WO2015083588A1 - シール構造、及び回転機械 - Google Patents
シール構造、及び回転機械 Download PDFInfo
- Publication number
- WO2015083588A1 WO2015083588A1 PCT/JP2014/081181 JP2014081181W WO2015083588A1 WO 2015083588 A1 WO2015083588 A1 WO 2015083588A1 JP 2014081181 W JP2014081181 W JP 2014081181W WO 2015083588 A1 WO2015083588 A1 WO 2015083588A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- fin
- gap
- seal
- protrusion
- vortex
- Prior art date
Links
- 238000011144 upstream manufacturing Methods 0.000 claims description 27
- 238000007789 sealing Methods 0.000 claims description 11
- 230000002093 peripheral effect Effects 0.000 description 7
- 238000005192 partition Methods 0.000 description 5
- 230000003247 decreasing effect Effects 0.000 description 4
- 230000000694 effects Effects 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 239000007787 solid Substances 0.000 description 2
- 230000003068 static effect Effects 0.000 description 2
- 239000012530 fluid Substances 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000006467 substitution reaction Methods 0.000 description 1
Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D11/00—Preventing or minimising internal leakage of working-fluid, e.g. between stages
- F01D11/02—Preventing or minimising internal leakage of working-fluid, e.g. between stages by non-contact sealings, e.g. of labyrinth type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D11/00—Preventing or minimising internal leakage of working-fluid, e.g. between stages
- F01D11/08—Preventing or minimising internal leakage of working-fluid, e.g. between stages for sealing space between rotor blade tips and stator
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
- F01D5/12—Blades
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
- F01D5/12—Blades
- F01D5/22—Blade-to-blade connections, e.g. for damping vibrations
- F01D5/225—Blade-to-blade connections, e.g. for damping vibrations by shrouding
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16J—PISTONS; CYLINDERS; SEALINGS
- F16J15/00—Sealings
- F16J15/44—Free-space packings
- F16J15/447—Labyrinth packings
- F16J15/4472—Labyrinth packings with axial path
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2220/00—Application
- F05D2220/30—Application in turbines
- F05D2220/31—Application in turbines in steam turbines
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
- F05D2220/00—Application
- F05D2220/30—Application in turbines
- F05D2220/32—Application in turbines in gas turbines
Definitions
- the present invention relates to a seal structure that seals a gap between structures that rotate relative to each other in a rotary machine such as a steam turbine and a gas turbine, and to a rotary machine that includes this seal structure.
- a non-contact type seal structure such as a labyrinth seal is used to prevent leakage of working fluid such as steam from a gap formed between the stationary side and the rotating side. It is used.
- the labyrinth seal there is a step type having a seal member such as a seal fin extending toward the rotor blade on the inner periphery of the casing that forms the outer shell of the rotating machine, and a step-like shroud provided at the tip of the rotor blade. It is known (see, for example, Patent Document 1).
- a step type having a plurality of seal fins 17, 18, 19 extending from the casing 10 and a step portion 3 formed on a shroud 51 provided at the tip of the moving blade 50.
- the labyrinth seal 102 includes an upstream cavity 25 that forms a forward step and a downstream cavity 26 that forms a backward step.
- the leak jet SL that has passed through the upstream gap mA between the upstream seal fin 17 and the base surface 4 of the shroud 51 forms a vortex B, while upstream of the step portion 3.
- the leak jet SL is deflected by colliding with the surface.
- leakage of the leak jet SL2 into the intermediate gap mB between the intermediate seal fin 18 and the step portion 3 is suppressed, and the amount of leakage is reduced.
- the reattachment point of the leak jet SL2 passing through the intermediate gap mB becomes unstable and the sealing performance becomes unstable.
- the flow rate of the leak jet SL3 that blows through the downstream gap mC increases, and the amount of leakage increases.
- An object of the present invention is to provide a rotating machine that can reduce a leak jet that leaks from a gap formed between a stationary side and a rotating side, and can stabilize sealing performance.
- the seal structure includes a first structure and a second structure that faces the first structure in the radial direction and rotates relative to the first structure about an axis.
