JP6909681B2

JP6909681B2 - A steam turbine sealing device and a steam turbine equipped with this sealing device

Info

Publication number: JP6909681B2
Application number: JP2017173058A
Authority: JP
Inventors: 一貴白波瀬; 近藤　誠; 近藤　　誠; 徳幸岡田; 雄久 ▲濱▼田
Original assignee: Mitsubishi Power Ltd
Current assignee: Mitsubishi Power Ltd
Priority date: 2017-09-08
Filing date: 2017-09-08
Publication date: 2021-07-28
Anticipated expiration: 2037-09-08
Also published as: JP2019049218A

Description

本開示は、蒸気タービンのシール装置及びこのシール装置を備える蒸気タービンに関する。 The present disclosure relates to a steam turbine sealing device and a steam turbine including the sealing device.

蒸気タービンには、タービンロータと、その周りに設けられた環形状のリング部材との間をシールするシール装置が設けられている。蒸気タービンの性能を向上するためには、タービンロータとリング部材との間をリークする蒸気を低減する必要があり、そのためには、定格運転時におけるタービンロータとリング部材との間のクリアランスを小さくする必要がある。定格運転時におけるタービンロータとリング部材との間のクリアランスを小さくするためには、定格運転時においてリング部材の温度上昇を抑え、リング部材とタービンロータとの温度差をできる限り小さくする必要がある。 The steam turbine is provided with a sealing device that seals between the turbine rotor and the ring-shaped ring member provided around the turbine rotor. In order to improve the performance of the steam turbine, it is necessary to reduce the steam leaking between the turbine rotor and the ring member, and for that purpose, the clearance between the turbine rotor and the ring member during rated operation is reduced. There is a need to. In order to reduce the clearance between the turbine rotor and the ring member during rated operation, it is necessary to suppress the temperature rise of the ring member during rated operation and to minimize the temperature difference between the ring member and the turbine rotor. ..

特許文献１には、タービンロータとリング部材との間のクリアランスの拡大の抑制を目的とするものではないが、蒸気タービンの蒸気入口部の車室壁の温度上昇を抑制するために熱遮蔽板を設けることが記載されている。 Patent Document 1 is not intended to suppress the expansion of the clearance between the turbine rotor and the ring member, but is a heat shield plate for suppressing the temperature rise of the passenger compartment wall at the steam inlet portion of the steam turbine. It is stated that

特開平６−１２９２０７号公報Japanese Unexamined Patent Publication No. 6-129207

本発明者らの鋭意検討の結果、蒸気タービンの蒸気入口部にリング部材が面することにより、定格運転時に蒸気入口部の蒸気の熱によってタービンロータよりもリング部材の温度が上昇し、タービンロータよりもリング部材の変形量が大きくなるので、タービンロータとリング部材との間のクリアランスが拡大する傾向にあることが明らかになった。 As a result of diligent studies by the present inventors, when the ring member faces the steam inlet portion of the steam turbine, the temperature of the ring member rises more than that of the turbine rotor due to the heat of the steam at the steam inlet portion during the rated operation, and the turbine rotor It was clarified that the clearance between the turbine rotor and the ring member tends to increase because the amount of deformation of the ring member is larger than that of the ring member.

上述の事情に鑑みて、本発明の少なくとも１つの実施形態は、蒸気タービンの性能を向上できる蒸気タービンのシール装置及びこのシール装置を備える蒸気タービンを提供することを目的とする。 In view of the above circumstances, at least one embodiment of the present invention aims to provide a steam turbine sealing device capable of improving the performance of the steam turbine and a steam turbine including the sealing device.

（１）本発明の少なくとも１つの実施形態に係る蒸気タービンのシール装置は、
タービンロータの周囲に設けられた環形状のリング部材と、
前記リング部材に保持されるとともに前記リング部材と前記タービンロータとの間に形成された環形状の間隙をシールするように構成された少なくとも１つのシール部材と
を備える、蒸気タービンのシール装置であって、
前記リング部材は、
前記蒸気タービンの蒸気入口部に面するように設けられる第１部分と、
前記タービンロータの軸方向において前記第１部分に対して前記蒸気入口部とは反対側に位置する第２部分と
に分割され、
前記少なくとも１つのシール部材のうちの少なくとも１つは前記第２部分に保持され、
前記第１部分は、
前記蒸気入口部の環状流路の一部を構成する湾曲部と、
前記湾曲部よりも前記タービンロータの径方向内側に設けられ、前記蒸気入口部の蒸気を整流する整流部と
を備え、
前記径方向において前記湾曲部と前記整流部との間で前記第１部分と前記第２部分とが固定されている。 (1) The steam turbine sealing device according to at least one embodiment of the present invention is
A ring-shaped ring member provided around the turbine rotor and
A steam turbine sealing device including at least one sealing member held by the ring member and configured to seal a ring-shaped gap formed between the ring member and the turbine rotor. hand,
The ring member
A first portion provided so as to face the steam inlet portion of the steam turbine, and
It is divided into a second portion located on the side opposite to the steam inlet portion with respect to the first portion in the axial direction of the turbine rotor.
At least one of the at least one sealing member is held by the second portion .
The first part is
A curved portion forming a part of the annular flow path of the steam inlet portion and a curved portion.
A rectifying unit provided inside the turbine rotor in the radial direction with respect to the curved portion and rectifying steam at the steam inlet portion.
With
It said curved portion and said first portion between said rectifier and said second portion that is fixed in the radial direction.

上記（１）の構成によると、リング部材が、蒸気タービンの蒸気入口部に面するように設けられる第１部分と、リング部材とタービンロータとの間に形成された環形状の間隙をシールするシール部材が設けられた第２部分とに分割されていることにより、第１部分によって第２部分への入熱が抑制されることで第２部分の温度上昇が抑制される。このため、定格運転時における第２部分及びタービンロータの温度差の拡大が抑制されて、第２部分及びタービンロータの変形量の差が低減されるので、タービンロータと第２部分との間の間隙の幅（クリアランス）の拡大が抑制される。その結果、定格運転時においてリング部材とタービンロータとの間からリークする蒸気の量を低減できるので、蒸気タービンの性能を向上することができる。また、上記（１）の構成によると、湾曲部と整流部との間で第１部分と第２部分とが固定されているので、蒸気の整流効果を妨げずに第１部分と第２部分とを固定することができる。 According to the configuration of (1) above, the ring member seals the ring-shaped gap formed between the ring member and the turbine rotor with the first portion provided so as to face the steam inlet portion of the steam turbine. Since the seal member is divided into the second portion provided, the first portion suppresses the heat input to the second portion, so that the temperature rise of the second portion is suppressed. Therefore, the expansion of the temperature difference between the second portion and the turbine rotor during the rated operation is suppressed, and the difference in the amount of deformation between the second portion and the turbine rotor is reduced, so that the difference between the turbine rotor and the second portion is reduced. The expansion of the gap width (clearance) is suppressed. As a result, the amount of steam leaking from between the ring member and the turbine rotor during rated operation can be reduced, so that the performance of the steam turbine can be improved. Further, according to the configuration of (1) above, since the first portion and the second portion are fixed between the curved portion and the rectifying portion, the first portion and the second portion do not interfere with the rectifying effect of steam. And can be fixed.

