EP1861584B1 - Heat accumulation segment for sealing a flow channel of a turbine engine - Google Patents
Heat accumulation segment for sealing a flow channel of a turbine engine Download PDFInfo
- Publication number
- EP1861584B1 EP1861584B1 EP06725191A EP06725191A EP1861584B1 EP 1861584 B1 EP1861584 B1 EP 1861584B1 EP 06725191 A EP06725191 A EP 06725191A EP 06725191 A EP06725191 A EP 06725191A EP 1861584 B1 EP1861584 B1 EP 1861584B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- contour
- sealing means
- joining
- reception
- heat shield
- 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.)
- Not-in-force
Links
- 238000007789 sealing Methods 0.000 title claims description 58
- 238000009825 accumulation Methods 0.000 title description 8
- 238000000926 separation method Methods 0.000 claims abstract description 4
- 239000003566 sealing material Substances 0.000 claims description 5
- 239000007769 metal material Substances 0.000 claims description 4
- 239000007787 solid Substances 0.000 claims 1
- 230000000295 complement effect Effects 0.000 abstract 1
- 239000000565 sealant Substances 0.000 description 21
- 239000007789 gas Substances 0.000 description 10
- 238000001816 cooling Methods 0.000 description 8
- 239000000463 material Substances 0.000 description 7
- 230000000694 effects Effects 0.000 description 5
- 238000011084 recovery Methods 0.000 description 4
- 238000005299 abrasion Methods 0.000 description 3
- 239000000567 combustion gas Substances 0.000 description 2
- 230000017525 heat dissipation Effects 0.000 description 2
- 238000003825 pressing Methods 0.000 description 2
- 238000010521 absorption reaction Methods 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 238000002485 combustion reaction Methods 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 239000004744 fabric Substances 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
- 239000012812 sealant material Substances 0.000 description 1
- 230000035939 shock Effects 0.000 description 1
Images
Classifications
-
- 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
- F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
- F01D25/24—Casings; Casing parts, e.g. diaphragms, casing fastenings
-
- 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
- F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
- F01D25/24—Casings; Casing parts, e.g. diaphragms, casing fastenings
- F01D25/246—Fastening of diaphragms or stator-rings
-
- 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
-
- 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
- F01D11/005—Sealing means between non relatively rotating elements
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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
- F01D11/14—Adjusting or regulating tip-clearance, i.e. distance between rotor-blade tips and stator casing
- F01D11/20—Actively adjusting tip-clearance
- F01D11/24—Actively adjusting tip-clearance by selectively cooling-heating stator or rotor components
Definitions
- the invention relates to a heat recovery segment for local separation of a flow channel within a flow rotating machine, in particular a gas turbine plant, opposite to a stator radially surrounding the stator housing, with two axially opposite joining contours, which are each engageable with two along the flow channel axially adjacent components, the to the joining contours each provide a gegenkonturrATOR receiving contour, of which at least one receiving contour has an axial play, along which the joined joining contour is axially displaceable, wherein between the axially displaceable joining contour and the receiving contour at least one sealing means is provided.
- Heat accumulation segments of the type described above are part of axial flow-through turbomachines through which flow for compression or targeted expansion gaseous working media and due to their high process temperatures, the thermally heavily loaded with the hot working fluids system components.
- axially one behind the other arranged blades and vanes are acted upon directly with the resulting hot combustion gases in the combustion chamber.
- heat accumulation segments which are provided on the stator side between each two axially adjacent rows of vanes, for a gas-tight as possible bridge-like seal between two axially adjacent arranged guide blade rows.
- Correspondingly designed heat accumulation segments can also be provided along the rotor unit, which are each mounted on the rotor side between two axially adjacent rotor blade rows in order to protect co-rotating rotor components from too high a heat input.
- FIG. 1 is a schematic longitudinal section shown by a gas turbine stage, in the flow channel radially projecting from the outside with a stator housing S, the special design further has no further significance, associated guide vanes 1.
- a blade 2 which is spaced radially from the end face against a heat shield segment 3, which includes the smallest possible clearance gap 4 with the vane 2 to leakage losses with respect to flow components of the hot gas flow through avoid the intermediate gap 4 as possible.
- the blade tip Sealing structures 5, which are arranged freely rotating relative to so-called abrasion elements 6.
- the heat staging segment 3 sees two axially opposite one another Join contours 7, 8, which open axially into corresponding receiving contours 9, 10 within the Leitschaufelfdorf.
- the receiving contour 9 corresponds to a precisely matched to the joining contour 7 gegenkonturriert running groove-shaped recess which is incorporated in the foot region of the guide vane 1.
- the axially opposite joining contour 8 of the heat shield segment 3 is likewise inserted into a receiving contour 10 which is counter-contoured corresponding to the outer contour of the joining contour 8 and is inserted in the foot region of the guide blade 1 '.
- the receiving contour 10 has an axial play 11, so that the joining contour 8 is axially slidably mounted with a corresponding operational thermal expansion of the heat shield segment 3.
- sealing means 12, 13 are provided between the joining contours 7, 8 and the associated receiving contours 9, 10.
- the sealing means 12, 13 are each located in a groove-shaped recess 14 within the joining contours 7, 8 (see also detailed representation according to FIG Fig. 2b the joining region between the joining contour 8 and the receiving contour 10).
- the sealing means 12, 13 are preferably made of an elastic sealing material in the form of a round rod, partially project beyond the radially outer boundary surface 16 and nestle flush, at least along a joint line to the surface portion 17 of the receiving contour 10 at.
- the sealing effect of the sealing means 12, 13 can be avoided on the one hand, that hot gases from the flow channel in the radially remote from the flow channel areas penetrate to the heat shield segment 3, also prevents stator-fed cooling air L can pass through appropriate leakage points in the flow channel.