- a seal structure that seals a gap between the body and one of the first structure and the second structure includes a base surface and a step surface that protrudes to the other side of the base surface.
- the other has a first fin extending toward the step surface and forming a first gap with the step surface; and extending toward the base surface on the downstream side of the first fin.
- a second fin that forms a second gap with the base surface, and a leak flow that is disposed between the first fin and the second fin and passes through the first gap is transferred to the first fin.
- the leak flow that has passed through the first gap is divided into the first vortex and the second vortex by the protrusion, and the leak flow is prevented from re-adhering to the base surface, so that the leak flow into the second gap is suppressed. Leakage flow is reduced. Thereby, sealing performance can be stabilized.
- the protrusion is circumferential between the downstream end of the step surface and the second fin in the axial direction and between the step surface and the other in the radial direction. It is good also as a structure which has a redeposition edge which extends in length and reattaches the said leak flow. According to the above configuration, the leak flow that has passed through the first gap can be stably reattached to the reattachment edge of the protrusion.
- the protrusion is connected to the upstream side of the second fin, and extends between the other and the reattachment edge, the reattachment edge, and the second fin.
- a cylindrical surface that is a concentric cylindrical surface extending in the direction of the axis, and the shape viewed from the circumferential direction may be a rectangular member.
- the protrusion may be connected to an upstream surface of the second fin and may be a cylindrical member concentric with the axis extending between the reattachment edge and the second fin. Good.
- the first vortex on the downstream side of the first fin is increased, the vorticity of the first vortex is decreased, and the static pressure is increased, so that the pressure difference before and after the first fin is decreased. Thereby, the leakage amount can be further reduced.
- the protrusion may be a disk-shaped member extending between the other and the reattachment edge. According to the above configuration, a vortex is generated on the downstream side of the protrusion, and kinetic energy is dissipated into heat due to mixing loss in the vortex, resulting in a total pressure loss. Thereby, the leakage amount can be further reduced.
- the present invention also provides a rotating machine having any one of the above-described seal structures.
- the leak flow that has passed through the first gap is divided into the first vortex and the second vortex by the protrusion, and the leak flow is suppressed from re-adhering to the base surface.
- the flow through is reduced. Thereby, sealing performance can be stabilized.
- a steam turbine 1 of the present embodiment is provided with a casing 10 (structure) and a rotating shaft that is rotatably provided inside the casing 10 and transmits power to a machine such as a generator (not shown).
- a machine such as a generator (not shown).
- a stationary blade 40 held in the casing 10 a moving blade 50 provided on the rotary shaft 30, and a bearing portion 60 that supports the rotary shaft 30 so as to be rotatable about the axis.
- the steam S is introduced from a main inlet 21 formed in the casing 10 through a steam supply pipe 20 connected to a steam supply source (not shown) and discharged from a steam discharge pipe 22 connected to the downstream side of the steam turbine 1. Is done.
- the stationary blade 40 and the moving blade 50 are blades extending in the radial direction of the axis O.
- the casing 10 is a structure that rotates relative to the rotor blade 50 about the axis O.
- the internal space of the casing 10 is hermetically sealed.
- the casing 10 is a flow path for the steam S.
- a ring-shaped partition plate outer ring 11 through which the rotation shaft 30 is inserted is firmly fixed to the inner wall surface of the casing 10.
- the bearing unit 60 includes a journal bearing device 61 and a thrust bearing device 62, and supports the rotary shaft 30 in a freely rotatable manner.
- the stationary blades 40 extend from the casing 10 toward the inner peripheral side, and constitute a group of annular stationary blades arranged radially so as to surround the rotating shaft 30.
- the plurality of stationary blades 40 are respectively held by the partition plate outer ring 11.
- a plurality of annular stator blade groups composed of a plurality of stator blades 40 are formed at intervals in the axial direction of the rotating shaft 30 (hereinafter simply referred to as the axial direction).
- the plurality of stationary blades 40 convert the pressure energy of the steam S into velocity energy and flow into the moving blade 50 adjacent to the downstream side.
- the rotor blade 50 is firmly attached to the outer peripheral portion of the rotary shaft main body 31 of the rotary shaft 30.
