JPH10196801A - Shaft seal - Google Patents
Shaft sealInfo
- Publication number
- JPH10196801A JPH10196801A JP9003831A JP383197A JPH10196801A JP H10196801 A JPH10196801 A JP H10196801A JP 9003831 A JP9003831 A JP 9003831A JP 383197 A JP383197 A JP 383197A JP H10196801 A JPH10196801 A JP H10196801A
- Authority
- JP
- Japan
- Prior art keywords
- rotating shaft
- seal
- shaft
- wire
- rotary shaft
- 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.)
- Granted
Links
Landscapes
- Sealing With Elastic Sealing Lips (AREA)
- 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、蒸気タービン、ガ
スタービンなど大型流体機械の回転軸などに適用される
軸シールに関する。The present invention relates to a shaft seal applied to a rotating shaft of a large fluid machine such as a steam turbine and a gas turbine.
【０００２】[0002]
【従来の技術】蒸気タービン、ガスタービンなど大型流
体機械の回転軸のシール材として従来から非接触型のラ
ビリンスシールが幅広く使用されている。しかしなが
ら、ラビリンスシールは回転過渡期の軸振動、或いは過
渡的な熱変形時にもフィン先端の隙間が接触しないよう
にフィン先端の隙間を或る程度大きくしなければならな
いために漏れ量が大きい。このようなラビリンスシール
に代え、漏れ量の低減を狙って開発されたシール材とし
てブラシシールがある。2. Description of the Related Art Non-contact type labyrinth seals have been widely used as seal materials for rotating shafts of large fluid machines such as steam turbines and gas turbines. However, the amount of leakage of the labyrinth seal is large because the gap at the fin tip must be increased to some extent so that the gap at the fin tip does not come into contact even during shaft vibration during transient rotation or transient thermal deformation. Instead of such a labyrinth seal, there is a brush seal as a seal material developed to reduce the amount of leakage.
【０００３】図２は蒸気タービン、ガスタービンなど大
型流体機械の回転軸などに使用されている従来のブラシ
シールの説明図である。図において、ブラシシールはワ
イヤ６と高圧側側板４と低圧側側板３などとで構成さ
れ、ワイヤ６外周端側はケーシング２にろう付け５され
ている。ワイヤ６は回転軸１の振動、或いは熱変形によ
る偏心などを吸収することができるように適度の剛性を
持つ線径約５０〜１００μｍのフィラメントで構成さ
れ、ワイヤ６間は略隙間がないように幅３〜５mmの密集
した束になっている。ワイヤ６は回転軸１外周と鋭角を
なすように回転方向に対して傾斜して取付けられてい
る。ワイヤ６の先端は回転軸１の外周に所定の予圧を有
して接触しており、接触することにより軸方向の漏れ量
を低減する構造になっている。ワイヤ６は回転軸１に接
触して摺動し、雰囲気条件、或いは周速によってはこの
摺動により発熱してワイヤ６が赤熱状態になるため、使
用する条件によってワイヤ６にインコネル、ハステロイ
などの耐高熱材が用いられている。また、ワイヤ６とと
もに回転軸１外周の摺動面も摩耗するため、通常は回転
軸１の摺動面に耐摩耗材がコーティングされている。FIG. 2 is an explanatory view of a conventional brush seal used for a rotating shaft of a large fluid machine such as a steam turbine and a gas turbine. In the figure, the brush seal includes a wire 6, a high-pressure side plate 4, a low-pressure side plate 3, and the like, and the outer peripheral end of the wire 6 is brazed 5 to the casing 2. The wire 6 is made of a filament having a wire diameter of about 50 to 100 μm having an appropriate rigidity so as to absorb vibration of the rotating shaft 1 or eccentricity due to thermal deformation. It is a dense bundle 3-5 mm wide. The wire 6 is attached at an angle to the rotation direction so as to form an acute angle with the outer periphery of the rotating shaft 1. The distal end of the wire 6 is in contact with the outer periphery of the rotating shaft 1 with a predetermined preload, and the contact is configured to reduce the amount of leakage in the axial direction. The wire 6 slides in contact with the rotating shaft 1 and generates heat due to the sliding depending on the atmospheric conditions or the peripheral speed, and the wire 6 becomes a red heat state. Therefore, depending on the use conditions, the wire 6 may be made of Inconel, Hastelloy, or the like. High heat resistant material is used. In addition, since the sliding surface on the outer periphery of the rotating shaft 1 is worn together with the wire 6, the sliding surface of the rotating shaft 1 is usually coated with a wear-resistant material.