（２）いくつかの実施形態では、上記（１）の構成において、
前記第１部分と前記第２部分とは、少なくとも１つの締結部材によって固定され、
前記第１部分には、前記少なくとも１つの締結部材が挿入される少なくとも１つの貫通孔が形成され、
前記貫通孔は、前記第１部分の周方向における開口幅よりも前記第１部分の径方向における開口幅の方が長い。 (2) In some embodiments, in the configuration of (1) above,
The first portion and the second portion are fixed by at least one fastening member.
At least one through hole into which the at least one fastening member is inserted is formed in the first portion.
The through hole has a longer opening width in the radial direction of the first portion than an opening width in the circumferential direction of the first portion.

上記（２）の構成によると、第１部分は蒸気入口部の蒸気と接触して温度が上昇することにより、第１部分と第２部分とに温度差が生じるので、第１部分と第２部分とに径方向の熱伸び差が生じる。この熱伸び差により、締結部材による固定個所に応力が発生し得るが、締結部材が挿入される貫通孔が第１部分の径方向に長孔の形状となっていることによりこの熱伸び差を許容することができるので、締結部材による固定個所に応力が発生するのを抑制することができる。 According to the configuration of (2) above, the first portion comes into contact with the steam at the steam inlet portion and the temperature rises, so that a temperature difference occurs between the first portion and the second portion. There is a radial difference in thermal elongation between the portion and the portion. Due to this thermal elongation difference, stress may be generated at the fixed portion by the fastening member, but this thermal elongation difference is caused by the shape of the through hole into which the fastening member is inserted is a long hole in the radial direction of the first portion. Since it can be tolerated, it is possible to suppress the generation of stress at the fixed portion by the fastening member.

（３）いくつかの実施形態では、上記（２）の構成において、
前記貫通孔は、
前記締結部材の軸部が挿入されるように構成された第１孔部と、
前記第１孔部に対して前記蒸気入口部側に位置するとともに前記締結部材の頭部が挿入されるように構成された第２孔部と
を備え、
前記締結部材の前記頭部の端面が、前記蒸気入口部に面する前記第１部分の表面と面一又は前記表面よりも前記第２部分側に位置するように、前記締結部材が前記貫通孔に挿入されて前記第１部分と前記第２部分とを固定する。 (3) In some embodiments, in the configuration of (2) above,
The through hole is
A first hole portion configured to insert a shaft portion of the fastening member, and a first hole portion.
It is provided with a second hole portion which is located on the steam inlet portion side with respect to the first hole portion and is configured so that the head of the fastening member is inserted.
The fastening member has a through hole so that the end surface of the head of the fastening member is flush with the surface of the first portion facing the steam inlet portion or is located on the second portion side of the surface. It is inserted into and fixes the first part and the second part.

上記（３）の構成によると、蒸気入口部側の第１部分の表面から締結部材の頭部が突出しないので、蒸気入口部側の第１部分の表面に沿った蒸気の流れの乱れを抑制することができる。 According to the configuration of (3) above, since the head of the fastening member does not protrude from the surface of the first portion on the steam inlet side, the turbulence of the steam flow along the surface of the first portion on the steam inlet side is suppressed. can do.

（４）いくつかの実施形態では、上記（２）または（３）の構成において、
前記締結部材は、前記タービンロータの軸方向に前記第１部分と前記第２部分とを固定する。 (4) In some embodiments, in the configuration of (2) or (3) above,
The fastening member fixes the first portion and the second portion in the axial direction of the turbine rotor.

蒸気入口部に蒸気が流入すると、第１部分に対する蒸気入口部側と第２部分側との間で圧力差が生じ、この圧力差によって第１部分が第２部分に向かって押し付けられる力が第１部分に加えられる。上記（４）の構成によると、締結部材は、タービンロータの軸方向に第１部分と第２部分とを固定していることにより、この圧力差に起因する力が締結部材をタービンロータの軸方向に第２部分に向かって押し付けることになるので、締結部材による第１部分と第２部分との固定力を高めることができる。 When steam flows into the steam inlet portion, a pressure difference is generated between the steam inlet portion side and the second portion side with respect to the first portion, and the force that pushes the first portion toward the second portion by this pressure difference is the second. Added to one part. According to the configuration of (4) above, the fastening member fixes the first portion and the second portion in the axial direction of the turbine rotor, so that the force caused by this pressure difference causes the fastening member to be the shaft of the turbine rotor. Since it is pressed toward the second portion in the direction, the fixing force between the first portion and the second portion by the fastening member can be increased.

（５）いくつかの実施形態では、上記（１）〜（４）のいずれかの構成において、
前記第１部分は、前記第２部分に面する第１対向面を含み、
前記第２部分は、前記第１部分に面する第２対向面を含み、
前記第１部分と前記第２部分とは、前記第１対向面と前記第２対向面との間に部分的に間隔をあけるようにして固定されている。 (5) In some embodiments, in any of the configurations (1) to (4) above,
The first portion includes a first facing surface facing the second portion.
The second portion includes a second facing surface facing the first portion.
The first portion and the second portion are fixed so as to be partially spaced between the first facing surface and the second facing surface.

上記（５）の構成によると、第１部分と第２部分との間に間隔がない場合に比べて、第１部分と第２部分との接触面積が小さくなることにより、熱伝導による第１部分から第２部分への熱移動が抑制されるので、定格運転時における第２部分及びタービンロータの温度差の拡大が抑制され、タービンロータと第２部分との間のクリアランスの拡大が抑制される。その結果、定格運転時においてリング部材とタービンロータとの間からリークする蒸気の量を低減できるので、蒸気タービンの性能を向上することができる。 According to the configuration of (5) above, the contact area between the first portion and the second portion is smaller than that in the case where there is no space between the first portion and the second portion, so that the first portion due to heat conduction is used. Since the heat transfer from the portion to the second portion is suppressed, the expansion of the temperature difference between the second portion and the turbine rotor during rated operation is suppressed, and the expansion of the clearance between the turbine rotor and the second portion is suppressed. NS. As a result, the amount of steam leaking from between the ring member and the turbine rotor during rated operation can be reduced, so that the performance of the steam turbine can be improved.