- a large number of moving blades 50 are arranged radially on the downstream side of each annular stationary blade group to constitute an annular moving blade group.
- the annular stator blade group and the annular rotor blade group are one set and one stage.
- the tip part of the moving blade 50 in the final stage is connected to the tip parts of the moving blades adjacent to each other in the circumferential direction (hereinafter simply referred to as the circumferential direction) of the rotating shaft 30 and is called a shroud 51. .
- a cylindrical annular shape whose diameter is increased from the inner peripheral portion of the partition plate outer ring 11 and the inner peripheral surface of the casing 10 is the bottom surface 13 (opposing surface).
- a groove 12 is formed.
- a shroud 51 is accommodated in the annular groove 12, and the bottom surface 13 faces the shroud 51 in the radial direction via the gap Gd.
- the shroud 51 includes a step portion 3 formed in a step shape with a central portion protruding in the axial direction.
- the radially outer peripheral surface of the shroud 51 includes a base surface 4 (tip surface) and a step portion 3 that constitutes a step surface 5 that protrudes more radially outward than the base surface 4. is doing.
- the bottom surface 13 is provided with three seal fins 17, 18, 19 extending in the radial direction toward the shroud 51.
- the seal fins 17, 18, and 19 extend from the bottom surface 13 toward the inner peripheral side toward the shroud 51, and extend in the circumferential direction.
- the upstream seal fin 17 protrudes toward the base surface 4 on the upstream side of the step portion 3.
- the intermediate seal fin 18 (first fin) protrudes toward the step surface 5 of the step portion 3.
- the downstream seal fin 19 (second fin) protrudes toward the base surface 4 on the downstream side of the step portion 3.
- the intermediate seal fin 18 is formed to have a shorter radial length than the upstream seal fin 17 and the downstream seal fin 19. That is, the seal structure 2 that is a step-type labyrinth seal is provided in the gap Gd between the casing 10 and the moving blade 50 of the present embodiment.
- seal fins 17, 18, and 19 form a shroud 51 and a minute gap m in the radial direction.
- the gap between the upstream seal fin 17 and the base surface 4 is the upstream gap mA
- the gap between the intermediate seal fin 18 and the step surface 5 is the intermediate gap mB (first gap)
- the downstream seal fin 19 and the base surface. 4 is called a downstream gap mC (second gap).
- Each dimension of the minute gap m takes into consideration the thermal elongation amount of the casing 10 and the moving blade 50, the centrifugal elongation amount of the moving blade 50, and the like.
- Each dimension of the minute gap m (mA to mC) is set in a range in which the seal fins 17, 18, 19 and the moving blade 50 do not contact each other.
- An upstream cavity 25 and a downstream cavity 26 are formed in the gap Gd by the annular groove 12, the shroud 51, and the seal fins 17, 18, and 19. The positions of the seal fins 17, 18, 19 in the axial direction are appropriately set according to the behavior of leak jets and vortices in the cavities 25, 26.
- the protrusion 7 is a solid member having a rectangular cross-sectional shape when viewed from the circumferential direction, and extends in the circumferential direction together with the downstream seal fin 19.
- the protrusion 7 is a cylindrical surface 8 that is orthogonal to the axial direction on the upstream side of the downstream seal fin 19 and a cylindrical surface that is orthogonal to the circular surface 8 and extends in the circumferential direction and concentric with the axial line.
- a ridge line where the disc surface 8 and the cylindrical surface 9 intersect with each other is a reattachment edge 15.
- the disk surface 8 and the cylindrical surface 9 are surfaces for determining the position of the reattachment edge 15.
- the disc surface 8 is located between the downstream end of the step surface 5 and the downstream seal fin 19 in the axial direction. Specifically, it arrange
- the cylindrical surface 9 is located between the step surface 5 and the bottom surface 13 of the annular groove 12 in the radial direction. Specifically, it is arranged based on the position of the reattachment edge 15.
- steam S flows into the internal space of the casing 10 through a steam supply pipe 20 from a steam supply source such as a boiler (not shown).
- the steam S flowing into the internal space of the casing 10 sequentially passes through the annular stator blade group and the annular rotor blade group in each stage.