【０００４】ブラシシールにおける漏れは、ワイヤ６間
からの漏れとワイヤ６先端からの漏れと回転軸１外周と
接触する摺動面からの漏れとである。また、ワイヤ６の
回転軸１軸方向の剛性が小さいため、低圧側側板３の内
径を回転軸１の外周と略等しくしてワイヤ６の破損を防
止している。[0004] Leakage in the brush seal includes leakage from between the wires 6, leakage from the tip of the wire 6, and leakage from a sliding surface that comes into contact with the outer periphery of the rotating shaft 1. Further, since the rigidity of the wire 6 in the axial direction of the rotating shaft 1 is small, the inner diameter of the low-pressure side plate 3 is substantially equal to the outer periphery of the rotating shaft 1 to prevent the wire 6 from being damaged.
【０００５】[0005]
【発明が解決しようとする課題】上記のような従来のブ
ラシシールにおいては、ブラシシールを構成するワイヤ
６の剛性が回転軸１の軸振れに対する追随性および回転
軸１との適正な予圧などから決められており、ワイヤ６
の線径を太くするなどして剛性を上げる場合は限界があ
る。従って、ワイヤ６の剛性に支配される回転軸１軸方
向のシール差圧は５kgf/cm2 程度が限界で、大きな差圧
をシールすることができない。In such a conventional brush seal as described above, the rigidity of the wire 6 constituting the brush seal depends on the followability of the rotating shaft 1 against shaft run-out and an appropriate preload with the rotating shaft 1. Determined, wire 6
There is a limit in increasing the rigidity by increasing the diameter of the wire. Therefore, the seal differential pressure in the direction of one axis of the rotating shaft, which is governed by the rigidity of the wire 6, is limited to about 5 kgf / cm 2 , and a large differential pressure cannot be sealed.
【０００６】また、シール差圧がワイヤ６の線径および
低圧側側板３の配置などから決まるシール許容値を越え
るとワイヤ６全体が低圧側に変形を生じて倒れ、ワイヤ
６と回転軸１との間が吹き抜けの状態になってシール機
能を失う。When the seal differential pressure exceeds a seal allowable value determined by the wire diameter of the wire 6 and the arrangement of the low-pressure side plate 3, the entire wire 6 is deformed on the low-pressure side and falls down, and the wire 6 and the rotary shaft 1 The space between the two is blown off, and the sealing function is lost.
【０００７】また、ワイヤ６の線径は通常約５０〜１０
０μｍと非常に細く、回転軸１の周面と接触して摺動す
ることによりワイヤ６が破断して脱落する危険性があ
り、蒸気タービン、ガスタービンなどにおける長時間の
使用には問題がある。The wire diameter of the wire 6 is usually about 50 to 10
It is very thin, 0 μm, and there is a danger that the wire 6 will break and fall off when it comes into contact with and slides on the peripheral surface of the rotating shaft 1, and there is a problem in long-term use in a steam turbine, a gas turbine, or the like. .
【０００８】また、ワイヤ６と回転軸１の周面とが接触
して摺動するために通常は回転軸１の表面に耐摩耗材の
コーティングが必要であるが、蒸気タービン、ガスター
ビンなどの大径の回転軸１の周面に対して長時間の使用
に耐える耐摩耗材のコーティング技術が確立されておら
ず、ワイヤ６および回転軸１の摩耗が大きいため、ブラ
シシールの寿命が短く、頻繁に交換を要する。Further, since the wire 6 and the peripheral surface of the rotary shaft 1 come into contact with each other and slide, the surface of the rotary shaft 1 usually needs to be coated with a wear-resistant material. A coating technique of a wear-resistant material that can withstand long-time use has not been established for the peripheral surface of the rotating shaft 1 having a diameter, and the wear of the wire 6 and the rotating shaft 1 is large. Requires replacement.
【０００９】また、ワイヤ６先端からの漏れ量はワイヤ
６が回転軸１の周面に接触して摺動するためにラビリン
スシールなどと比べて飛躍的に小さいが、ワイヤ６間か
らの漏れ量を安定して小さく保持することが難しい。The amount of leakage from the distal end of the wire 6 is significantly smaller than that of a labyrinth seal or the like because the wire 6 comes into contact with the peripheral surface of the rotating shaft 1 and slides. It is difficult to keep small and stable.
