EP1836442A1 - Ecran thermique - Google Patents

Ecran thermique

Info

Publication number
EP1836442A1
EP1836442A1 EP05821767A EP05821767A EP1836442A1 EP 1836442 A1 EP1836442 A1 EP 1836442A1 EP 05821767 A EP05821767 A EP 05821767A EP 05821767 A EP05821767 A EP 05821767A EP 1836442 A1 EP1836442 A1 EP 1836442A1
Authority
EP
European Patent Office
Prior art keywords
heat shield
shield element
cooling
wall
coolant
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.)
Withdrawn
Application number
EP05821767A
Other languages
German (de)
English (en)
Inventor
Heinrich Pütz
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Siemens AG
Original Assignee
Siemens AG
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Siemens AG filed Critical Siemens AG
Priority to EP05821767A priority Critical patent/EP1836442A1/fr
Publication of EP1836442A1 publication Critical patent/EP1836442A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23R—GENERATING COMBUSTION PRODUCTS OF HIGH PRESSURE OR HIGH VELOCITY, e.g. GAS-TURBINE COMBUSTION CHAMBERS
    • F23R3/00—Continuous combustion chambers using liquid or gaseous fuel
    • F23R3/005—Combined with pressure or heat exchangers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23R—GENERATING COMBUSTION PRODUCTS OF HIGH PRESSURE OR HIGH VELOCITY, e.g. GAS-TURBINE COMBUSTION CHAMBERS
    • F23R2900/00—Special features of, or arrangements for continuous combustion chambers; Combustion processes therefor
    • F23R2900/03044—Impingement cooled combustion chamber walls or subassemblies

Definitions

  • the invention relates to a heat shield element having a wall, which has a hot medium which can be acted upon by a hot medium and a cold side which is opposite to the hot side, and to which a coolant distributor system assigned to the cold side.
  • a heat shield assembly having a plurality of heat shield components.
  • the heat shield components are attached to a support structure and each heat shield component is directed along a major axis that is substantially perpendicular to that support structure.
  • a heat-shield component has an axis extending parallel to the support structure, a hot gas on exposed hot wall, which is adjacent to an interior space of ⁇ .
  • An inlet channel for cooling fluid directed along the main axis propagates in the direction of the hot gas wall into the interior. He is sen askschlos ⁇ with a cover wall which has passages for the flow of cooling fluid to ⁇ .
  • the cover panel is directed substantially parallel to the hot gas ⁇ wall and extends over the entire From ⁇ strain.
  • the cooling fluid flowing through the passages under high pressure impinges perpendicularly on the inner surface, causing impingement cooling there.
  • the discharge channel is followed by a discharge channel, which can be designed, for example, as a pipe.
  • the discharge channel preferably leads to a Bren ⁇ ner of the gas turbine, where the heated cooling air planning process supports the combustion.
  • DE 29714742 Ul is thus ge ⁇ characterized by a closed cooling system with inputs set an impingement cooling means.
  • DE 196 43 715 A1 has a cooled flame tube with egg ⁇ ner outer and an inner wall lining for a combustion chamber, wherein the wall lining is flowed through with a vaporous coolant.
  • the wall lining consists of juxtaposed segments which are provided with a number of through holes. The segments are equipped at the ends with a collector for the vaporous coolant. prevented. The coolant now passes from the collectors through the through holes in the flame tube. This is a closed cooling in which the coolant water vapor ⁇ is provided.
  • EP 1 005 620 B1 also discloses an impingement cooling device for cooling the combustion chamber wall of a gas turbine.
  • the whole combustion chamber wall is clad with heat-shield components out ⁇ which have the form of hollow tiles, and this heat-shield components are mounted on a support structure of the combustion chamber.
  • Each heat shield component has a hollow body whose bottom side can be exposed to a hot gas.
  • In the hollow body is another smaller hollow body than use.
  • This insert has on its bottom side passage openings, so that there is an impact cooling device. As a result, an interior space is formed, which is limited by the insert and the support structure.