- the steam S increases in the circumferential velocity component while passing through the stationary blade 40 in the annular stationary blade group of each stage.
- Most of the steam SM (see FIG. 2) of the steam S flows between the rotor blades 50, and the energy of the steam SM is converted into rotational energy, so that the rotation shaft 30 is rotated.
- a part of the steam S (for example, about several percent) of the leak jet SL (leakage flow, leak flow), after flowing out of the stationary blade 40, is annular in a state where a strong circumferential component is maintained (swirl flow). It flows into the groove 12.
- the leak jet SL collides with the surface facing the upstream side of the step portion 3 and deflects while forming the vortex B1. Thereby, the leakage amount of the leak jet SL to the intermediate gap mB is reduced.
- the leak jet SL2 that has passed through the intermediate gap mB stably reattaches to the reattachment edge 15 of the protrusion 7 provided on the downstream side.
- the reattachment point of the leak jet SL2 is controlled, and a vortex B3 (first vortex) is formed in a space surrounded by the leak jet SL, the intermediate seal fin 18 and the disk surface 8, and the leak jet SL2
- a vortex B4 (second vortex) is formed in a space surrounded by the cylindrical surface 9 and the base surface 4.
- the leak jet SL2 is divided by the protrusion 7 into a vortex B3 along the intermediate seal fin 18 and a vortex B4 along the downstream seal fin 19.
- the vortex B4 collides with the downstream seal fin 19 and becomes a flow that faces the leak jet SL3 that passes through the downstream gap mC, so that the leak jet SL3 is reduced.
- the position of the reattachment edge 15 is set to a position where the leak jet SL2 that has passed through the intermediate gap mB easily reattaches.
- the reattachment edge 15 of the present embodiment is set slightly radially outside the step surface 5 in the radial direction, and is set near an intermediate point between the downstream end of the step surface 5 and the downstream seal fin 19 in the axial direction. ing.
- the position of the reattachment edge 15 depends on the specifications of the steam turbine 1, for example, the distance between the shroud 51 and the bottom surface 13, the flow rate of the swirling flow flowing into the cavities 25, 26, etc. It is calculated as appropriate using an analysis using.
- the leak jet SL2 that has passed through the intermediate gap mB is stably reattached to the reattachment edge 15 of the protrusion 7. That is, it is possible to stabilize the sealing performance by suppressing the leak jet SL2 from reattaching to the base surface 4 and reducing the blow-through of the leak jet SL3 to the downstream gap mC.
- the flow rate of the leak jet SL3 can be reduced by the vortex B4 formed by the leak jet SL2 reattaching to the reattachment edge 15 of the protrusion 7.
- the disk surface 8 of this embodiment is formed so that the main surface may be orthogonal to the axis line O, it is not this limitation if the position of the reattachment edge 15 can be maintained as set.
- the disk surface 8 may have a shape that inclines toward the upstream side toward the radially outer peripheral side.
- the cylindrical surface 9 of the present embodiment may also have a shape that inclines toward the radially inner periphery as it goes downstream.
- the protrusion 7 is not solid and may have a hollow structure.
- the protrusion 7 ⁇ / b> B of the seal structure 2 ⁇ / b> B of this embodiment is a cylindrical member that protrudes upstream from the upstream surface 19 a of the downstream seal fin 19 and extends in the circumferential direction.
- the protrusion 7B is connected to the upstream surface 19a of the downstream seal fin 19 and is concentric with an axis O (see FIG. 1) extending between the reattachment edge 15 and the downstream seal fin 19. It is a member.
- the leak jet SL2 that has passed through the intermediate gap mB is reattached to the reattachment edge 15 that is the end on the most upstream side of the protrusion 7B, and a large vortex B5 is generated downstream of the intermediate seal fin 18.
- the vortex B5 on the downstream side of the intermediate seal fin 18 is increased, the vorticity of the vortex B5 is decreased, and the static pressure is increased, whereby the pressure difference between the front and rear of the intermediate seal fin 18 is decreased.
- the leakage amount can be further reduced.
- the protrusion 7 ⁇ / b> C of the seal structure 2 ⁇ / b> C of the present embodiment is disposed between the intermediate seal fin 18 and the downstream seal fin 19, and is directed from the bottom surface 13 of the annular groove 12 toward the base surface 4 of the shroud 51. And a disk-shaped member extending in the radial direction.