- the clearance 11 provided in the recess 11 serves for a thermally induced material expansion along the heat shield segment 3, whereby the joining contour 8 together with the sealing means 12 provided in it is displaced to a right position shown in the illustration. If, on the other hand, the gas turbine stage is switched off and the individual components cool down, the joining contour 8, together with the sealing means 12 provided in it, returns to the original starting position.
- sealing means 12 is subject by the thermally induced relative movements between the receiving contour 8 and the surface region 17 Materialabrieberscheinungen that leads to a wear-related reduction of the sealing function of the sealant when exceeding a maximum allowable limit, so that cooling air L through the adjusting or existing intermediate gaps between the joining contour 8 and the receiving contour 10 can escape.
- This not only leads to a considerable loss of cooling air, whereby the cooling effect is drastically reduced, however, there is a risk that hot gases may also enter areas that are located facing away from the flow channel to the heat shield segment 3.
- sealing means are used, which consist of a fabric material which can be thinned at high mechanical rubbing stress, whereby the sealing effect of the sealant decreases with increasing operating time.
- the US 5423659 alternatively discloses a heat shield assembly in which by flexible, so-called "W seals", an axial gap between the stator and heat shield segment is sealed. By the axial direction of the spring force of the seal, the heat dissipation segment is held in position.
- the invention is based on the object, a heat dissipation segment for local separation of a flow channel within a flow rotating machine, in particular a gas turbine plant, opposite to a radially surrounding the flow channel stator housing, with two axially opposite joining contours, the each in engagement with two along the flow channel axially adjacent components can be brought, which provide for the joining contours each have a gegenkonturrATOR receiving contour, of which at least one receiving contour has an axial play along which the joining contour is axially slidably mounted, wherein between the axially displaceable Joining contour and the receiving contour at least one sealing means is provided to form such that the sealant should experience no or significantly lower Abriebeigenschaften caused by the thermally induced material expansion and shrinkage caused relative movements between the joining contour and the receiving contour.
- a heat damper arrangement according to the features of the preamble of claim 1 is designed such that the sealing means is movably mounted within the receiving contour or the joining contour such that the sealing means can be deflected against a surface region of the receiving contour or the joining contour.
- the sealing means which is preferably made of a metallic material, preferably of an incompressible material, as it were introduced in the prior art within a recess along the receiving contour or joining contour, but additionally subjected to a force, Preferably spring-loaded against a surface area of the receiving contour or joining contour to deflect or press.
- a force Preferably spring-loaded against a surface area of the receiving contour or joining contour to deflect or press.
- the following considerations provide for integrating the sealing means in the joining contour of the heat spreader segment, so that the sealing means is pressed against a surface area of the receiving contour by a spring force.
- FIG. 1a shows a partial view through a longitudinal section of a heat shield segment 3 in the region of the joining contour 8, which opens into a corresponding groove-shaped receiving contour 10 of an axially adjacent foot of a guide vane 1 '.
- the axial depth of the receiving contour 10 is dimensioned so to speak to the prior art described above such that in thermally induced material expansion of the heat shield segment 3, the joining contour 8 along the axially oriented game 11 is slidably mounted.
- the joining contour 8 consequently carries out a translational movement indicated in the direction of the arrow E.
- the joining contour 8 has a radially outer joining surface 16, in which a groove-shaped recess 14 is incorporated.
- the depth of the groove-shaped recess 14, measured from the joining surface 16 corresponds at least to the maximum radial extent of the sealing means 12, whose shape is adapted to the inner contour of the groove-shaped recess 14, so that the sealing means 14 can be completely inserted into the recess 14.
- a spring element 18 is provided within the groove-shaped recess 14, which is introduced between the groove bottom of the recess 14 and the sealing means 12, so that the spring element 18 is able to drive the sealing means 12 radially upwards.
- the sealant 12 is in the in FIG. 1b Perspective manner shown rod-shaped and preferably made of an incompressible metallic material, which has substantially no Abriebeigenschaften.
- the sealing means 12 has a rectangular design in the middle Projection 19, which engages in a corresponding rectangular recess 20 in the inserted state within the groove-shaped recess 14.
- the sealing means 12 is forced radially linearly by the projection 19, so that slippage of the sealing means 12 in the circumferential direction along the groove-shaped recess 14 is avoided.
- a swung formed spring element 18 is introduced, which is capable of pressing the sealing means 12 radially upward Federkraftbeetzschlagt.
- the curved spring element section 18 'facing the groove bottom opens into a recess (not shown) inserted correspondingly in the groove bottom.
- the rectangular shaped recess 20 axially opposite boundary wall 21 within the groove-shaped recess 14 is made of a sealing material and is able to produce in this way in a fluid-tight contact with the sealant 12.
- FIG. 1 a is the inserted state of the joining contour 8 shown within the receiving contour 10, wherein the spring element 18, the sealant 12 radially outwardly against a surface portion 17 of the receiving contour 10 presses and thus the heat shield segment 3 fluid-tight against the receiving contour 10th within the foot of the vane 1 'presses.
- the radially lower side edge of the sealant 12 is formed inclined, so that the spring element 18, the sealant 12 also axially against the rear Limiting surface 21 can press fluid-tight.
- the side edge of the sealant facing the surface area 17 is contoured to the surface area 17.
- the sealing system made in accordance with the invention can not avoid the axial longitudinal movement of the thermal damper segment 3 due to the thermal material expansion or shrinkage, the material abrasion completely disappears with a suitable choice of the sealant material, especially since the sealant 12 is made of an incompressible, wear-free, preferably metallic material is selected, which ensures a fluid-tight seal due to the spring-loaded pressure.
- cooling air L flowing in under high pressure can exert a high contact pressure on the axially directed surface 23 of the projection 19 within the cooling volume V enclosed by the thermal damper segment 3, so that the sealing means is pressed in the axial direction in addition to the spring force component against the sealing side 21 consisting of sealing material ,
- spring element 18 In addition to the in the FIGS. 1a and b illustrated concrete embodiment of the spring element 18 are also other spring element designs conceivable, such as a plurality of individual spiral spring elements, helically shaped or coiled spring elements and suitably shaped flat springs.