（６）いくつかの実施形態では、上記（５）の構成において、
前記第１対向面及び前記第２対向面の少なくとも一方には、前記締結部材を囲むように他方に向かって突出する突出部が設けられ、該突出部以外の部分で前記第１対向面と前記第２対向面との間に部分的な間隔が形成されている。 (6) In some embodiments, in the configuration of (5) above,
At least one of the first facing surface and the second facing surface is provided with a protruding portion that projects toward the other so as to surround the fastening member, and the first facing surface and the said portion other than the protruding portion. A partial gap is formed between the surface and the second facing surface.

上記（６）の構成によると、第１対向面及び第２対向面の少なくとも一方から他方に向かって突出する突出部において締結部材が第１部分と第２部分とを固定することにより、締結部材による固定の障害となるものが締結部材の周囲に存在しなくなるので、締結部材による第１部分と第２部分との固定力を高めることができる。 According to the configuration of (6) above, the fastening member fixes the first portion and the second portion at the protruding portion protruding from at least one of the first facing surface and the second facing surface toward the other, thereby fixing the fastening member. Since there is no obstacle to fixing by the fastening member around the fastening member, the fixing force between the first portion and the second portion by the fastening member can be increased.

（７）いくつかの実施形態では、上記（５）または（６）の構成において、
前記第１部分と前記第２部分とは、前記間隔があいた部分以外において、互いの間に断熱部材を挟むようにして固定されている。 (7) In some embodiments, in the configuration of (5) or (6) above,
The first portion and the second portion are fixed so as to sandwich a heat insulating member between them except for the portions where the distance is provided.

上記（７）の構成によると、断熱部材により熱伝導による第１部分から第２部分への熱移動がさらに抑制されるので、定格運転時における第２部分及びタービンロータの温度差の拡大がさらに抑制され、タービンロータと第２部分との間のクリアランスの拡大がさらに抑制される。その結果、定格運転時においてリング部材とタービンロータとの間からリークする蒸気の量をさらに低減できるので、蒸気タービンの性能をさらに向上することができる。 According to the configuration of (7) above, the heat insulating member further suppresses the heat transfer from the first portion to the second portion due to heat conduction, so that the temperature difference between the second portion and the turbine rotor during rated operation is further increased. It is suppressed and the expansion of the clearance between the turbine rotor and the second part is further suppressed. As a result, the amount of steam leaking from between the ring member and the turbine rotor during rated operation can be further reduced, so that the performance of the steam turbine can be further improved.

（８）いくつかの実施形態では、上記（１）〜（７）のいずれかの構成において、
前記少なくとも１つのシール部材は全て前記第２部分に保持される。 (8) In some embodiments, in any of the configurations (1) to (7) above,
The at least one sealing member is all held in the second portion.

上記（８）の構成によると、定格運転時における第２部分とタービンロータとの間のクリアランスが適正化されるので、シール部材による蒸気のシール機能が向上し、その結果、蒸気タービンの性能を向上することができる。 According to the configuration of (8) above, the clearance between the second part and the turbine rotor during rated operation is optimized, so that the steam sealing function by the sealing member is improved, and as a result, the performance of the steam turbine is improved. Can be improved.

（９）いくつかの実施形態では、上記（１）〜（８）のいずれかの構成において、
前記第１部分は２つの第１半体部を含み、該２つの第１半体部は互いの間に前記タービンロータを挟むようにして組み合わされた状態で固定されている。 (9) In some embodiments, in any of the configurations (1) to (8) above,
The first portion includes two first half bodies, and the two first half bodies are fixed in a combined state so as to sandwich the turbine rotor between them.

上記（９）の構成によると、蒸気タービンへの第１部分の組付けが容易になる。 According to the configuration of (9) above, the assembly of the first part to the steam turbine becomes easy.

（１０）いくつかの実施形態では、上記（１）〜（９）のいずれかの構成において、
前記第２部分は２つの第２半体部を含み、該２つの第２半体部は互いの間に前記タービンロータを挟むようにして組み合わされた状態で固定されている。 (10) In some embodiments, in any of the configurations (1) to (9) above,
The second part includes two second half parts, and the two second half parts are fixed in a combined state so as to sandwich the turbine rotor between them.

上記（１０）の構成によると、蒸気タービンへの第２部分の組付けが容易になる。 According to the configuration of (10) above, the assembly of the second part to the steam turbine becomes easy.

（１１）本発明の少なくとも１つの実施形態に係る蒸気タービンは、
タービンロータと、
上記（１）〜（１０）のいずれかのシール装置と
を備える。 ( 11 ) The steam turbine according to at least one embodiment of the present invention is
Turbine rotor and
The sealing device according to any one of (1) to ( 10) above is provided.

上記（１１）の構成によると、リング部材が、蒸気タービンの蒸気入口部に面するように設けられる第１部分と、リング部材とタービンロータとの間に形成された環形状の間隙をシールするシール部材が設けられた第２部分とに分割されていることにより、第１部分によって第２部分への入熱が抑制されることで第２部分の温度上昇が抑制される。このため、定格運転時における第２部分及びタービンロータの温度差の拡大が抑制されて、第２部分及びタービンロータの変形量の差が低減されるので、タービンロータと第２部分との間の間隙の幅（クリアランス）の拡大が抑制される。その結果、定格運転時においてリング部材とタービンロータとの間からリークする蒸気の量を低減できるので、蒸気タービンの性能を向上することができる。 According to the configuration of ( 11 ) above, the ring member seals the ring-shaped gap formed between the ring member and the turbine rotor with the first portion provided so as to face the steam inlet portion of the steam turbine. Since the seal member is divided into the second portion provided, the first portion suppresses the heat input to the second portion, so that the temperature rise of the second portion is suppressed. Therefore, the expansion of the temperature difference between the second portion and the turbine rotor during the rated operation is suppressed, and the difference in the amount of deformation between the second portion and the turbine rotor is reduced, so that the difference between the turbine rotor and the second portion is reduced. The expansion of the gap width (clearance) is suppressed. As a result, the amount of steam leaking from between the ring member and the turbine rotor during rated operation can be reduced, so that the performance of the steam turbine can be improved.