- the protrusion 7 ⁇ / b> C of the present embodiment is a disk-shaped member that extends between the bottom surface 13 of the annular groove 12 and the reattachment edge 15.
- the leak jet SL2 that has passed through the intermediate gap mB is reattached to the reattachment edge 15 that is the end on the most upstream side of the protrusion 7C, and a further vortex B6 is generated downstream of the protrusion 7C.
- the vortex B6 is generated on the downstream side of the protrusion 7C, and the kinetic energy is dissipated by heat due to the mixing loss in the vortex, resulting in a total pressure loss.
- the amount of leaks can be reduced further.
- the present invention can be applied to a shaft seal between a turbine casing and a rotor, a seal between a blade and a casing of an axial compressor, a seal between a centrifugal compressor casing and an impeller, and the like.
- the seal structure of each of the embodiments described above includes a second structure that is opposed to the first structure in the radial direction via a gap and that rotates relative to the first structure about the axis, A plurality of seal fins provided on one of the structure and the second structure, projecting toward the other and forming a minute gap between the other and spaced apart in the axial direction; It can be applied to a rotating machine equipped with
- the leak flow that has passed through the first gap is divided into the first vortex and the second vortex by the protrusions, and the leak flow is prevented from reattaching to the base surface, and thus to the second gap.
- the leakage of the leak flow is reduced. Thereby, sealing performance can be stabilized.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Turbine Rotor Nozzle Sealing (AREA)
- Sealing Using Fluids, Sealing Without Contact, And Removal Of Oil (AREA)
Abstract
Description
本願は、2013年12月3日に出願された特願2013-250307号について優先権を主張し、その内容をここに援用する。
ラビリンスシールとしては、回転機械の外郭をなすケーシングの内周に動翼に向かって伸びるシールフィン等のシール部材と、動翼の先端に設けられたステップ状のシュラウドとを有するステップ型のものが知られている(例えば特許文献1参照)。
上記構成によれば、第一間隙を通過したリーク流を突部の再付着縁に安定的に再付着させることができる。
上記構成によれば、突部の下流側に渦が生成され、渦内のミキシングロスにより運動エネルギーが熱に散逸し、全圧損失が生じる。これにより、更に漏れ量を低減することができる。
以下、本発明の第一実施形態の回転機械である蒸気タービンについて図面に基づき説明する。