【００１０】[0010]
【課題を解決するための手段】本発明に係る軸シールは
上記課題の解決を目的にしており、回転軸の軸方向に幅
を有して先端が上記回転軸の周面に摺動し互いに隙間を
空けて外周側基端がケーシング側に固定された複数の可
撓性を有する薄板を上記回転軸の周方向に上記回転軸の
外周をシール可能に多重に備えている。SUMMARY OF THE INVENTION An object of the present invention is to provide a shaft seal having a width in the axial direction of a rotating shaft, a tip of which is slid on a peripheral surface of the rotating shaft, and a shaft seal is provided. A plurality of flexible thin plates having an outer peripheral base fixed to the casing side with a gap provided in a multiplex manner so as to seal the outer periphery of the rotating shaft in a circumferential direction of the rotating shaft.
【００１１】また、本発明に係る軸シールは、回転軸の
軸方向に幅を有して先端が上記回転軸の周面に摺動し互
いに隙間を空けて外周側基端がケーシング側に固定され
た複数の可撓性を有する薄板を上記回転軸の周方向に上
記回転軸の外周をシール可能に多重に備え、上記薄板と
上記回転軸の周面とが鋭角をなすとともに上記薄板間の
隙間が外周側と内周側とで互いに等しくなっている。Further, the shaft seal according to the present invention has a width in the axial direction of the rotating shaft, the leading end thereof slides on the peripheral surface of the rotating shaft, the outer peripheral base end is fixed to the casing side with a gap therebetween. A plurality of flexible thin plates are provided in a multiplex manner so as to seal the outer periphery of the rotating shaft in the circumferential direction of the rotating shaft, and the thin plate and the circumferential surface of the rotating shaft form an acute angle and are disposed between the thin plates. The gap is equal on the outer peripheral side and the inner peripheral side.
【００１２】このように、本軸シールにおいてはシール
部材として回転軸の軸方向に幅を有する薄板を周方向に
多層状に配置しており、シール部材が回転軸の軸方向に
幅を有することにより回転軸の周方向には柔らかく、軸
方向には剛性の高いシール構造になっている。そして、
シール部材を薄板形状にすることにより薄板の外周側基
端をケーシング側に幅方向にろう付けしてブラシシール
のワイヤなどと比べて強固に固定することができる。ま
た、薄板の先端は回転軸の軸方向に幅を有し、周方向に
は柔らかいことにより共振点の通過時など回転軸の振動
が大きいときには薄板が変形して回転軸との接触を緩和
することが可能で、また定格条件では回転軸の回転によ
る動圧効果で薄板の先端が僅かに浮上することにより回
転軸との接触がなくメタル同士の接触が回避される。ま
た、シール部材が薄板状で回転軸の軸方向に幅を有する
ことによりシールによる差圧方向の剛性をブラシシール
などと比べて大幅に大きくすることができる。As described above, in the present shaft seal, a thin plate having a width in the axial direction of the rotary shaft is arranged in a multilayer shape in the circumferential direction as a seal member, and the seal member has a width in the axial direction of the rotary shaft. Thus, a seal structure that is soft in the circumferential direction of the rotating shaft and highly rigid in the axial direction is obtained. And
By forming the seal member into a thin plate shape, the base end on the outer peripheral side of the thin plate can be brazed to the casing side in the width direction and can be fixed more firmly than a brush seal wire or the like. In addition, the tip of the thin plate has a width in the axial direction of the rotating shaft, and is soft in the circumferential direction, so that when the vibration of the rotating shaft is large, such as when passing a resonance point, the thin plate is deformed to reduce contact with the rotating shaft. Under the rated condition, the tip of the thin plate slightly floats due to the dynamic pressure effect of the rotation of the rotating shaft, so that there is no contact with the rotating shaft and metal-to-metal contact is avoided. Further, since the seal member is thin and has a width in the axial direction of the rotating shaft, the rigidity of the seal in the differential pressure direction can be greatly increased as compared with a brush seal or the like.