この発明によれば、リング部材が、蒸気タービンの蒸気入口部に面するように設けられる第１部分と、リング部材とタービンロータとの間に形成された環形状の間隙をシールするシール部材が設けられた第２部分とに分割されていることにより、第１部分によって第２部分への入熱が抑制されることで第２部分の温度上昇が抑制される。このため、定格運転時における第２部分及びタービンロータの温度差の拡大が抑制されて、第２部分及びタービンロータの変形量の差が低減されるので、タービンロータと第２部分との間の間隙の幅（クリアランス）の拡大が抑制される。その結果、定格運転時においてリング部材とタービンロータとの間からリークする蒸気の量を低減できるので、蒸気タービンの性能を向上することができる。また、湾曲部と整流部との間で第１部分と第２部分とが固定されているので、蒸気の整流効果を妨げずに第１部分と第２部分とを固定することができる。 According to the present invention, a sealing member that seals a ring-shaped gap formed between the ring member and the turbine rotor is provided with a first portion in which the ring member is provided so as to face the steam inlet portion of the steam turbine. By being divided into the provided second portion, the first portion suppresses the heat input to the second portion, so that the temperature rise of the second portion is suppressed. Therefore, the expansion of the temperature difference between the second portion and the turbine rotor during the rated operation is suppressed, and the difference in the amount of deformation between the second portion and the turbine rotor is reduced, so that the difference between the turbine rotor and the second portion is reduced. The expansion of the gap width (clearance) is suppressed. As a result, the amount of steam leaking from between the ring member and the turbine rotor during rated operation can be reduced, so that the performance of the steam turbine can be improved. Further, since the first portion and the second portion are fixed between the curved portion and the rectifying portion, the first portion and the second portion can be fixed without interfering with the rectifying effect of steam.

本発明の一実施形態に係る蒸気タービンの断面図である。It is sectional drawing of the steam turbine which concerns on one Embodiment of this invention. 図１のＩＩ−ＩＩ断面図である。FIG. 2 is a cross-sectional view taken along the line II-II of FIG. 図２のＩＩＩ−ＩＩＩ断面図である。FIG. 2 is a sectional view taken along line III-III of FIG. 図１のＩＶ−ＩＶ断面図である。FIG. 1 is a sectional view taken along line IV-IV of FIG.

以下、添付図面を参照して本発明のいくつかの実施形態について説明する。ただし、本発明の範囲は以下の実施形態に限定されるものではない。以下の実施形態に記載されている構成部品の寸法、材質、形状、その相対配置などは、本発明の範囲をそれにのみ限定する趣旨ではなく、単なる説明例に過ぎない。 Hereinafter, some embodiments of the present invention will be described with reference to the accompanying drawings. However, the scope of the present invention is not limited to the following embodiments. The dimensions, materials, shapes, relative arrangements, and the like of the components described in the following embodiments are not intended to limit the scope of the present invention only to them, but are merely explanatory examples.

図１に示されるように、蒸気タービン１は、車室２と、車室２内に回転可能に設けられたタービンロータ３とを備えている。車室２内には、タービンロータ３の周りに、環形状の翼環４が設けられている。翼環４には、タービンロータ３に向かって延びるように複数の静翼５（図１には１つの静翼のみが描かれている）が設けられ、タービンロータ３には、隣り合う静翼５間で翼環４に向かって延びるように複数の動翼６（図１には１つの動翼のみが描かれている）が設けられている。 As shown in FIG. 1, the steam turbine 1 includes a vehicle interior 2 and a turbine rotor 3 rotatably provided in the vehicle interior 2. In the vehicle interior 2, a ring-shaped blade ring 4 is provided around the turbine rotor 3. The blade ring 4 is provided with a plurality of stationary blades 5 (only one stationary blade is drawn in FIG. 1) so as to extend toward the turbine rotor 3, and the turbine rotor 3 is provided with adjacent stationary blades. A plurality of moving blades 6 (only one moving blade is drawn in FIG. 1) are provided so as to extend toward the wing ring 4 between the five blades.

また、車室２内には、タービンロータ３の周りに、環形状のリング部材であるダミーリング１０が設けられている。ダミーリング１０は、蒸気タービン１の蒸気入口部７に面するように設けられる第１部分１１と、タービンロータ３の軸方向において第１部分１１に対して蒸気入口部７とは反対側に位置する第２部分１２とに分割されている。 Further, in the vehicle interior 2, a dummy ring 10 which is a ring-shaped ring member is provided around the turbine rotor 3. The dummy ring 10 is located on the side opposite to the steam inlet portion 7 with respect to the first portion 11 provided so as to face the steam inlet portion 7 of the steam turbine 1 and the first portion 11 in the axial direction of the turbine rotor 3. It is divided into a second part 12 to be used.

タービンロータ３とダミーリング１０との間には、環形状の間隙８が形成されている。蒸気タービン１は、間隙８をシールするためのシール装置２０を備えている。シール装置２０は、間隙８に面する第２部分１２の内周面１２ｃに設けられた複数のシール部材２１を含んでいる。複数のシール部材２１は、タービンロータ３の軸方向に沿って設けられ、各シール部材２１は、タービンロータ３の周方向に沿って配置された複数のシールセグメント２１ａを含んでいる。 A ring-shaped gap 8 is formed between the turbine rotor 3 and the dummy ring 10. The steam turbine 1 includes a sealing device 20 for sealing the gap 8. The sealing device 20 includes a plurality of sealing members 21 provided on the inner peripheral surface 12c of the second portion 12 facing the gap 8. A plurality of sealing members 21 are provided along the axial direction of the turbine rotor 3, and each sealing member 21 includes a plurality of sealing segments 21a arranged along the circumferential direction of the turbine rotor 3.

第１部分１１は、円環板形状の取付部１３と、取付部１３よりもタービンロータ３の径方向外側に設けられた湾曲部１４と、取付部１３よりもタービンロータ３の径方向内側に設けられた整流部１５とを備えている。湾曲部１４は、円弧形状に湾曲した断面を有し、蒸気入口部７の環状流路９を車室２と共に構成している。整流部１５は、蒸気入口部７に面する表面１５ａが円弧状の湾曲した断面を含むとともに静翼５まで延びるように構成されている。第１部分１１の取付部１３、湾曲部１４及び整流部１５のそれぞれは、比較的厚く剛性があるため、後述する動作で蒸気入口部７に流入した蒸気の圧力による曲げ変形やたわみが生じにくい。 The first portion 11 has an annular plate-shaped mounting portion 13, a curved portion 14 provided on the radial outer side of the turbine rotor 3 with respect to the mounting portion 13, and a radial inner side of the turbine rotor 3 with respect to the mounting portion 13. It is provided with a rectifying unit 15 provided. The curved portion 14 has a cross section curved in an arc shape, and constitutes an annular flow path 9 of the steam inlet portion 7 together with the vehicle interior 2. The rectifying unit 15 is configured such that the surface 15a facing the steam inlet portion 7 includes an arcuate curved cross section and extends to the stationary blade 5. Since each of the mounting portion 13, the curved portion 14, and the rectifying portion 15 of the first portion 11 is relatively thick and rigid, bending deformation and bending due to the pressure of the steam flowing into the steam inlet portion 7 in the operation described later are unlikely to occur. ..