- FIG. 1 a and b illustrated heat shield segment in a ring-like array the entire peripheral area between two adjacent limited to each other Leitschaufelschschsch.
- two heat accumulation segments arranged adjacent to one another in the circumferential direction engage via a common strip band seal 24, by means of which a possible loss of cooling air along two circumferentially adjacent heat accumulation segments can be avoided.
- the spring-pressure of the sealant ensures at any time a sealing of the joining area with respect to its radially upper and lower boundary surfaces, especially since the radially upper sealing means 12 by the force exerted on the joint counterforce and the radially lower boundary surface of the joining region against the boundary surface of the receiving contour 10 can press fluid-tight. If the sealing means be provided in the region of the boundary surface of the receiving contour 10, the same applies accordingly.
- the spring element 18 Due to the spring-loaded pressing action of the sealing means 12 against the surface region 16 of the receiving contour 10, the spring element 18 carries due its inherent elasticity to a certain capacity at impact or vibration absorption, so that occurring mechanical shocks within the joint area can be absorbed by the spring element 18 and thus not too strong mechanical stress on the joint area.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Turbine Rotor Nozzle Sealing (AREA)
- Gasket Seals (AREA)
- Heating, Cooling, Or Curing Plastics Or The Like In General (AREA)
- Lining Or Joining Of Plastics Or The Like (AREA)
Abstract
Description
Die Erfindung bezieht sich auf ein Wärmestausegment zum lokalen Abtrennen eines Strömungskanals innerhalb einer Strömungsrotationsmaschine, insbesondere einer Gasturbinenanlage, gegenüber eines den Strömungskanal radial umgebenden Statorgehäuses, mit zwei axial gegenüberliegenden Fügekonturen, die jeweils in Eingriff mit zwei längs des Strömungskanals axial benachbarten Komponenten bringbar sind, die zu den Fügekonturen jeweils eine gegenkonturrierte Aufnahmekontur vorsehen, von denen wenigstens eine Aufnahmekontur ein axiales Spiel aufweist, längs dem die darin gefügte Fügekontur axial verschiebbar gelagert ist, wobei zwischen der axial verschiebbaren Fügekontur und der Aufnahmekontur wenigstens ein Dichtmittel vorgesehen ist.The invention relates to a heat recovery segment for local separation of a flow channel within a flow rotating machine, in particular a gas turbine plant, opposite to a stator radially surrounding the stator housing, with two axially opposite joining contours, which are each engageable with two along the flow channel axially adjacent components, the to the joining contours each provide a gegenkonturrierte receiving contour, of which at least one receiving contour has an axial play, along which the joined joining contour is axially displaceable, wherein between the axially displaceable joining contour and the receiving contour at least one sealing means is provided.
Wärmestausegmente der vorstehend bezeichneten Gattung sind Teil axial durchströmter Strömungsmaschinen, durch die zur Kompression oder gezielten Expansion gasförmige Arbeitsmedien hindurchströmen und aufgrund ihrer hohen Prozesstemperaturen die mit dem heissen Arbeitsmedien unmittelbar beaufschlagten Anlagenkomponenten thermisch stark belasten. Insbesondere in den Turbinenstufen von Gasturbinenanlagen werden die in Lauf- und Leitschaufelreihen axial hintereinander angeordnete Lauf- und Leitschaufeln mit den in der Brennkammer entstehenden heissen Verbrennungsgasen unmittelbar beaufschlagt. Um zu verhindern, dass die den Strömungskanal durchströmenden Heissgase Bereiche innerhalb der Strömungsrotationsmaschine thermisch belasten, die in den Strömungskanal abgewandten Statorbereichen vorgesehen sind, sorgen sogenannte Wärmestausegmente, die statorseitig zwischen jeweils zwei axial benachbart zueinander angeordneten Leitschaufelreihen vorgesehen sind, für eine möglichst Gasdichte brückenartige Abdichtung zwischen zwei axial benachbart angeordneten Leitschaufelreihen. Entsprechend konzipierte Wärmestausegmente können auch längs der Rotoreinheit vorgesehen werden, die jeweils zwischen zwei axial benachbarte Laufschaufelreihen rotorseitig angebracht sind, um mitrotierende Rotorkomponenten vor einem zu hohen Wärmeeintrag zu schützen.Heat accumulation segments of the type described above are part of axial flow-through turbomachines through which flow for compression or targeted expansion gaseous working media and due to their high process temperatures, the thermally heavily loaded with the hot working fluids system components. In particular, in the turbine stages of gas turbine plants in the rows of blades and vanes axially one behind the other arranged blades and vanes are acted upon directly with the resulting hot combustion gases in the combustion chamber. To prevent the hot gases flowing through the flow channel areas load thermally within the flow rotating machine, which are provided in the flow channel remote stator, so-called heat accumulation segments which are provided on the stator side between each two axially adjacent rows of vanes, for a gas-tight as possible bridge-like seal between two axially adjacent arranged guide blade rows. Correspondingly designed heat accumulation segments can also be provided along the rotor unit, which are each mounted on the rotor side between two axially adjacent rotor blade rows in order to protect co-rotating rotor components from too high a heat input.