【００１３】[0013]
【発明の実施の形態】図１は本発明の実施の一形態に係
るリーフシールの説明図である。図において、本実施の
形態に係るリーフシールは蒸気タービン、ガスタービン
など大型流体機械の回転軸などに使用されるもので、図
における符号１は回転軸、２はケーシング、３は低圧側
側板、４は高圧側側板、５はろう付け、８は薄板（リー
フ）、９は各薄板８間の隙間である。本リーフシールは
同図（ａ）に示すように、回転軸１の軸方向に所定の幅
を有する薄板（リーフ）８を回転軸１の周方向に多層に
配置した構造になっている。薄板８は薄板８の外周側基
端のみを本リーフシールのケーシング２にろう付け５さ
れて回転軸１の外周をシールすることにより高圧側領域
と低圧側領域とに分けており、薄板８の両側には高圧側
領域に高圧側側板４が、低圧側領域に高圧側側板３がそ
れぞれ圧力作用方向のガイド板として装着されている。
薄板８は互いの間に僅かに隙間９があり、薄板８は板厚
で決まる所定の剛性を回転軸１の周方向に持つように設
計されている。また、薄板８は回転軸１の回転方向に対
して回転軸１の周面となす角が鋭角となるように取付け
られており、回転軸１の停止時には薄板８の先端は所定
の予圧で回転軸１に接触しているが、回転軸１が回転す
ることによる動圧効果で薄板８の先端が浮上して回転軸
１と非接触状態になり、薄板８の先端および回転軸１表
面が摩耗しない。FIG. 1 is an explanatory view of a leaf seal according to an embodiment of the present invention. In the drawing, the leaf seal according to the present embodiment is used for a rotating shaft of a large fluid machine such as a steam turbine or a gas turbine. In the drawing, reference numeral 1 denotes a rotating shaft, 2 denotes a casing, 3 denotes a low-pressure side plate, 4 is a high-pressure side plate, 5 is brazing, 8 is a thin plate (leaf), and 9 is a gap between the thin plates 8. As shown in FIG. 1A, the present leaf seal has a structure in which thin plates (leaves) 8 having a predetermined width in the axial direction of the rotating shaft 1 are arranged in multiple layers in the circumferential direction of the rotating shaft 1. The thin plate 8 is divided into a high-pressure side region and a low-pressure side region by brazing 5 only the outer peripheral side base end of the thin plate 8 to the casing 2 of the leaf seal and sealing the outer periphery of the rotating shaft 1. On both sides, a high-pressure side plate 4 is mounted on the high-pressure side region, and a high-pressure side plate 3 is mounted on the low-pressure side region as a guide plate in the direction of pressure action.
The thin plates 8 have a slight gap 9 therebetween, and the thin plates 8 are designed to have a predetermined rigidity determined by the thickness in the circumferential direction of the rotating shaft 1. The thin plate 8 is attached so that an angle between the thin plate 8 and the circumferential surface of the rotary shaft 1 is acute with respect to the rotation direction of the rotary shaft 1. When the rotary shaft 1 stops, the tip of the thin plate 8 rotates with a predetermined preload. Although it is in contact with the shaft 1, the tip of the thin plate 8 floats due to the dynamic pressure effect caused by the rotation of the rotating shaft 1 and is brought into a non-contact state with the rotating shaft 1, and the tip of the thin plate 8 and the surface of the rotating shaft 1 are worn. do not do.
【００１４】同図（ｂ）に示すように、各薄板８は外周
側基端と内周側先端とで各薄板８間の隙間９が一定にな
るように設定されており、半径座標ｒにおいて薄板８の
接線と各薄板８による円の中心を通る線とがなす角度θ
が次式を満たすように変化している。As shown in FIG. 1B, each thin plate 8 is set so that a gap 9 between the thin plates 8 is constant between a base end on an outer peripheral side and a distal end on an inner peripheral side. The angle θ between the tangent line of the thin plate 8 and the line passing through the center of the circle formed by each thin plate 8
Is changed to satisfy the following equation.