取付部１３には、タービンロータ３の周方向に沿って複数の貫通孔３１（図１には１つの貫通孔のみが描かれている）が形成されている。第２部分１２に対向する第１部分１１の表面である第１対向面１１ａから第２部分１２に向かって突出する円筒形状の複数の突出部３２が、各貫通孔３１を囲むように形成されている。第１部分１１に対向する第２部分１２の表面である第２対向面１２ａは、取付部１３に対向するとともにタービンロータ３の軸方向に直交する円環形状の取付面１２ｂを含んでいる。取付面１２ｂには、タービンロータ３の周方向に沿って複数の凹部３３（図１には１つの凹部のみが描かれている）が形成されている。貫通孔３１に挿入された締結部材であるボルト３４が凹部３３に挿入されることによって、第１部分１１が第２部分１２に固定される。突出部３２はボルト３４を囲むように取付面１２ｂに向かって突出しているので、第１対向面１１ａと第２対向面１２ａとの間には、突出部３２以外の部分で間隔３６があいている。 A plurality of through holes 31 (only one through hole is drawn in FIG. 1) are formed in the mounting portion 13 along the circumferential direction of the turbine rotor 3. A plurality of cylindrical protrusions 32 protruding from the first facing surface 11a, which is the surface of the first portion 11 facing the second portion 12, toward the second portion 12, are formed so as to surround the through holes 31. ing. The second facing surface 12a, which is the surface of the second portion 12 facing the first portion 11, includes an annular mounting surface 12b facing the mounting portion 13 and orthogonal to the axial direction of the turbine rotor 3. A plurality of recesses 33 (only one recess is drawn in FIG. 1) are formed on the mounting surface 12b along the circumferential direction of the turbine rotor 3. The first portion 11 is fixed to the second portion 12 by inserting the bolt 34, which is a fastening member inserted into the through hole 31, into the recess 33. Since the protruding portion 32 projects toward the mounting surface 12b so as to surround the bolt 34, there is a gap 36 between the first facing surface 11a and the second facing surface 12a at a portion other than the protruding portion 32. There is.

各突出部３２と取付面１２ｂとの間には、セラミックス製の断熱部材３５を設けてもよい。ただし、断熱部材３５は必須の構成要件ではなく、突出部３２と取付面１２ｂとが直接接するようにして第１部分１１と第２部分１２とが固定されてもよい。また、締結部材はボルト３４に限定するものではなく、ねじ、ピン、釘、リベット等であってもよい。 A ceramic heat insulating member 35 may be provided between each protrusion 32 and the mounting surface 12b. However, the heat insulating member 35 is not an indispensable constituent requirement, and the first portion 11 and the second portion 12 may be fixed so that the protruding portion 32 and the mounting surface 12b are in direct contact with each other. Further, the fastening member is not limited to the bolt 34, and may be a screw, a pin, a nail, a rivet or the like.

図２に示されるように、第１部分１１は、鉛直方向に２分割された２つの第１半体部４１，４２をボルト４３によって固定することによって構成されている。蒸気タービン１（図１参照）へ第１部分１１を組み付けるためには、第１半体部４１，４２の間にタービンロータ３（図１参照）を挟むようにして第１半体部４１，４２を組み合わせればよいので、蒸気タービン１への第１部分１１の組付けを容易に行うことができる。 As shown in FIG. 2, the first portion 11 is configured by fixing two first semi-body portions 41, 42 divided into two in the vertical direction by bolts 43. In order to assemble the first portion 11 to the steam turbine 1 (see FIG. 1), the first half body portions 41 and 42 are sandwiched between the first half body portions 41 and 42 so as to sandwich the turbine rotor 3 (see FIG. 1). Since it may be combined, the first portion 11 can be easily assembled to the steam turbine 1.

また、各貫通孔３１は、第１部分１１の周方向における開口幅Ｗ_１よりも第１部分１１の径方向における開口幅Ｗ_２の方が長い形状、すなわち、第１部分１１の径方向に長孔の形状を有している。貫通孔３１がこのような長孔の形状を有することにより、ボルト３４は貫通孔３１内で、第１部分１１の径方向にスライド可能となる。また、図３に示されるように、貫通孔３１は、ボルト３４の軸部３４ａが挿入されるように構成された第１孔部３１ａと、第１孔部３１ａに対して蒸気入口部７（図１参照）側に位置するとともにボルト３４の頭部３４ｂが挿入されるように構成された第２孔部３１ｂとを備えている。ボルト３４が貫通孔３１に挿入されて第１部分１１と第２部分１２（図１参照）とを固定する際、ボルト３４の頭部３４ｂの端面３４ｂ１が、蒸気入口部７に面する取付部１３の表面１３ａと面一となっている。尚、端面３４ｂ１は、表面１３ａよりも第２部分１２側、すなわち第２孔部３１ｂの内部に位置してもよい。 Further, each through hole 31 has a _{shape in which the opening width W 2} in the radial direction of the first portion 11 _{is longer than the opening width W 1} in the circumferential direction of the first portion 11, that is, in the radial direction of the first portion 11. It has the shape of a long hole. Since the through hole 31 has such an elongated shape, the bolt 34 can slide in the through hole 31 in the radial direction of the first portion 11. Further, as shown in FIG. 3, the through hole 31 includes a first hole portion 31a configured to insert the shaft portion 34a of the bolt 34 and a steam inlet portion 7 (with respect to the first hole portion 31a). It is provided with a second hole portion 31b located on the side (see FIG. 1) and configured to insert the head portion 34b of the bolt 34. When the bolt 34 is inserted into the through hole 31 to fix the first portion 11 and the second portion 12 (see FIG. 1), the end surface 34b1 of the head 34b of the bolt 34 faces the steam inlet portion 7. It is flush with the surface 13a of 13. The end surface 34b1 may be located on the second portion 12 side of the surface 13a, that is, inside the second hole portion 31b.

