaft seal mechanism for a rotary machine according to claim 1, wherein the high-pressure fluid and the low-pressure fluid are gases, and the seal liquid is water or oil. Seal mechanism.
械の回転軸シール機構において、前記排出手段は、前記
第１回転軸と第２回転軸の回転時に前記Ｕ字形流体貯留
室にバランス保持されたシール液体の低圧側の液面より
高い液面を有するドレイン室を前記Ｕ字形流体貯留室に
隣接して設けたこと特徴とする回転機械の回転軸シール
機構。3. The rotary shaft sealing mechanism for a rotary machine according to claim 1, wherein the discharging means balances the U-shaped fluid storage chamber when the first rotary shaft and the second rotary shaft rotate. A rotary shaft seal mechanism for a rotary machine, wherein a drain chamber having a liquid level higher than a low-pressure side liquid level of the retained seal liquid is provided adjacent to the U-shaped fluid storage chamber.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2001346490A JP2003148632A (en) | 2001-11-12 | 2001-11-12 | Rotating shaft seal mechanism for rotary machine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2001346490A JP2003148632A (en) | 2001-11-12 | 2001-11-12 | Rotating shaft seal mechanism for rotary machine |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JP2003148632A true JP2003148632A (en) | 2003-05-21 |
Family
ID=19159661
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2001346490A Pending JP2003148632A (en) | 2001-11-12 | 2001-11-12 | Rotating shaft seal mechanism for rotary machine |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2003148632A (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US7159873B2 (en) | 2002-09-10 | 2007-01-09 | United Technologies Corporation | Shaft seal |
| WO2008065359A2 (en) * | 2006-11-28 | 2008-06-05 | Cummins Turbo Technologies Limited | Hydraulic seal for a turbocharger |
| JP2010107038A (en) * | 2008-10-14 | 2010-05-13 | Rolls Royce Plc | Seal |
| US9157532B2 (en) | 2012-12-06 | 2015-10-13 | Rolls-Royce Plc | Hydraulic seal arrangement |
-
2001
- 2001-11-12 JP JP2001346490A patent/JP2003148632A/en active Pending
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US7159873B2 (en) | 2002-09-10 | 2007-01-09 | United Technologies Corporation | Shaft seal |
| WO2008065359A2 (en) * | 2006-11-28 | 2008-06-05 | Cummins Turbo Technologies Limited | Hydraulic seal for a turbocharger |
| WO2008065359A3 (en) * | 2006-11-28 | 2008-07-31 | Cummins Turbo Tech Ltd | Hydraulic seal for a turbocharger |
| GB2456483A (en) * | 2006-11-28 | 2009-07-22 | Cummins Turbo Technologies | Hydraulic seal for a turbocharger |
| GB2456483B (en) * | 2006-11-28 | 2011-03-16 | Cummins Turbo Technologies | Hydraulic seal for a turbocharger |
| US8075251B2 (en) | 2006-11-28 | 2011-12-13 | Cummins Turbo Technologies Limited | Hydraulic seal for a turbocharger |
| CN101595277B (en) * | 2006-11-28 | 2013-07-24 | 康明斯涡轮增压技术有限公司 | Hydraulic seal for a turbocharger |
| JP2010107038A (en) * | 2008-10-14 | 2010-05-13 | Rolls Royce Plc | Seal |
| US9157532B2 (en) | 2012-12-06 | 2015-10-13 | Rolls-Royce Plc | Hydraulic seal arrangement |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US8057163B2 (en) | Gas turbine engine cooling system and method | |
| US6988367B2 (en) | Gas turbine engine cooling system and method | |
| JP4929217B2 (en) | Gas turbine, gas turbine intermediate shaft, and gas turbine compressor cooling method | |
| FR2648866A1 (en) | DEVICE FOR CONTROLLING A LEAK AIR FLOW IN A TURBOMOTEUR | |
| JP2005054781A (en) | Low pressure turbine for turbo machine | |
| EP1552111A1 (en) | Gas turbine ventilation circuitry | |
| JPS58135305A (en) | Housing of turbo machine rotor | |
| JP2010138916A (en) | Steam turbine | |
| JP2016196885A (en) | Heat pipe temperature management system for wheels and buckets in turbomachine | |
| JP2011117717A (en) | Rotary valve assembly for high temperature and high pressure operation | |
| JP2003148632A (en) | Rotating shaft seal mechanism for rotary machine | |
| EP2837856B1 (en) | Fluid seal arrangement and method for constricting a leakage flow through a leakage gap | |
| US6951444B2 (en) | Turbine and a turbine vane for a turbine | |
| US7037067B2 (en) | Gas turbine engine | |
| JPH06101597B2 (en) | Gas transport laser device with axial gas flow | |
| FR3054858A1 (en) | TURBOMACHINE COMPRISING A DEVICE FOR DRIVING EQUIPMENT ARRANGED IN THE EXHAUST CONE | |
| US20130156602A1 (en) | Film cooled turbine component | |
| EP3054091B1 (en) | Gas turbine engine having section with thermally isolated area | |
| WO1994001657A1 (en) | An inert gas turbine engine | |
| CN114508525A (en) | Cooling device for hydraulic equipment | |
| JPH0586901A (en) | Gas turbine | |
| WO2020018056A2 (en) | Cooling of gas turbine engines with water recirculation | |
| JPS5838617B2 (en) | gas turbine home | |
| CN219242010U (en) | Engineering machine tool machine oil cooling system fast | |
| JP2004060544A (en) | Clearance reduction method for gas turbine compressor, and gas turbine plant |