Gleichwohl sich die nachstehenden Ausführungen ausschliesslich auf Wärmestausegmente beziehen, die zwischen zwei Leitschaufelreihen angeordnet sind und insofern das statorseitige Gehäuse und die damit verbundenen Komponenten gegenüber dem hitzebelasteten Strömungskanal abzutrennen und entsprechend zu schützen vermögen, ist es auch denkbar, die nachfolgenden Massnahmen an einem Wärmestausegment vorzusehen, das dem Schutz mitrotierender Rotorkomponenten dient und zwischen zwei axial benachbart zueinander angeordneten Laufschaufelreihen einbringbar ist.Although the following statements relate exclusively to heat accumulator segments, which are arranged between two rows of stator blades and insofar able to separate the stator housing and the components associated therewith against the heat-stressed flow channel and protect accordingly, it is also conceivable to provide the following measures on a heat shield segment, serves the protection co-rotating rotor components and between two axially adjacent to each other arranged rows of blades can be introduced.
In
Zwischen zwei in Leitschaufelreihen benachbart angeordnete Leitschaufeln 1 ragt mit einer nicht dargestellten Rotoreinheit verbunden, eine Laufschaufel 2, die radial stirnseitig gegenüber einem Wärmestausegment 3 beabstandet ist, das mit der Leitschaufel 2 einen möglichst kleinen freien Zwischenspalt 4 einschliesst, um Leckageverluste hinsichtlich Strömungsanteile des Heissgasstromes durch den Zwischenspalt 4 möglichst zu vermeiden. Hierzu weist die Laufschaufelspitze Dichtstrukturen 5 auf, die gegenüber sogenannten Abriebelementen 6 frei rotierend angeordnet sind.Between two adjacent guide vanes arranged in rows of
Um zu vermeiden, dass heisse Verbrennungsgase im Bereich des Wärmestausegmentes 3, das den Zwischenraum zwischen zwei axial zueinander benachbart angeordneten Leitschaufeln 1, 1' brückenartig überspannt, in den vom Strömungskanal radial abgewandten Bereich des Wärmestausegmentes 3 gelangen können, sieht das Wärmestausegment 3 zwei axial gegenüberliegende Fügekonturen 7, 8 vor, die in entsprechende Aufnahmekonturen 9, 10 innerhalb der Leitschaufelfüsse axialwärts einmünden.In order to avoid that hot combustion gases in the region of the
Die Aufnahmekontur 9 entspricht einer passgenau an die Fügekontur 7 gegenkonturriert ausgeführten nutförmigen Ausnehmung, die im Fussbereich der Leitschaufel 1 eingearbeitet ist. Die axial gegenüberliegende Fügekontur 8 des Wärmestausegmentes 3 ist gleichfalls in eine entsprechend zur Aussenkontur der Fügekontur 8 gegenkonturriert ausgeführte Aufnahmekontur 10, die im Fussbereich der Leitschaufel 1' eingebracht ist, eingefügt. Die Aufnahmekontur 10 weist jedoch ein axiales Spiel 11 auf, so dass die Fügekontur 8 bei entsprechender betriebsbedingter, thermischer Ausdehnung des Wärmestausegmentes 3 axial gleitend gelagert ist.The
Zur fluiddichten Abdichtung des Wärmestausegmentes 3 gegenüber den jeweiligen Aufnahmekonturen 9, 10 in den Fussbereichen der Leitschaufeln 1, 1' sind Dichtmittel 12, 13 zwischen den Fügekonturen 7, 8 und den zugehörigen Aufnahmekonturen 9, 10 vorgesehen. Die Dichtmittel 12, 13 befinden sich jeweils in einer nutförmigen Ausnehmung 14 innerhalb der Fügekonturen 7, 8 (siehe auch Detailldarstellung gem
Durch die Dichtwirkung der Dichtmittel 12, 13 kann einerseits vermieden werden, dass Heissgase aus dem Strömungskanal in die radial dem Strömungskanal abgewandten Bereiche zum Wärmestausegment 3 eindringen, gleichfalls wird verhindert, dass statorseitig eingespeiste Kühlluft L durch entsprechende Leckagestellen in den Strömungskanal gelangen können. Wie bereits eingangs erläutert, dient das in der Ausnehmung 10 vorgesehene Spiel 11 für eine thermisch bedingte Materialausdehnung längs des Wärmestausegmentes 3, wodurch die Fügekontur 8 samt dem in ihr vorgesehenen Dichtmittel 12 eine in der Darstellung ersichtliche rechte Position verschoben wird. Wird hingegen die Gasturbinenstufe ausgeschaltet und die einzelnen Komponenten kühlen sich ab, so kehrt die Fügekontur 8 samt dem in ihr vorgesehenen Dichtmittel 12 in die ursprünglich Ausgangslage zurück. Es liegt auf der Hand, dass das Dichtmittel 12 durch die thermisch bedingten Relativbewegungen zwischen der Aufnahmekontur 8 und dem Oberflächenbereich 17 Materialabrieberscheinungen unterliegt, die bei Überschreiten einer maximal zulässigen Toleranzgrenze zu einer verschleissbedingten Verminderung der Abdichtfunktion des Dichtmittels führt, so dass Kühlluft L durch die sich einstellenden oder bereits vorhandenen Zwischenspalte zwischen der Fügekontur 8 und der Aufnahmekontur 10 entweichen kann. Dies führt nicht nur zu einem erheblichen Kühlluftverlust, wodurch die Kühlwirkung drastisch verringert wird, gleichwohl besteht die Gefahr, dass Heissgase auch in Bereiche eintreten können, die den Strömungskanal bezogen zum Wärmestausegment 3 abgewandt gelegen sind. Hinzu kommt, dass für gewöhnlich Dichtmittel eingesetzt werden, die aus einem Gewebematerial bestehen, das bei zu hoher mechanischer Reibebeanspruchung ausgedünnt werden kann, wodurch die Dichtwirkung des Dichtmittels mit zunehmender Betriebszeit abnimmt.