図４に示されるように、第２部分１２は、鉛直方向に２分割された２つの第２半体部４５，４６を、図示しないボルトによって固定することによって構成されている。蒸気タービン１（図１参照）へ第２部分１２を組み付けるためには、第２半体部４５，４６の間にタービンロータ３（図１参照）を挟むようにして第２半体部４５，４６を組み合わせればよいので、蒸気タービン１への第２部分１２の組付けを容易に行うことができる。 As shown in FIG. 4, the second portion 12 is configured by fixing two second semifield portions 45, 46, which are divided into two in the vertical direction, with bolts (not shown). In order to assemble the second part 12 to the steam turbine 1 (see FIG. 1), the second half bodies 45 and 46 are placed so as to sandwich the turbine rotor 3 (see FIG. 1) between the second half bodies 45 and 46. Since it may be combined, the second portion 12 can be easily assembled to the steam turbine 1.

次に、本発明の一実施形態に係るシール装置の動作について説明する。
図１に示されるように、蒸気タービン１の起動後、蒸気が蒸気入口部７に流入する。蒸気入口部７に流入した蒸気は翼環４内に流入し、動翼６に対して仕事をすることでタービンロータ３が回転する。 Next, the operation of the sealing device according to the embodiment of the present invention will be described.
As shown in FIG. 1, after the steam turbine 1 is started, steam flows into the steam inlet portion 7. The steam that has flowed into the steam inlet portion 7 flows into the blade ring 4, and works on the moving blades 6 to rotate the turbine rotor 3.

蒸気入口部７に流入した蒸気が翼環４内に流入する際、蒸気は、取付部１３及び整流部１５に沿って流れる。整流部１５は、蒸気入口部７に面する表面１５ａが円弧状の湾曲した断面を含むとともに静翼５まで延びるように構成されているので、蒸気は、整流部１５に沿って流れることによって整流されて翼環４内に流入する。蒸気は、整流部１５に沿って流れる前に取付部１３に沿って流れるが、ボルト３４の頭部３４ｂ（図３参照）が取付部１３の表面１３ａ（図３参照）に対して突出していると、頭部３４ｂによって蒸気の流れが乱されてしまい、翼環４内に流入する蒸気の整流効果が悪化してしまう。しかしながら、蒸気タービン１では、頭部３４ｂの端面３４ｂ１（図３参照）が、蒸気入口部７に面する取付部１３の表面１３ａと面一となっており、蒸気が取付部１３に沿って流れる際に乱されることがないので、翼環４内に流入する蒸気の整流効果の悪化を抑制することができる。 When the steam that has flowed into the steam inlet portion 7 flows into the blade ring 4, the steam flows along the mounting portion 13 and the rectifying portion 15. Since the rectifying unit 15 is configured such that the surface 15a facing the steam inlet portion 7 includes an arcuate curved cross section and extends to the stationary blade 5, steam is rectified by flowing along the rectifying unit 15. It is made to flow into the wing ring 4. The steam flows along the mounting portion 13 before flowing along the rectifying portion 15, but the head 34b (see FIG. 3) of the bolt 34 protrudes from the surface 13a (see FIG. 3) of the mounting portion 13. Then, the flow of steam is disturbed by the head 34b, and the rectifying effect of the steam flowing into the blade ring 4 is deteriorated. However, in the steam turbine 1, the end surface 34b1 (see FIG. 3) of the head 34b is flush with the surface 13a of the mounting portion 13 facing the steam inlet portion 7, and steam flows along the mounting portion 13. Since it is not disturbed at that time, it is possible to suppress deterioration of the rectifying effect of the steam flowing into the blade ring 4.

蒸気入口部７に蒸気が流入すると、第１部分１１に対する蒸気入口部７側と第２部分１２側との間で圧力差が生じ、この圧力差によって第１部分１１が第２部分１２に向かって押し付けられる力が第１部分１１に加えられる。蒸気タービン１では、ボルト３４がタービンロータ３の軸方向に第１部分１１と第２部分１２とを固定していることにより、この圧力差に起因する力がボルト３４をタービンロータ３の軸方向に第２部分１２に向かって押し付けることになるので、ボルト３４による第１部分１１と第２部分１２との固定力を高める効果が得られる。 When steam flows into the steam inlet portion 7, a pressure difference is generated between the steam inlet portion 7 side and the second portion 12 side with respect to the first portion 11, and this pressure difference causes the first portion 11 to move toward the second portion 12. The pressing force is applied to the first portion 11. In the steam turbine 1, the bolt 34 fixes the first portion 11 and the second portion 12 in the axial direction of the turbine rotor 3, so that the force caused by this pressure difference causes the bolt 34 to move the bolt 34 in the axial direction of the turbine rotor 3. Since it is pressed toward the second portion 12, the effect of increasing the fixing force between the first portion 11 and the second portion 12 by the bolt 34 can be obtained.

また、蒸気入口部７に蒸気が流入すると、蒸気が第１部分１１に接することにより、第１部分１１の温度が上昇する。これに対して、第２部分１２は、第１部分１１に遮蔽されることにより蒸気と直接には接しないものの、第１部分１１からの熱移動により温度が上昇し得る。しかしながら、蒸気タービン１では、第１対向面１１ａと第２対向面１２ａとの間に、突出部３２以外の部分で間隔３６があいており、第１部分１１から第２部分１２への熱移動は主に、突出部３２を介した熱伝導となる。このため、第１部分１１と第２部分１２との間に間隔３６がない場合、すなわち、第１対向面１１ａの全体と第２対向面１２ａの全体とが接している場合に比べて、第１部分１１と第２部分１２との接触面積が小さくなることにより、熱伝導による第１部分１１から第２部分１２への熱移動が抑制される。そうすると、定格運転時における第２部分１２の温度上昇が第１部分１１の温度上昇に比べて抑制され、第２部分１２とタービンロータ３との温度差が小さくなるので、タービンロータ３と第２部分１２との間の間隙８の幅（クリアランス）の拡大が抑制される。その結果、定格運転時においてダミーリング１０とタービンロータ３との間からリークする蒸気の量を低減できるので、蒸気タービン１の性能が向上する。 Further, when steam flows into the steam inlet portion 7, the temperature of the first portion 11 rises because the steam comes into contact with the first portion 11. On the other hand, although the second portion 12 is shielded by the first portion 11 and does not come into direct contact with steam, the temperature may rise due to heat transfer from the first portion 11. However, in the steam turbine 1, there is a gap 36 between the first facing surface 11a and the second facing surface 12a in a portion other than the protruding portion 32, and heat transfer from the first portion 11 to the second portion 12 Is mainly heat conduction through the protrusion 32. Therefore, as compared with the case where there is no gap 36 between the first portion 11 and the second portion 12, that is, when the entire first facing surface 11a and the entire second facing surface 12a are in contact with each other, the first By reducing the contact area between the first portion 11 and the second portion 12, heat transfer from the first portion 11 to the second portion 12 due to heat conduction is suppressed. Then, the temperature rise of the second portion 12 during the rated operation is suppressed as compared with the temperature rise of the first portion 11, and the temperature difference between the second portion 12 and the turbine rotor 3 becomes smaller, so that the temperature difference between the turbine rotor 3 and the second portion 12 becomes smaller. The expansion of the width (clearance) of the gap 8 with the portion 12 is suppressed. As a result, the amount of steam leaking from between the dummy ring 10 and the turbine rotor 3 during rated operation can be reduced, so that the performance of the steam turbine 1 is improved.