図1に示すように、本実施形態の蒸気タービン1は、ケーシング10(構造体)と、ケーシング10の内方に回転自在に設けられ、動力を図示しない発電機等の機械に伝達する回転軸30と、ケーシング10に保持された静翼40と、回転軸30に設けられた動翼50と、回転軸30を軸回りに回転可能に支持する軸受部60とを備えている。
静翼40及び動翼50は軸線Oの径方向に延びるブレードである。ケーシング10は、動翼50に対して軸線O回りに相対回転する構造体である。
軸受部60は、ジャーナル軸受装置61及びスラスト軸受装置62を備えており、回転軸30を回転自在に支持している。
環状静翼群と環状動翼群とは、一組一段とされている。このうち、最終段における動翼50の先端部は、回転軸30の周方向(以下、単に周方向と呼ぶ)に隣接する動翼の先端部同士と連結されておりシュラウド51と呼ばれている。
シュラウド51は、軸方向における中央部分が突出してステップ状に形成されたステップ部3を備えている。具体的には、シュラウド51の径方向外周側の面は、ベース面4(先端面)と、ベース面4よりも径方向外周側に突出するステップ面5を構成するステップ部3と、を有している。
即ち、本実施形態のケーシング10と動翼50との間の隙間Gdには、ステップ型のラビリンスシールであるシール構造2が設けられている。
隙間Gdには、環状溝12、シュラウド51、及びシールフィン17,18,19によって上流側キャビティ25と、下流側キャビティ26とが形成される。シールフィン17,18,19の軸線方向の位置は、これらキャビティ25,26内におけるリークジェットや渦の挙動に応じて適宜設定される。
突起7は、下流シールフィン19の上流側にて軸線方向に直交する円板面8と、円板面8と直交するとともに周方向に延在する、軸線と同心の円筒状の面である円筒面9と、を有している。円板面8と円筒面9とが交わる稜線は、再付着縁15とされている。換言すれば、円板面8と円筒面9は、再付着縁15の位置を確定するための面である。
円筒面9は、径方向において、ステップ面5と環状溝12の底面13との間に位置している。具体的には、再付着縁15の位置に基づいて配置されている。
まず、図示しないボイラなどの蒸気供給源から蒸気供給管20を介して、蒸気Sがケーシング10の内部空間に流入する。
ケーシング10の内部空間に流入した蒸気Sは、各段における環状静翼群と環状動翼群とを順次通過する。
一方、蒸気Sのうち一部(例えば、約数%)のリークジェットSL(漏れ流、リーク流)は、静翼40から流出した後、強い周方向成分を維持した状態(旋回流)で環状溝12に流入する。
中間間隙mBを通過したリークジェットSL2は、下流側に設けられた突起7の再付着縁15に安定的に再付着する。即ち、リークジェットSL2の再付着点が制御され、リークジェットSLと中間シールフィン18と、円板面8とによって囲まれた空間に渦B3(第一渦)が形成されるとともに、リークジェットSL2と円筒面9とベース面4とによって囲まれた空間に渦B4(第二渦)が形成される。換言すれば、リークジェットSL2は、突起7によって中間シールフィン18に沿う渦B3と、下流シールフィン19に沿う渦B4とに分断される。
これにより、リークジェットSL2が、底面13や、ベース面4(ステップ部3)に再付着することが抑制される。
図4に示すように、渦B4は、下流シールフィン19に衝突して下流間隙mCを通過するリークジェットSL3に対向する流れとなるため、リークジェットSL3が低減される。
再付着縁15の位置は、中間間隙mBを通過したリークジェットSL2が再付着しやすい位置に設定される。本実施形態の再付着縁15は、径方向においてステップ面5よりもやや径方向外周側であって、軸線方向においてステップ面5の下流側端部と下流シールフィン19の中間点付近に設定されている。
再付着縁15は、このような回転軸30とケーシング10間との間で相対位置が変化した場合においても再付着縁15が、ステップ面5に対して径方向に対向する位置にならないように設定されている。換言すれば、突起7は、再付着縁15が常にベース面4と径方向に対向するように設定されている。
同様に、本実施形態の円筒面9も下流側に向かうに従って、径方向内周側に傾斜するような形状としてもよい。
また、突起7は中実とせず、中空構造としてもよい。
以下、本発明の第二実施形態の蒸気タービンのシール構造を図面に基づいて説明する。なお、本実施形態では、上述した第一実施形態との相違点を中心に述べ、同様の部分についてはその説明を省略する。
図5に示すように、本実施形態のシール構造2Bの突起7Bは、下流シールフィン19の上流側の面19aから上流側に突出するとともに、周方向に延在する円筒状の部材である。換言すれば、突起7Bは、下流シールフィン19の上流側の面19aに接続され、再付着縁15と下流シールフィン19との間に延在する軸線O(図1参照)と同心の円筒状の部材である。
以下、本発明の第二実施形態の蒸気タービンのシール構造を図面に基づいて説明する。なお、本実施形態では、上述した第一実施形態との相違点を中心に述べ、同様の部分についてはその説明を省略する。
図6に示すように、本実施形態のシール構造2Cの突起7Cは、中間シールフィン18と下流シールフィン19との間に配置され、環状溝12の底面13からシュラウド51のベース面4に向けて径方向に延出する円板状の部材である。換言すれば、本実施形態の突起7Cは、環状溝12の底面13と再付着縁15との間に延在する円板状の部材である。