【００１５】sinθi ＝ｔ／Ｔ＝ｔ／（ｒi ψ） ∴ｔ／ψ＝ｒi sin θi ＝ｒ sinθ ∴ sinθ＝ｒi sin θi ／ｒ 但し、ｔは薄板８の厚み＋各薄板８間の隙間９、ψは薄
板８間の中心角、Ｔは薄板８内周の幅（＝ｒi ψ）、θ
i は薄板８先端の角度、θO は薄板８基端の角度であ
る。薄板８をこのように設計することにより、薄板８間
の隙間９は内外径で一定になって薄板８間からの漏れを
所定の量以内に抑えることができる。[0015] sinθ i = t / T = t / (r i ψ) ∴t / ψ = r i sin θ i = r sinθ ∴ sinθ = r i sin θ i / r However, t is a thin plate 8 thickness + each The gap 9 between the thin plates 8, ８ is the central angle between the thin plates 8, T is the width of the inner circumference of the thin plate 8 (= ri i ), θ
i is the angle of the leading end of the thin plate 8, and θ O is the angle of the base end of the thin plate 8. By designing the thin plates 8 in this way, the gap 9 between the thin plates 8 is constant at the inner and outer diameters, and leakage from between the thin plates 8 can be suppressed within a predetermined amount.
【００１６】従来のブラシシールにおいては、ブラシシ
ールを構成するワイヤの剛性が回転軸の軸振れに対する
追随性および回転軸との適正な予圧などから決められて
おり、ワイヤの線径を太くするなどして剛性を上げる場
合は限界がある。従って、ワイヤの剛性に支配される回
転軸軸方向のシール差圧は５kgf/cm2 程度が限界で、大
きな差圧をシールすることができない。また、シール差
圧がワイヤの線径および低圧側側板の配置などから決ま
るシール許容値を越えるとワイヤ全体が低圧側に変形を
生じて倒れ、ワイヤと回転軸との間が吹き抜けの状態に
なってシール機能を失う。また、ワイヤの線径は通常約
５０〜１００μｍと非常に細く、回転軸の周面と接触し
て摺動することによりワイヤが破断して脱落する危険性
があり、蒸気タービン、ガスタービンなどにおける長時
間の使用には問題がある。また、ワイヤと回転軸の周面
とが接触して摺動するために通常は回転軸の表面に耐摩
耗材のコーティングが必要であるが、蒸気タービン、ガ
スタービンなどの大径の回転軸の周面に対して長時間の
使用に耐える耐摩耗材のコーティング技術が確立されて
おらず、ワイヤおよび回転軸の摩耗が大きいため、ブラ
シシールの寿命が短く、頻繁に交換を要する。また、ワ
イヤ先端からの漏れ量はワイヤが回転軸の周面に接触し
て摺動するためにラビリンスシールなどと比べて飛躍的
に小さいが、ワイヤ間からの漏れ量を安定して小さく保
持することが難しい。これに対し、本リーフシールにお
いては回転軸１の軸方向に幅を有する薄板（リーフ）８
を回転軸１周方向に多層状に配置し、薄板８相互の拘束
がないように薄板８間に僅かな隙間９を設け、薄板８と
回転軸１外周とのなす確度が鋭角となるように回転軸１
回転方向に対し傾斜して配置し、各薄板８間の外周側の
隙間９と内周側の隙間９とが等間隔になるように薄板８
の曲率が半径方向の位置に応じて変化するようにしてお
り、シール部材として回転軸１の軸方向に幅を有する薄
板８を回転軸１の周方向に多層に配置することにより、
シール部材が回転軸１の周方向には柔らかく回転軸１の
軸方向には剛性の高いシール構造にしている。また、シ
ール部材を薄板形状にすることにより、本リーフシール
のケーシング２に固定される外周側のろう付け５を強固
なものにすることができる。また、薄板８の先端を回転
軸１の軸方向に剛性を有し、回転軸１の周方向には柔ら
かくすることにより、薄板８の先端が回転軸１の回転に
よる動圧効果で僅かに浮上するようにしている。このよ
うに、シール部材が薄板形状であることにより、ブラシ
シールなどに比べてシール部材のシールによる差圧方向
の剛性をはるかに大きくすることができ、大きな差圧ま
でシールすることが可能である。また、薄板８の外周側
基端を幅方向に強固にろう付け５することができること
により、ブラシシールにおけるワイヤの場合のようなシ
ール部材の脱落を防止することができる。また、共振点
通過時など回転軸１の振動が大きいときには薄板８が変
形することにより回転軸１との接触を緩和することが可
能で、また定格条件では回転軸１の回転による動圧効果
により薄板８の先端が浮上することにより薄板８と回転
軸１との接触が回避され、メタル同士の接触による過大
な発熱および摩耗が防止される。また、シール部材が薄
板形状でシールによる差圧方向の剛性が大きいことによ
り、シール差圧を大きくすることができる。また、薄板
８の先端と回転軸１との隙間を従来の非接触型のラビリ
ンスシールなどと比べて飛躍的に小さくすることができ
ることにより、ブラシシールと同等なラビリンスシール
の１／１０レベルの大幅な漏れ量の低減が可能である。
また、シール部材先端の接触による発熱が防止されるこ
とにより、回転軸１におけるサーマルバランスによる振
動の発生が避けられる。In the conventional brush seal, the stiffness of the wire constituting the brush seal is determined based on the followability of the rotating shaft to the axial runout and an appropriate preload with the rotating shaft. There is a limit in increasing the rigidity. Therefore, the seal differential pressure in the direction of the rotation axis, which is governed by the rigidity of the wire, is limited to about 5 kgf / cm 2 , and a large differential pressure cannot be sealed. Also, if the seal differential pressure exceeds the seal allowable value determined by the wire diameter of the wire and the arrangement of the low-pressure side plate, the entire wire will be deformed on the low-pressure side and fall, resulting in a blow-through between the wire and the rotating shaft. Loses the sealing function. Further, the wire diameter of the wire is usually very thin, about 50 to 100 μm, and there is a risk that the wire may break and fall off by sliding in contact with the peripheral surface of the rotating shaft. There is a problem with prolonged use. In addition, the surface of the rotating shaft usually needs to be coated with a wear-resistant material because the wire and the peripheral surface of the rotating