Die
The
Der Erfindung liegt die Aufgabe zugrunde, ein Wärmestausegment zum lokalen Abtrennen eines Strömungskanals innerhalb einer Strömungsrotationsmaschine, insbesondere einer Gasturbinenanlage, gegenüber eines den Strömungskanal radial umgebenden Statorgehäuses, mit zwei axial gegenüberliegenden Fügekonturen, die jeweils in Eingriff mit zwei längs des Strömungskanals axial benachbarten Komponenten bringbar sind, die zu den Fügekonturen jeweils eine gegenkonturrierte Aufnahmekontur vorsehen, von denen wenigstens eine Aufnahmekontur ein axiales Spiel aufweist, längs dem die darin gefügte Fügekontur axial verschiebbar gelagert ist, wobei zwischen der axial verschiebbaren Fügekontur und der Aufnahmekontur wenigstens ein Dichtmittel vorgesehen ist, derart auszubilden, dass das Dichtmittel keinerlei oder erheblich geringere Abriebeigenschaften bedingt durch die thermisch verursachten Materialausdehnungen und Schrumpfungen hervorgerufenen Relativbewegungen zwischen der Fügekontur und der Aufnahmekontur erfahren soll. Insbesondere gilt es Vorkehrungen zu treffen, die den Verschleiss des Dichtmittels erheblich reduzieren, obgleich die hierfür zu treffenden Massnahme konstruktiv möglichst einfach auszuführen sind. Schliesslich gilt es, die Wartungszyklen der wartungsunterworfenen Komponenten am Wärmestausegment, so insbesondere die Dichtmittel betreffend, entscheidend zu verlängern und ihre Betriebssicherheit zu verbessern.The invention is based on the object, a heat dissipation segment for local separation of a flow channel within a flow rotating machine, in particular a gas turbine plant, opposite to a radially surrounding the flow channel stator housing, with two axially opposite joining contours, the each in engagement with two along the flow channel axially adjacent components can be brought, which provide for the joining contours each have a gegenkonturrierte receiving contour, of which at least one receiving contour has an axial play along which the joining contour is axially slidably mounted, wherein between the axially displaceable Joining contour and the receiving contour at least one sealing means is provided to form such that the sealant should experience no or significantly lower Abriebeigenschaften caused by the thermally induced material expansion and shrinkage caused relative movements between the joining contour and the receiving contour. In particular, it is necessary to take precautions which considerably reduce the wear of the sealant, although the measures to be taken for this purpose should be constructively as simple as possible. Finally, it is essential to extend the maintenance cycles of the maintenance-subject components on the heat recovery segment, in particular the sealant, to significantly improve their reliability.
Die Lösung der der Erfindung zugrunde liegenden Aufgabe ist im Anspruch 1 angegeben. Den Erfindungsgedanken vorteilhaft ausbildende Merkmale sind Gegenstand der Unteransprüche und insbesondere der Beschreibung unter Bezugnahme auf das weitere Ausführungsbeispiel zu entnehmen.The solution of the problem underlying the invention is specified in
Lösungsgemäss ist eine Wärmestausegmentanordnung gemäss den Merkmalen des Oberbegriffes des Anspruches 1 derart ausgebildet, dass das Dichtmittel innerhalb der Aufnahmekontur oder der Fügekontur derart beweglich gelagert ist, dass das Dichtmittel gegen einen Oberflächenbereich der Aufnahmekontur oder der Fügekontur kraftbeaufschlagt auslenkbar ist.According to the solution, a heat damper arrangement according to the features of the preamble of
Die lösungsgemässe Idee sieht vor, das Dichtmittel, das vorzugsweise aus einem metallischen Material, vorzugsweise aus einem inkompressiblen Material besteht, gleichsam wie beim Stand der Technik innerhalb einer Ausnehmung längs der Aufnahmekontur oder Fügekontur einzubringen, jedoch zusätzlich kraftbeaufschlagt, vorzugsweise federkraftbeaufschlagt gegen einen Oberflächenbereich der Aufnahmekontur bzw. Fügekontur auszulenken bzw. zu pressen. Die folgenden Überlegungen sehen vor, das Dichtmittel in die Fügekontur des Wärmestausegmentes zu integrieren, so dass das Dichtmittel federkraftbeaufschlagt gegen einen Oberflächenbereich der Aufnahmekontur gedrückt wird. Gleichfalls ist es jedoch auch möglich, das Dichtmittel in einer entsprechenden innerhalb der Aufnahmekontur vorgesehenen Ausnehmung zu integrieren, so dass das Dichtmittel gegen einen Oberflächenbereich der Fügekontur gepresst wird. Die Wahl der Anbringung des Dichtmittels sei den jeweiligen konstruktiven Gegebenheiten der Fügeverbindung zwischen dem Wärmestausegment und der sich axialwärts anschliessenden Komponente der Gasturbinenanlage überlassen. Ohne Einschränkung auf den allgemeinen Erfindungsgedanken soll im Weiteren die erfindungsgemässe Dichtmittelausbildung als integraler Bestandteil der Fügekontur des Wärmestausegmentes beschrieben werden. In diesem Zusammenhang wird auf das in den Figuren beschriebene Ausführungsbeispiel Bezug genommen.The solution according to the invention provides that the sealing means, which is preferably made of a metallic material, preferably of an incompressible material, as it were introduced in the prior art within a recess along the receiving contour or joining contour, but additionally subjected to a force, Preferably spring-loaded against a surface area of the receiving contour or joining contour to deflect or press. The following considerations provide for integrating the sealing means in the joining contour of the heat spreader segment, so that the sealing means is pressed against a surface area of the receiving contour by a spring force. Likewise, however, it is also possible to integrate the sealing means in a corresponding recess provided within the receiving contour, so that the sealing means is pressed against a surface region of the joining contour. The choice of the attachment of the sealant is the respective structural conditions of the joint connection between the heat shield segment and the axialwärts subsequent component of the gas turbine plant left. Without restricting to the general idea of the invention, the sealant formation according to the invention will be described below as an integral part of the joining contour of the heat recovery segment. In this context, reference is made to the embodiment described in the figures.