各突出部３２と取付面１２ｂとの間に断熱部材３５を設ける場合、断熱部材３５により熱伝導による第１部分１１から第２部分１２への熱移動がさらに抑制されるので、定格運転時における第２部分１２の温度上昇が第１部分１１の温度上昇に比べてさらに抑制され、第２部分１２とタービンロータ３との温度差がさらに小さくなるので、タービンロータ３と第２部分１２との間の間隙８も幅（クリアランス）の拡大がさらに抑制される。その結果、定格運転時においてダミーリング１０とタービンロータ３との間からリークする蒸気の量をさらに低減できるので、蒸気タービン１の性能がさらに向上する。 When the heat insulating member 35 is provided between each projecting portion 32 and the mounting surface 12b, the heat insulating member 35 further suppresses heat transfer from the first portion 11 to the second portion 12 due to heat conduction, and thus during rated operation. Since the temperature rise of the second portion 12 is further suppressed as compared with the temperature rise of the first portion 11, and the temperature difference between the second portion 12 and the turbine rotor 3 is further reduced, the temperature difference between the turbine rotor 3 and the second portion 12 is further reduced. The expansion of the width (clearance) of the gap 8 between them is further suppressed. As a result, the amount of steam leaking from between the dummy ring 10 and the turbine rotor 3 during rated operation can be further reduced, so that the performance of the steam turbine 1 is further improved.

一方、熱伝導による第１部分１１から第２部分１２への熱移動が抑制されると、第１部分１１と第２部分１２との温度差は大きくなる。その結果、タービンロータ３の径方向における第２部分１２の熱伸び量に比べて第１部分１１の熱伸び量が大きくなる。上述したように第１部分１１は比較的厚く剛性があるため、第１部分１１と第２部分１２とに熱伸び差が生じると、この熱伸び差により、ボルト３４による固定個所に応力が発生し得る。しかし、蒸気タービン１では、ボルト３４が挿入される貫通孔３１が第１部分１１の径方向に長孔の形状となっていることにより、第１部分１１は、貫通孔３１内でボルト３４がスライドするように熱伸びして、この熱伸び差を許容することができるので、ボルト３４による固定個所に応力が発生するのを抑制することができる。 On the other hand, when the heat transfer from the first portion 11 to the second portion 12 due to heat conduction is suppressed, the temperature difference between the first portion 11 and the second portion 12 becomes large. As a result, the amount of heat elongation of the first portion 11 is larger than the amount of heat elongation of the second portion 12 in the radial direction of the turbine rotor 3. As described above, since the first portion 11 is relatively thick and rigid, when a difference in thermal elongation occurs between the first portion 11 and the second portion 12, stress is generated at the fixed portion by the bolt 34 due to the difference in thermal elongation. Can be done. However, in the steam turbine 1, the through hole 31 into which the bolt 34 is inserted has a shape of an elongated hole in the radial direction of the first portion 11, so that the bolt 34 is inserted in the through hole 31 in the first portion 11. Since the heat is stretched so as to slide and this difference in heat stretch can be tolerated, it is possible to suppress the generation of stress at the fixed portion by the bolt 34.

このように、ダミーリング１０が、蒸気タービン１の蒸気入口部７に面するように設けられる第１部分１１と、ダミーリング１０とタービンロータ３との間に形成された環形状の間隙８をシールするシール部材２１が設けられた第２部分１２とに分割されていることにより、第１部分１１によって第２部分１２への入熱が抑制されることで第２部分１２の温度上昇が抑制される。このため、定格運転時における第２部分１２及びタービンロータ３の温度差の拡大が抑制されて、第２部分１２及びタービンロータ３の熱伸び差が低減されるので、タービンロータ３と第２部分１２との間の間隙８の幅（クリアランス）の拡大が抑制される。その結果、定格運転時においてダミーリング１０とタービンロータ３との間からリークする蒸気の量を低減できるので、蒸気タービン１の性能を向上することができる。 As described above, the ring-shaped gap 8 formed between the dummy ring 10 and the turbine rotor 3 is formed between the first portion 11 in which the dummy ring 10 is provided so as to face the steam inlet portion 7 of the steam turbine 1. Since the sealing member 21 for sealing is divided into the second portion 12, the first portion 11 suppresses the heat input to the second portion 12, and the temperature rise of the second portion 12 is suppressed. Will be done. Therefore, the expansion of the temperature difference between the second portion 12 and the turbine rotor 3 during the rated operation is suppressed, and the thermal elongation difference between the second portion 12 and the turbine rotor 3 is reduced, so that the turbine rotor 3 and the second portion The expansion of the width (clearance) of the gap 8 between 12 and 12 is suppressed. As a result, the amount of steam leaking from between the dummy ring 10 and the turbine rotor 3 during rated operation can be reduced, so that the performance of the steam turbine 1 can be improved.

また、この実施形態では、タービンロータ３の径方向において湾曲部１４と整流部１５との間で第１部分１１と第２部分１２とが固定されているので、蒸気の整流効果を妨げずに第１部分１１と第２部分１２とを固定することができる。 Further, in this embodiment, since the first portion 11 and the second portion 12 are fixed between the curved portion 14 and the rectifying portion 15 in the radial direction of the turbine rotor 3, the rectifying effect of steam is not hindered. The first portion 11 and the second portion 12 can be fixed.