shaft come into contact with each other and slide, but the circumference of a large-diameter rotating shaft such as a steam turbine or a gas turbine is required. The coating technology of the wear-resistant material that can withstand long-time use on the surface has not been established, and the wear of the wire and the rotating shaft is large. Therefore, the life of the brush seal is short, and frequent replacement is required. In addition, the amount of leakage from the tip of the wire is drastically smaller than that of a labyrinth seal because the wire slides in contact with the peripheral surface of the rotating shaft, but the amount of leakage between the wires is stably kept small. It is difficult. On the other hand, in the present leaf seal, a thin plate (leaf) 8 having a width in the axial direction of the rotating shaft 1 is provided.
Are arranged in a multilayer shape in the circumferential direction of the rotating shaft 1, a slight gap 9 is provided between the thin plates 8 so that there is no restriction between the thin plates 8, and the accuracy between the thin plate 8 and the outer periphery of the rotating shaft 1 is an acute angle. Rotary axis 1
The thin plates 8 are arranged so as to be inclined with respect to the rotation direction so that the gap 9 on the outer peripheral side and the gap 9 on the inner peripheral side between the thin plates 8 are at equal intervals.
Is changed according to the position in the radial direction, and by arranging thin plates 8 having a width in the axial direction of the rotating shaft 1 as a seal member in a multilayer manner in the circumferential direction of the rotating shaft 1,
The sealing member has a sealing structure that is soft in the circumferential direction of the rotating shaft 1 and has high rigidity in the axial direction of the rotating shaft 1. Further, by forming the seal member into a thin plate shape, the brazing 5 on the outer peripheral side fixed to the casing 2 of the present leaf seal can be made strong. In addition, the distal end of the thin plate 8 has rigidity in the axial direction of the rotary shaft 1 and is softened in the circumferential direction of the rotary shaft 1 so that the distal end of the thin plate 8 slightly floats due to the dynamic pressure effect due to the rotation of the rotary shaft 1. I am trying to do it. As described above, since the seal member has a thin plate shape, the rigidity of the seal member in the differential pressure direction due to the seal of the seal member can be made much larger than that of a brush seal or the like, and it is possible to seal up to a large differential pressure. . Further, since the base end on the outer peripheral side of the thin plate 8 can be firmly brazed 5 in the width direction, it is possible to prevent the sealing member from falling off as in the case of the wire in the brush seal. Further, when the vibration of the rotating shaft 1 is large, such as when passing through a resonance point, the thin plate 8 is deformed, so that the contact with the rotating shaft 1 can be relaxed. By floating the tip of the thin plate 8, contact between the thin plate 8 and the rotating shaft 1 is avoided, and excessive heat generation and abrasion due to contact between metals is prevented. In addition, since the seal member has a thin plate shape and has high rigidity in the differential pressure direction due to the seal, the seal differential pressure can be increased. In addition, the clearance between the tip of the thin plate 8 and the rotating shaft 1 can be significantly reduced as compared with a conventional non-contact labyrinth seal or the like. It is possible to greatly reduce the amount of leakage.