Die Erfindung wird nachstehend ohne Beschränkung des allgemeinen Erfindungsgedankens anhand von Ausführungsbeispielen unter Bezugnahme auf die Zeichnungen exemplarisch beschrieben. Es zeigen:
- Fig. 1 a
- schematisierte Teil-Längsschnittdarstellung durch einen Fügebereich zwischen einem Wärmestausegment und einer axialwärts angren- zenden Leitschaufel,
- Fig. 1 b
- perspektivische Darstellung des Dichtelementes mit Federelement in senkrechter Projektion über einer Ausnehmung innerhalb der Fügekontur,
- Fig. 2a, b
- Längsschnittteildarstellung durch ein Wärmestausegment mit axial angrenzenden Leitschaufeln sowie Detailldarstellung hierzu gemäss Stand der Technik.
- Fig. 1 a
- Schematic partial longitudinal section through a joining region between a heat shield segment and an axially adjacent guide vane,
- Fig. 1 b
- perspective view of the sealing element with spring element in a vertical projection over a recess within the joining contour,
- Fig. 2a, b
- Longitudinal section of a heat recovery segment with axially adjacent vanes and a detailed illustration of this according to the prior art.
Das Dichtmittel 12 ist in der in
Die der rechteckförmig ausgebildeten Aussparung 20 axial gegenüberliegende Begrenzungswand 21 innerhalb der nutförmigen Ausnehmung 14 ist aus einem Dichtmaterial gefertigt und vermag auf diese Weise in einen fluiddichten Kontakt mit dem Dichtmittel 12 herzustellen.The rectangular shaped
In
Um die Dichtwirkung des Dichtmittels 12 gegen den Oberflächenbereich 17 der Aufnahmekontur 10 zu verbessern, ist die dem Oberflächenbereich 17 zugewandte Seitenkante des Dichtmittels konturgetreu an den Oberflächenbereich 17 ausgebildet.In order to improve the sealing effect of the
Zwar vermag das löungsgemäss ausgebildete Dichtsystem die axiale Längsbewegungen des Wärmestausegmentes 3 bedingt durch die thermische Materialausdehnung bzw. -schrumpfung nicht zu vermeiden, doch tritt der Materialabrieb bei geeigneter Wahl des Dichtmittelmaterials vollständig in den Hintergrund, zumal das Dichtmittel 12 aus einem inkompressiblen, verschleissfreien, vorzugsweise metallischen Material gewählt ist, das aufgrund der federkraftbeaufschlagten Pressung für eine fluiddichte Abdichtung sorgt.Although the sealing system made in accordance with the invention can not avoid the axial longitudinal movement of the
Ebenso denkbar ist es die federkraftbeaufschlagte Dichtmittelanordnung anstelle der in
Ferner vermag die unter hohem Druck einströmende Kühlluft L innerhalb des vom Wärmestausegment 3 eingeschlossenen Kühlvolumens V auf die axial gerichtete Fläche 23 der Auskragung 19 einen hohen Anpressdruck auszuüben, so dass das Dichtmittel in axialer Richtung zusätzlich zur Federkraftkomponente gegen die aus Dichtmaterial bestehende Begrenzungsseite 21 gepresst wird.Furthermore, the cooling air L flowing in under high pressure can exert a high contact pressure on the axially directed
Neben der in den
Aus Gründen der Vollständigkeit halber wird zudem darauf hingewiesen, dass das in
Die lösungsgemässe Dichtungsanordnung ist somit mit folgenden Vorteilen verbunden:
- Die Dichtheit des Kühlluftvolumens, das durch das Wärmestausegment vom Strömungskanal abgetrennt wird, wird aufgrund des abnutzungsfreien Dichtmittels erheblich verbessert, zumal die Dichtwirkung trotz thermischer Ausdehnungs- und Schrumpfungserscheinungen durch die federkraftbeaufschlagte Anpressung des Dichtmittels an den jeweiligen dem Dichtmittel gegenüberliegenden Oberflächenbereich gewährleistet wird.
- The tightness of the cooling air volume, which is separated by the heat discharge segment from the flow channel is significantly improved due to the wear-free sealant, especially since the sealing effect is guaranteed despite thermal expansion and shrinkage phenomena by the spring-loaded contact pressure of the sealant to the respective surface area opposite the sealant.
Unabhängig von vorgegebenen Toleranzmassen hinsichtlich der Ausführung der Aufnahmekontur bzw. der Fügekontur stellt die federkraftbedingte Anpressung des Dichtmittels jederzeit eine Abdichtung des Fügebereiches bezüglich seiner radial oben und unten liegenden Begrenzungsflächen sicher, zumal das radial oben liegende Dichtmittel 12 durch die auf den Fügebereich ausgeübte Gegenkraft auch die radial unten liegende Begrenzungsfläche des Fügebereiches gegen die Begrenzungsfläche der Aufnahmekontur 10 fluiddicht zu pressen vermag. Sollte das Dichtmittel im Bereich der Begrenzungsfläche der Aufnahmekontur 10 vorgesehen sein, gilt entsprechend das gleiche.Regardless of predetermined tolerances with respect to the execution of the receiving contour or the joining contour, the spring-pressure of the sealant ensures at any time a sealing of the joining area with respect to its radially upper and lower boundary surfaces, especially since the radially upper sealing means 12 by the force exerted on the joint counterforce and the radially lower boundary surface of the joining region against the boundary surface of the receiving
Durch die federkraftbeaufschlagte Anpresswirkung des Dichtmittels 12 gegen den Oberflächenbereich 16 der Aufnahmekontur 10 trägt das Federelement 18 aufgrund seiner Eigenelastizität zu einem gewissen Vermögen an Stoß- oder Vibrationsabsorption bei, so dass auftretende mechanische Erschütterungen innerhalb des Fügebereiches durch das Federelement 18 aufgefangen werden können und somit den Fügebereich nicht zu stark mechanisch beanspruchen.Due to the spring-loaded pressing action of the sealing means 12 against the
- 1, 1'1, 1 '
- Leitschaufelvane
- 22
- Laufschaufelblade
- 33
- WärmestausegmentHeat shield
- 44
- Zwischenspaltintermediate gap
- 55
- Rippenribs
- 66
- Abriebelementeabrasion elements
- 7, 87, 8
- Fügekonturjoining contour
- 9,109.10
- AufnahmekonturUp Silhouette
- 1111
- axiales Spielaxial play
- 12, 1312, 13
- Dichtmittelsealant
- 1414
- nutförmige Ausnehmunggroove-shaped recess
- 1515
- n.n.N. N.