  • the support structure has one or more inlet channels through which cooling fluid can enter the interior.
  • the support structure further has outlet channels from the gap, which is bounded by the insert, the hollow body and the support structure.
  • cooling fluid flows under high pressure through the inlet channels into the interior of the impingement baffle and passes through the plurality of impingement cooling holes in the gap, bouncing against the inside of the bottom side.
  • the heated after the impingement cooling fluid is conducted from the intermediate space via the off ⁇ vent channels.
  • the cooling fluid is thus, also in EP 1 005 620 Bl, guided in a closed cooling circuit.
  • the described heat shield ⁇ elements are designed so that a low consumption of cooling air is ensured. This allows a econom ⁇ 's operation of the system, but still under the condition that the cooling air is introduced under relatively high pressure for impingement cooling in the heat shield element to be cooled.
  • the object of the invention is a heat shield element suits ⁇ ben so that the disadvantages described of the prior Tech ⁇ nik be overcome, in particular, a uniform cooling of the wall to be cooled with efficient coolant inlet is set enabled.
  • the object relating to the heat shield element object is OF INVENTION ⁇ dung achieved by a heat shield member having a wall which includes a pressurizable with a hot medium hot side and a hot side opposite to the cold side on ⁇ , and with one of the cold side associated Verteilersys ⁇ system for coolant, wherein within the wall a plurality of cooling channels running along the hot side is provided and these cooling channels are fluidically connected to the distributor system.
  • the invention is based on the recognition that the existing ⁇ cooling concepts based on an impingement cooling of the wall to be cooled reach the design and optimization limits with respect to the coolant consumption. Therefore, the invention takes a completely different route to cool the wall using convective concepts. It is proposed for the first time, the wall to be cooled even for a design efficient convective cooling in which cooling channels are provided within the wall. These cooling channels are supplied by means of the associated distribution system in each case with coolant , for example cooling air of suitable pressure and temperature levels as well as mass flow.
  • the convective cooling which takes place in the cooling channels during operation, achieves a reduction of the temperature in the wall to be cooled even before the large part of the heat flow has reached the inside of the heat shield.
  • ner impingement cooling the heat is removed from the hollow interior of the heat shield element.
  • ⁇ a lot of heat at an earlier stage of the heat transfer is transported away via the channels in the wall. In this way, the temperature gradient of the interim rule ⁇ the hot side and the cold side significantly reduced the wall to be cooled.
  • the advantage of convective cooling, which takes place already in the wall, opposite the impingement cooling or convective cooling in the interior of the thermal shields of is that the temperature of the interior is clearly niedri ⁇ ger than in the other cases, and that is particularly Güns ⁇ tig for the components of the heat shield (bolts, gaskets, springs) that are not thermally stressed.
  • the coolant is supplied via a supply channel. At the end of this supply channel, the coolant collects and then flows into the distribution system.
  • the new concept disclosed in the present patent application overcomes both the disadvantages of the prior art and provides for a much more efficient use of coolant.
  • the advantages of a heat shield element designed after this concept are that, thanks to the predominantly convective cooling the amount of compressor bleed air at a Gastur ⁇ bine can be reduced even further, as compared with the above-discussed prior art.
  • this type of cooling ensures a uniform temperature distribution in the wall of the heat shield element and achieved by an adjustable over the pressure level coolant flow, the impingement cooling of the collection point of the coolant in the supply channel. This results in an improvement in the cooling of the particularly critical areas.
  • the cooling channels have an inlet and an outlet for the coolant.
  • Two execution ⁇ are forms possible, and the combination of the two.
  • each of the cooling channels has a respective inlet and outlet.
  • it is a common inlet (or outlet) which is connected to a plurality of channels, or fluidically communicates.
  • the wall to be cooled to a first Be ⁇ ten Scheme and an opposing second side region, so that the inlet of the cooling channel in the first Sobe ⁇ is arranged rich and the outlet is arranged in the second side portion.