In addition, since heat generation due to contact of the tip of the seal member is prevented, generation of vibration due to thermal balance in the rotating shaft 1 can be avoided.
【００１７】[0017]
【発明の効果】本発明に係る軸シールは前記のように構
成されており、シール部材を薄板形状にすることにより
薄板の外周側基端をケーシング側に幅方向にろう付けし
てブラシシールのワイヤなどと比べて強固に固定するこ
とができるので、シール部材の脱落が防止される。ま
た、薄板の先端は回転軸の軸方向に幅を有し、周方向に
は柔らかいことにより共振点の通過時など回転軸の振動
が大きいときには薄板が変形して回転軸との接触を緩和
することが可能で、また定格条件では回転軸の回転によ
る動圧効果で薄板の先端が僅かに浮上することにより回
転軸との接触がなくメタル同士の接触が回避されるの
で、シール部材と回転軸との接触による過大な発熱、シ
ール部材および回転軸の摩耗などが大幅に低減されると
ともに、回転軸におけるサーマルアンバランスによる振
動の発生が防止される。また、シール部材が薄板状で回
転軸の軸方向に幅を有することによりシールによる差圧
方向の剛性をブラシシールなどと比べて大幅に大きくす
ることができるので、飛躍的に大きな差圧までシールす
ることが可能である。The shaft seal according to the present invention is configured as described above. By forming the sealing member into a thin plate shape, the outer peripheral base end of the thin plate is brazed in the width direction to the casing side to form a brush seal. Since it can be fixed more firmly than a wire or the like, the sealing member is prevented from falling off. In addition, the tip of the thin plate has a width in the axial direction of the rotating shaft, and is soft in the circumferential direction, so that when the vibration of the rotating shaft is large, such as when passing a resonance point, the thin plate is deformed to reduce contact with the rotating shaft. Under the rated conditions, the tip of the thin plate slightly floats due to the dynamic pressure effect of the rotation of the rotating shaft, so that there is no contact with the rotating shaft and metal-to-metal contact is avoided. Excessive heat generation due to contact with the shaft, abrasion of the seal member and the rotating shaft, etc. are greatly reduced, and the occurrence of vibration due to thermal imbalance in the rotating shaft is prevented. In addition, since the sealing member has a thin plate shape and has a width in the axial direction of the rotating shaft, the rigidity in the differential pressure direction due to the seal can be greatly increased as compared with a brush seal, etc. It is possible to
【図１】図１（ａ）は本発明の実施の一形態に係るリー
フシールの斜視図、同図（ｂ）はその薄板の断面図であ
る。FIG. 1A is a perspective view of a leaf seal according to an embodiment of the present invention, and FIG. 1B is a sectional view of a thin plate thereof.
【図２】図２（ａ）は従来のブラシシールの断面図、同
図（ｂ）は同図（ａ）におけるＢ−Ｂ矢視断面図であ
る。FIG. 2A is a cross-sectional view of a conventional brush seal, and FIG. 2B is a cross-sectional view taken along a line BB in FIG. 2A.
１ 回転軸 ２ ケーシング ３ 低圧側側板 ４ 高圧側側板 ５ ろう付け ８ 薄板（リーフ） ９ 薄板間の隙間 DESCRIPTION OF SYMBOLS 1 Rotation shaft 2 Casing 3 Low pressure side plate 4 High pressure side plate 5 Brazing 8 Thin plate (leaf) 9 Gap between thin plates
Claims (2)
回転軸の周面に摺動し互いに隙間を空けて外周側基端が
ケーシング側に固定された複数の可撓性を有する薄板を
上記回転軸の周方向に上記回転軸の外周をシール可能に
多重に備えたことを特徴とする軸シール。1. A plurality of flexible members each having a width in the axial direction of a rotating shaft, a distal end thereof sliding on a peripheral surface of the rotating shaft, a gap between each other, and a base end on an outer peripheral side being fixed to a casing side. A shaft seal comprising a plurality of thin plates provided so as to seal the outer periphery of the rotation shaft in a circumferential direction of the rotation shaft.