- 1616
- Fügeflächejoining surface
- 1717
- Oberflächenbereichsurface area
- 1818
- Federelementspring element
- 18'18 '
- Teilbereich des FederelementesPart of the spring element
- 1919
- Auskragungprojection
- 2020
- Aussparungrecess
- 2121
- Begrenzungsflächeboundary surface
- 2323
- radiale Seitenfläche der Auskragungradial side surface of the projection
Claims (6)
- Arrangement containing a heat shield and at least one sealing means (12) for the local separation of a flow channel within a turbine engine, in particular gas turbine plant, with respect to a stator housing radially surrounding the flow channel, with two axially opposite joining contours (7, 8) which can be brought in each case into engagement with two components (1, 1') which are axially adjacent along the flow channel and which in each case provide a countercontoured reception contour (9, 10) for the joining contours (7, 8), of which reception contours at least one reception contour (10) has an axial clearance (11), along which the joining contour (8) joined in it is mounted axially displaceably, the at least one sealing means (12) being provided between the axially displaceable joining contour (8) and the reception contour (10) and the sealing means (12) being mounted movably within the reception contour (10) or the joining contour (8) in such a way that the sealing means (12) can be deflected against a surface region (17) of the reception contour (10) or of the joining contour (8), characterized in that the reception contour (10) or the joining contour (8) has a joining face (16) in which is introduced for the sealing means (12) a recess (14) out of which the sealing means (12) can be deflected so as to project partially beyond the joining face (16) and at least one spring element (18), which deflects the sealing means (12) by the action of spring force, is provided in the recess (14).
- Arrangement containing a heat shield according to Claim 1, characterized in that the sealing means (12) consists of a metallic material.
- Arrangement containing a heat shield according to Claim 1 or 2, characterized in that the sealing means (12) is a solid body with incompressible properties.
- Arrangement containing a heat shield according to one of Claims 1 to 3, characterized in that the sealing means (12) is of bar-shaped design and has a local protrusion (19) along its extent, and in that a recess (20), which is adapted to the protrusion (19) and along which the protrusion (19) is guided in the radial direction, is provided in the recess (14).
- Arrangement containing a heat shield according to one of Claims 1 to 4, characterized in that the spring element (18) is designed as a curved bar spring and is held in the longitudinal direction with respect to the recess (14).
- Arrangement containing a heat shield according to one of Claims 2 to 5, characterized in that the recess (14) has a radially oriented boundary face (21) which consists of a sealing material, in that the sealing means (12) has a radially upper side edge which is adapted to the surface region (17) against which the sealing means (12) can be pressed by the action of force, and in that the sealing means (12) has a radially lower sloped side edge, against which the spring element (18) presses, and the inclination of the slope is selected in such a way that the sealing means (12) can be pressed both against the surface region (17) and against the boundary face (21) consisting of the sealing material.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
SI200631029T SI1861584T1 (en) | 2005-03-24 | 2006-03-21 | Heat accumulation segment for sealing a flow channel of a turbine engine |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102005013798A DE102005013798A1 (en) | 2005-03-24 | 2005-03-24 | Heat release segment for sealing a flow channel of a flow rotary machine |
PCT/EP2006/060903 WO2006100235A1 (en) | 2005-03-24 | 2006-03-21 | Heat accumulation segment for sealing a flow channel of a turbine engine |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1861584A1 EP1861584A1 (en) | 2007-12-05 |
EP1861584B1 true EP1861584B1 (en) | 2011-03-09 |
Family
ID=36593051
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP06725191A Not-in-force EP1861584B1 (en) | 2005-03-24 | 2006-03-21 | Heat accumulation segment for sealing a flow channel of a turbine engine |
Country Status (10)
Country | Link |
---|---|
US (1) | US7665957B2 (en) |
EP (1) | EP1861584B1 (en) |
KR (1) | KR101287408B1 (en) |
AT (1) | ATE501341T1 (en) |
BR (1) | BRPI0609723A2 (en) |
CA (1) | CA2602458C (en) |
DE (2) | DE102005013798A1 (en) |
MX (1) | MX2007011589A (en) |
SI (1) | SI1861584T1 (en) |
WO (1) | WO2006100235A1 (en) |
Families Citing this family (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CA2690705C (en) * | 2007-06-28 | 2015-08-04 | Alstom Technology Ltd | Heat shield segment for a stator of a gas turbine engine |
DE102007031711A1 (en) | 2007-07-06 | 2009-01-08 | Rolls-Royce Deutschland Ltd & Co Kg | Housing shroud segment suspension |
EP2098688A1 (en) * | 2008-03-07 | 2009-09-09 | Siemens Aktiengesellschaft | Gas turbine |