  • the coolant can be passed through the distribution system in the first side area and enter the wall to be cooled via the inlet in the first side region.
  • the refrigerant then passes to the gege ⁇ nübericide page range and that leads to a uniform cooling along and within the entire wall.
  • the coolant can absorb correspondingly much heat energy due to the distance in the cooling channel and the average residence time, which leads to a low coolant requirement.
  • the length of the cooling channels and thus the length of the heat shield element are chosen so that all temperature boundary conditions are met at the highest ⁇ possibledeffenetzeckung, ie the heating of the coolant can be increased by variations of the heat shield or wall length up to the permissible limit.
  • the inlet and the outlet of the cooling channels in the first side region of the cooling channels in the first side region of the
  • the above-mentioned advantages are maintained - the heat shield element is pulled through from the first side area to the second side area of cooling channels, which ensure a uniform temperature distribution on the wall to be cooled and at the same time enables a more efficient use of coolant.
  • the cooling channel and thus the coolant makes a change in direction as it flows through the wall.
  • temperature gradients can be further reduced because on average in a side region the heat dissipation is more uniform, for. B. only up to the middle of the wall.
  • Another preferred feature of the heat shield element summarizes a cooling channel whose inlet in the first Sobe ⁇ reaching the wall is and has at least one U-turn in the second side portion of the wall such that opposite at a cooling adjacent channels are throughput can flow, so that a Countercurrent of coolant in the wall can be generated.
  • the principle here is that the allowable amount of heat that the coolant can absorb from the wall to be cooled is not achieved by variations in the wall length, but with a constant size of the heat shield element, the length of the channel is increased, resulting in at least one U-turn in the second page area leads.
  • a further preferred embodiment of this principle comprises the use of a cooling channel which is serpentine. This means more than a U-turn of the cooling channel and has a plurality of adjacent channels, in which a countercurrent of coolant is generated. This can be the outlet the cooling channel may be arranged both in the first and in the second side region.
  • the cooling channels are preferably arranged closer to the hot side than to the cold side of the wall to be cooled.
  • This embodiment leads to a significantly improved heat transfer between the hot side of the wall and the coolant in the Ka ⁇ nälen.
  • the overall thickness of the wall is designed so that deformations and stresses are considered and controlled.
  • the distance of the cooling channels from the hot side is between 20% and 40% of the wall thickness. A height ⁇ rer distance would affect the transfer of heat, a smaller would lead to significant distortions of the hot side of the wall.
  • the distribution system is mounted directly on the cold side of the wall to be cooled.
  • the cooling means may - for example in the state mounted on a combustion chamber wall with a support structure with a - enter through a sealed supply channel in the heat shield: in this case be in the system no Le ⁇ ckagen occur.
  • This supply channel is formed, for example, in the support structure. It opens in the mounted state of the heat ⁇ shield element in the distribution system itself and can also be regarded as part of the distribution system. Via the distributor system on the cold side of the heat shield element, the coolant reaches the first side region and enters the cooling channels there.
  • the distribution system and the cooling ⁇ channels can be designed for both a closed and for an open cooling, but preferably an open cooling is provided.
  • outlets of the cooling channels are preferably placed on the cold side is ⁇ so that coolant flows under the wall at the outlet from the cooling channels part or a sealing air effect is achieved.
  • the pressure of the coolant is higher than the ambient pressure of the hot gases. This will prevent that
  • the heat shield element preferably consists of a high temperature resistant ⁇ material, especially a metal or metal alloy, for example, high temperature resistant alloys based on iron, chromium, nickel and cobalt.
  • the length of the Hitzschildettis from the outer edge of the first Be ⁇ ten Schemes to the outer edge of the second side region is preferably between 200mm and 400mm.
  • the heat shield element is used for cooling a hot gas-carrying component, in particular a combustion chamber, an annular combustor before ⁇ preferably a gas turbine, comprising a support structure, are attached to the these heat shield elements.