なすとともに上記薄板間の隙間が外周側と内周側とで互
いに等しいことを特徴とする請求項１に記載の軸シー
ル。2. The shaft seal according to claim 1, wherein the thin plate and the peripheral surface of the rotary shaft form an acute angle, and a gap between the thin plates is equal to each other on an outer peripheral side and an inner peripheral side.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP00383197A JP3382802B2 (en) | 1997-01-13 | 1997-01-13 | Shaft seal |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP00383197A JP3382802B2 (en) | 1997-01-13 | 1997-01-13 | Shaft seal |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH10196801A true JPH10196801A (en) | 1998-07-31 |
| JP3382802B2 JP3382802B2 (en) | 2003-03-04 |
Family
ID=11568154
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP00383197A Expired - Lifetime JP3382802B2 (en) | 1997-01-13 | 1997-01-13 | Shaft seal |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3382802B2 (en) |
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2000170922A (en) * | 1998-12-03 | 2000-06-23 | Mtu Motoren & Turbinen Union Muenchen Gmbh | Brush seal having bent rigid brush |
| US6343792B1 (en) | 1998-07-13 | 2002-02-05 | Mitsubishi Heavy Industries, Ltd. | Shaft seal and turbine using the same |
| US6860484B2 (en) | 2000-02-12 | 2005-03-01 | Alstom (Switzerland) Ltd. | Rotor seal with folding strip |
| US7066468B2 (en) | 2001-02-08 | 2006-06-27 | Mitsubishi Heavy Industries, Ltd. | Shaft seal and gas turbine |
| US7364165B2 (en) * | 2003-05-21 | 2008-04-29 | Mitsubishi Heavy Industries, Ltd. | Shaft seal mechanism |
| JP2011002031A (en) * | 2009-06-18 | 2011-01-06 | Toshiba Corp | Steam valve device, and power generating facility equipped with the same |
| JP2014219079A (en) * | 2013-05-10 | 2014-11-20 | 株式会社デンソー | Pressure control device |
| CN105723132A (en) * | 2013-10-18 | 2016-06-29 | 三菱重工业株式会社 | Shaft sealing device and rotating machine provided therewith |
| US9677410B2 (en) | 2010-12-27 | 2017-06-13 | Mitsubishi Heavy Industries, Ltd. | Shaft sealing device, and rotary machine equipped therewith |
| US9879786B2 (en) | 2012-08-23 | 2018-01-30 | Mitsubishi Hitachi Power Systems, Ltd. | Rotary machine |
-
1997
- 1997-01-13 JP JP00383197A patent/JP3382802B2/en not_active Expired - Lifetime
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6343792B1 (en) | 1998-07-13 | 2002-02-05 | Mitsubishi Heavy Industries, Ltd. | Shaft seal and turbine using the same |
| JP2000170922A (en) * | 1998-12-03 | 2000-06-23 | Mtu Motoren & Turbinen Union Muenchen Gmbh | Brush seal having bent rigid brush |
| US6860484B2 (en) | 2000-02-12 | 2005-03-01 | Alstom (Switzerland) Ltd. | Rotor seal with folding strip |
| US7066468B2 (en) | 2001-02-08 | 2006-06-27 | Mitsubishi Heavy Industries, Ltd. | Shaft seal and gas turbine |
| US7364165B2 (en) * | 2003-05-21 | 2008-04-29 | Mitsubishi Heavy Industries, Ltd. | Shaft seal mechanism |
| JP2011002031A (en) * | 2009-06-18 | 2011-01-06 | Toshiba Corp | Steam valve device, and power generating facility equipped with the same |
| US9677410B2 (en) | 2010-12-27 | 2017-06-13 | Mitsubishi Heavy Industries, Ltd. | Shaft sealing device, and rotary machine equipped therewith |
| US9879786B2 (en) | 2012-08-23 | 2018-01-30 | Mitsubishi Hitachi Power Systems, Ltd. | Rotary machine |
| JP2014219079A (en) * | 2013-05-10 | 2014-11-20 | 株式会社デンソー | Pressure control device |
| CN105723132A (en) * | 2013-10-18 | 2016-06-29 | 三菱重工业株式会社 | Shaft sealing device and rotating machine provided therewith |
Also Published As
| Publication number | Publication date |
|---|---|
| JP3382802B2 (en) | 2003-03-04 |
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