この実施形態では、第２部分１２に設けられるシール部材２１の個数は任意であり、少なくとも１つのシール部材２１が設けられていればよい。また、シール部材２１の全てが第２部分１２に設けられることに限定するものではなく、シール部材２１の少なくとも１つを第１部分１１に設けてもよいが、シール部材２１の少なくとも１つは第２部分１２に設けられる必要がある。ただし、上述した動作によって、定格運転時における第２部分１２とタービンロータ３との間のクリアランスが適正化されるので、シール部材２１の全てを第２部分１２に設けることによりシール部材２１による蒸気のシール機能が向上し、その結果、蒸気タービン１の性能を向上することができる。 In this embodiment, the number of sealing members 21 provided in the second portion 12 is arbitrary, and at least one sealing member 21 may be provided. Further, not all of the seal members 21 are provided in the second portion 12, and at least one of the seal members 21 may be provided in the first portion 11, but at least one of the seal members 21 may be provided. It needs to be provided in the second part 12. However, since the clearance between the second portion 12 and the turbine rotor 3 during the rated operation is optimized by the above-described operation, the steam generated by the seal member 21 is provided by providing all of the seal members 21 in the second portion 12. As a result, the performance of the steam turbine 1 can be improved.

この実施形態では、突出部３２は第１対向面１１ａから第２部分１２に向かって突出しているが、この形態に限定するものではない。突出部は、各凹部３３を囲むように第２対向面１２ａから第１部分１１に向かって突出してもよい。または、第１対向面１１ａから第２部分１２に向かって突出する突出部と、第２対向面１２ａから第１部分１１に向かって突出する突出部とが両方設けられ、互いが接するように、又は、互いの間に断熱部材３５を挟むようにして第１部分１１と第２部分１２とが固定されてもよい。 In this embodiment, the protruding portion 32 protrudes from the first facing surface 11a toward the second portion 12, but the present invention is not limited to this embodiment. The protruding portion may project from the second facing surface 12a toward the first portion 11 so as to surround each recess 33. Alternatively, both a protruding portion protruding from the first facing surface 11a toward the second portion 12 and a protruding portion protruding from the second facing surface 12a toward the first portion 11 are provided so as to be in contact with each other. Alternatively, the first portion 11 and the second portion 12 may be fixed so as to sandwich the heat insulating member 35 between them.

１蒸気タービン
２車室
３タービンロータ
４翼環
５静翼
６動翼
７蒸気入口部
８間隙
９環状流路
１０ダミーリング（リング部材）
１１第１部分
１１ａ第１対向面
１２第２部分
１２ａ第２対向面
１２ｂ取付面
１２ｃ（第２部分の）内周面
１３取付部
１３ａ（取付部の）表面
１４湾曲部
１５整流部
２０シール装置
２１シール部材
２１ａシールセグメント
３１貫通孔
３１ａ第１孔部
３１ｂ第２孔部
３２突出部
３３凹部
３４ボルト（締結部材）
３４ａ（ボルトの）軸部
３４ｂ（ボルトの）頭部
３４ｂ１（頭部の）端面
３５断熱部材
３６間隔
４１第１半体部
４２第１半体部
４３ボルト
４５第２半体部
４６第２半体部 1 Steam turbine 2 Vehicle interior 3 Turbine rotor 4 Wing ring 5 Static blade 6 Moving blade 7 Steam inlet 8 Gap 9 Circular flow path 10 Dummy ring (ring member)
11 1st part 11a 1st facing surface 12 2nd part 12a 2nd facing surface 12b Mounting surface 12c (second part) inner peripheral surface 13 Mounting part 13a (mounting part) surface 14 Curved part 15 Rectifying part 20 Sealing device 21 Seal member 21a Seal segment 31 Through hole 31a First hole 31b Second hole 32 Protruding 33 Recess 34 Bolt (fastening member)
34a (Bolt) Shaft 34b (Bolt) Head 34b1 (Head) End Face 35 Insulation Member 36 Spacing 41 First Semifield 42 First Semifield 43 Bolt 45 Second Semifield 46 Second Half Body

Claims

A ring-shaped ring member provided around the turbine rotor and
A steam turbine sealing device including at least one sealing member held by the ring member and configured to seal a ring-shaped gap formed between the ring member and the turbine rotor. hand,
The ring member
A first portion provided so as to face the steam inlet portion of the steam turbine, and
It is divided into a second portion located on the side opposite to the steam inlet portion with respect to the first portion in the axial direction of the turbine rotor.
At least one of the at least one sealing member is held by the second portion .
The first part is
A curved portion forming a part of the annular flow path of the steam inlet portion and a curved portion.
A rectifying unit provided inside the turbine rotor in the radial direction with respect to the curved portion and rectifying steam at the steam inlet portion.
With
It said curved portion and said first portion between said rectifier and said second portion that is fixed, the seal device of the steam turbine in the radial direction.

The first portion and the second portion are fixed by at least one fastening member.
At least one through hole into which the at least one fastening member is inserted is formed in the first portion.
The steam turbine sealing device according to claim 1, wherein the through hole has a longer opening width in the radial direction of the first portion than an opening width in the circumferential direction of the first portion.

The through hole is
A first hole portion configured to insert a shaft portion of the fastening member, and a first hole portion.
It is provided with a second hole portion which is located on the steam inlet portion side with respect to the first hole portion and is configured so that the head of the fastening member is inserted.
The fastening member has a through hole so that the end surface of the head of the fastening member is flush with the surface of the first portion facing the steam inlet portion or is located on the second portion side of the surface. The steam turbine sealing device according to claim 2, wherein the first portion and the second portion are fixed to the steam turbine.

The steam turbine sealing device according to claim 2 or 3, wherein the fastening member fixes the first portion and the second portion in the axial direction of the turbine rotor.

The first portion includes a first facing surface facing the second portion.
The second portion includes a second facing surface facing the first portion.
Any one of claims 1 to 4, wherein the first portion and the second portion are fixed so as to be partially spaced between the first facing surface and the second facing surface. The steam turbine sealing device described in the section.

The first portion and the second portion are fixed by at least one fastening member.
At least one of the first facing surface and the second facing surface is provided with a protruding portion that projects toward the other so as to surround the fastening member, and the first facing surface and the said portion other than the protruding portion. The steam turbine sealing device according to claim 5, wherein a partial distance is formed from the second facing surface.

The steam turbine sealing device according to claim 5 or 6, wherein the first portion and the second portion are fixed so as to sandwich a heat insulating member between the first portion and the second portion other than the portions where the distance is provided.

The steam turbine sealing device according to any one of claims 1 to 7, wherein the at least one sealing member is all held in the second portion.

The first part includes two first half bodies, and the two first half bodies are fixed in a combined state so as to sandwich the turbine rotor between them. The steam turbine sealing device according to any one item.

The second part includes two second halves, and the two second halves are fixed in a combined state so as to sandwich the turbine rotor between them. The steam turbine sealing device according to any one item.

Turbine rotor and
A steam turbine comprising the sealing device according to any one of claims 1 to 10.