FR2954400B1 (en) * | 2009-12-18 | 2012-03-09 | Snecma | TURBINE STAGE IN A TURBOMACHINE |
CN104471197B (en) * | 2012-04-27 | 2016-05-11 | 通用电气公司 | Suspension bracket and the axially movable system and method for radome fairing inter-module in restriction turbine assembly |
US9771818B2 (en) | 2012-12-29 | 2017-09-26 | United Technologies Corporation | Seals for a circumferential stop ring in a turbine exhaust case |
US10458268B2 (en) * | 2016-04-13 | 2019-10-29 | Rolls-Royce North American Technologies Inc. | Turbine shroud with sealed box segments |
EP3412871B1 (en) | 2017-06-09 | 2021-04-28 | Ge Avio S.r.l. | Sealing arrangement for a turbine vane assembly |
US10858953B2 (en) * | 2017-09-01 | 2020-12-08 | Rolls-Royce Deutschland Ltd & Co Kg | Turbine casing heat shield in a gas turbine engine |
US11047248B2 (en) | 2018-06-19 | 2021-06-29 | General Electric Company | Curved seal for adjacent gas turbine components |
US11248705B2 (en) * | 2018-06-19 | 2022-02-15 | General Electric Company | Curved seal with relief cuts for adjacent gas turbine components |
CN110332023B (en) * | 2019-07-16 | 2021-12-28 | 中国航发沈阳发动机研究所 | End face sealing structure with cooling function |
Family Cites Families (19)
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US4576548A (en) * | 1984-01-17 | 1986-03-18 | Westinghouse Electric Corp. | Self-aligning static seal for gas turbine stator vanes |
US5188506A (en) * | 1991-08-28 | 1993-02-23 | General Electric Company | Apparatus and method for preventing leakage of cooling air in a shroud assembly of a gas turbine engine |
US5188507A (en) * | 1991-11-27 | 1993-02-23 | General Electric Company | Low-pressure turbine shroud |
US5333995A (en) * | 1993-08-09 | 1994-08-02 | General Electric Company | Wear shim for a turbine engine |
US5423659A (en) * | 1994-04-28 | 1995-06-13 | United Technologies Corporation | Shroud segment having a cut-back retaining hook |
DE4442157A1 (en) | 1994-11-26 | 1996-05-30 | Abb Management Ag | Method and device for influencing the radial clearance of the blades in compressors with axial flow |
US5901787A (en) * | 1995-06-09 | 1999-05-11 | Tuboscope (Uk) Ltd. | Metal sealing wireline plug |
US5609469A (en) * | 1995-11-22 | 1997-03-11 | United Technologies Corporation | Rotor assembly shroud |
US6315519B1 (en) * | 1998-09-28 | 2001-11-13 | General Electric Company | Turbine inner shroud and turbine assembly containing such inner shroud |
DE19938274A1 (en) | 1999-08-12 | 2001-02-15 | Asea Brown Boveri | Device and method for drawing the gap between the stator and rotor arrangement of a turbomachine |
FR2800797B1 (en) | 1999-11-10 | 2001-12-07 | Snecma | ASSEMBLY OF A RING BORDING A TURBINE TO THE TURBINE STRUCTURE |
US20030039542A1 (en) * | 2001-08-21 | 2003-02-27 | Cromer Robert Harold | Transition piece side sealing element and turbine assembly containing such seal |
US6514041B1 (en) * | 2001-09-12 | 2003-02-04 | Alstom (Switzerland) Ltd | Carrier for guide vane and heat shield segment |
JP2004036443A (en) * | 2002-07-02 | 2004-02-05 | Ishikawajima Harima Heavy Ind Co Ltd | Gas turbine shroud structure |
GB0308147D0 (en) * | 2003-04-09 | 2003-05-14 | Rolls Royce Plc | A seal |
EP1515003A1 (en) * | 2003-09-11 | 2005-03-16 | Siemens Aktiengesellschaft | Gas turbine and sealing means for a gas turbine |
FR2859762B1 (en) * | 2003-09-11 | 2006-01-06 | Snecma Moteurs | REALIZATION OF SEALING FOR CABIN TAKEN BY SEGMENT SEAL |
US7435049B2 (en) * | 2004-03-30 | 2008-10-14 | General Electric Company | Sealing device and method for turbomachinery |
US7207771B2 (en) * | 2004-10-15 | 2007-04-24 | Pratt & Whitney Canada Corp. | Turbine shroud segment seal |
-
2005
- 2005-03-24 DE DE102005013798A patent/DE102005013798A1/en not_active Withdrawn
-
2006
- 2006-03-21 AT AT06725191T patent/ATE501341T1/en active
- 2006-03-21 KR KR1020077021795A patent/KR101287408B1/en not_active IP Right Cessation
- 2006-03-21 BR BRPI0609723-5A patent/BRPI0609723A2/en not_active Application Discontinuation
- 2006-03-21 WO PCT/EP2006/060903 patent/WO2006100235A1/en not_active Application Discontinuation
- 2006-03-21 EP EP06725191A patent/EP1861584B1/en not_active Not-in-force
- 2006-03-21 CA CA2602458A patent/CA2602458C/en not_active Expired - Fee Related
- 2006-03-21 DE DE502006009054T patent/DE502006009054D1/en active Active
- 2006-03-21 SI SI200631029T patent/SI1861584T1/en unknown
- 2006-03-21 MX MX2007011589A patent/MX2007011589A/en active IP Right Grant
-
2007
- 2007-09-24 US US11/859,963 patent/US7665957B2/en active Active
Also Published As
Publication number | Publication date |
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MX2007011589A (en) | 2007-12-06 |
US20080260524A1 (en) | 2008-10-23 |
BRPI0609723A2 (en) | 2010-04-20 |
CA2602458C (en) | 2010-07-20 |
US7665957B2 (en) | 2010-02-23 |
EP1861584A1 (en) | 2007-12-05 |
ATE501341T1 (en) | 2011-03-15 |
DE502006009054D1 (en) | 2011-04-21 |
SI1861584T1 (en) | 2011-07-29 |
CA2602458A1 (en) | 2006-09-28 |
DE102005013798A1 (en) | 2006-09-28 |
KR101287408B1 (en) | 2013-07-19 |
KR20070115997A (en) | 2007-12-06 |
WO2006100235A1 (en) | 2006-09-28 |
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