例えば、上記各実施形態では、動翼50の先端側(回転側)に設けられたシュラウド51のステップ部3と、環状溝12の底面13(静止側)に設けられたシールフィン17,18,19とでラビリンスシールを構成したが、これに限ることはない。例えば、回転側である動翼の側にシールフィンを設けるとともに、静止側である環状溝12(ケーシング)にステップ部を設ける構成としてもよい。
また、動翼が設けられていない回転軸とケーシングとの間の隙間をシールするラビリンスシールに適用してもよい。例えば、タービン車室とローター間の軸封シールや、軸流圧縮機のブレード-ケーシング間のシール、遠心圧縮機ケーシング-インペラ間のシールなどに適用することができる。
換言すれば、上記各実施形態のシール構造は、第一構造体に隙間を介して径方向に対向するとともに、第一構造体に対して軸線回りに相対回転する第二構造体と、第一構造体と第二構造体とのいずれか一方に設けられて、他方に向かって突出して他方との間に微小隙間を形成するとともに軸線方向に間隔をあけて設けられた複数のシールフィンと、を備える回転機械に適用が可能である。
2,2B,2C シール構造
3 ステップ部
4 ベース面
5 ステップ面
7 突起(突部)
8 円板面
9 円筒面
10 ケーシング(第一構造体、第二構造体)
11 仕切板外輪
12 環状溝
13 底面
15 再付着縁
17 上流シールフィン
18 中間シールフィン(第一フィン)
19 下流シールフィン(第二フィン)
25 上流側キャビティ
26 下流側キャビティ
30 回転軸
31 軸本体
32 ディスク
40 静翼(ブレード)
50 動翼(ブレード)
51 シュラウド(第一構造体、第二構造体)
60 軸受部
61 ジャーナル軸受装置
62 スラスト軸受装置
B3 渦(第一渦)
B4 渦(第二渦)
Gd 隙間
mA 上流間隙
mB 中間間隙(第一間隙)
mC 下流間隙(第二間隙)
O 軸線
SL リークジェット(リーク流)
Claims (6)
- 第一構造体と、前記第一構造体に径方向に対向するとともに前記第一構造体に対して軸線回りに相対回転する第二構造体との間の隙間をシールするシール構造であって、
前記第一構造体と第二構造体のうちの一方は、ベース面と、前記ベース面よりも他方側に突出するステップ面と、を有し、
前記他方は、前記ステップ面に向かって延びて前記ステップ面との間で第一間隙を形成する第一フィンと、前記第一フィンの下流側にて前記ベース面に向かって延びて前記ベース面との間で第二間隙を形成する第二フィンと、
前記第一フィンと前記第二フィンとの間に配置されて、前記第一間隙を通過したリーク流を、第一フィンに沿う第一渦と第二フィンに沿う第二渦とに分断する突部と、を備えるシール構造。 - 前記突部は、前記軸線方向において前記ステップ面の下流側端部と前記第二フィンとの間、かつ、前記径方向において前記ステップ面と前記他方との間に、周方向に延在して前記リーク流を再付着させる再付着縁を有する請求項1に記載のシール構造。
- 前記突部は、前記第二フィンの上流側に接続され、前記他方と前記再付着縁との間に延在する円板面と、前記再付着縁と前記第二フィンとの間に延在する前記軸線と同心の円筒状の面である円筒面とを有し、周方向から見た形状が矩形状をなす部材である請求項2に記載のシール構造。
- 前記突部は、前記第二フィンの上流側の面に接続され、前記再付着縁と前記第二フィンとの間に延在する前記軸線と同心の円筒状の部材である請求項2に記載のシール構造。
- 前記突部は、前記他方と前記再付着縁との間に延在する円板状の部材である請求項2に記載のシール構造。
- 請求項1から請求項5のいずれか一項に記載のシール構造を備える回転機械。
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CN201480065520.9A CN105934615B (zh) | 2013-12-03 | 2014-11-26 | 密封构造及旋转机械 |
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US20170022838A1 (en) | 2017-01-26 |
EP3078888A4 (en) | 2017-08-30 |
JP2015108301A (ja) | 2015-06-11 |
KR20160079046A (ko) | 2016-07-05 |
EP3078888B1 (en) | 2020-08-05 |
US10385714B2 (en) | 2019-08-20 |
JP6131177B2 (ja) | 2017-05-17 |
CN105934615B (zh) | 2021-06-18 |
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KR101852700B1 (ko) | 2018-04-26 |
CN105934615A (zh) | 2016-09-07 |
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