  • the heat shield element is attached vorzugswei ⁇ se with a fastening bolt on the support structure of the combustion chamber.
  • the bolt is preferably located on the cold side of the wall to be cooled, which is very advantageous during operation.
  • the support structure of the combustion chamber preferably has at least one feed channel, so that the coolant on the Zubowka ⁇ nal is fed to the heat shield element.
  • the supply channel is introduced into the support structure, for example as a bore or as a plurality of holes forming the supply channel.
  • This supply channel preferably opens into the distribution system.
  • the feed channel is sealed from the environment to prevent leaks.
  • the combustion chamber to which heat shield elements are attached is preferably part of a gas turbine plant.
  • These gas turbine installation has a compressor, from the preferential ⁇ example cooling air is branched off as a cooling means for cooling the combustion chamber. This compressor discharge air serves to cool the heat shield elements.
  • FIG. 1 shows a half section through a gas turbine plant with compressor, combustion chamber and turbine
  • FIG 2 shows a longitudinal section through the heat shield element
  • FIG 3 shows a cross section through the heat shield element ge ⁇ Frankfurtss Fig. 2
  • FIG. 4 shows a cross section through a heat shield element GE measured Fig. 2, with respect to a to be cooled
  • FIG. 5 shows a cross section through one half of a heat ⁇ shield element with cooling channels
  • FIG. 6 shows a cross section through one half of a heat shield element with respect to FIG. 5 alternative
  • the gas turbine system 33 includes a compressor 35, an annular combustor 23 with a plurality of burners 37 for a liquid or gaseous fuel and a gas turbine 25 for driving the compaction ⁇ ters 35 and a generator, not shown in Fig. 1
  • the entire combustion chamber wall is lined with heat shield elements 1 shown in greater detail in FIG. 2, or the heat shield elements 1 are attached to a support structure 27 on the combustion chamber wall.
  • the Gasturbinenan ⁇ position 33 L air is sucked from the environment.
  • the compressor 35 the air L is compressed and thereby partially heated.
  • a small portion of the air L is taken from the compressor 35 and supplied to the heat shield elements 1 as coolant K, the greater part of the air L is supplied to the burners for combustion.
  • the greater part of the air L from the compressors 35 is brought together with the liquid or gaseous fuel and burnt.
  • ent ⁇ is the hot medium M, in particular hot gas
  • the gas turbine 27 drives ⁇ .
  • an Ent ⁇ voltage and cooling of the hot gas M is shown schematically in a longitudinal section.
  • the heat shield element 1 is fastened to the support structure 27 with a fastening bolt 29.
  • the heat shield ⁇ element 1 has a wall 3.
  • the wall 3 has a hot side 5 which can be acted upon by the hot medium M and a cold side 7 which lies opposite the hot side 5.
  • a manifold system 9 for coolant K is the cold side 7 supplied ⁇ arranged; present the manifold system 9 is mounted directly on the cold side 7, and is thus part of the heat shield element 1 itself.
  • the distribution system 9 is strö ⁇ mung-connected to the cooling channels 11 such that coolant K is distributed to the cooling channels 11 via the manifold system 9.
  • coolant K, in particular ⁇ special cooling air L which is taken from the compressor 35, passed into the distribution system 9 and thereby passes into the space on the cold side 7 of the wall.
  • the coolant K is introduced into the supply channels 31 under high pressure. This pressure causes an additional impingement cooling at the end of the leading channels ⁇ 31, that is, where the coolant K divider system in the United ⁇ 9 flows. This causes an improved cooling particularly critical areas, such as near the Fixed To ⁇ supply pin 29.
  • the distribution system 9 ensures that the coolant K, which is still under high pressure, is introduced into the cooling channels 11, where it passes through its flow in ⁇ nerrenz the plurality of cooling channels 11 leads to a particularly effective convective cooling of the wall 3.
  • the supply channels 31 are sealed from the environment with seals 41 at the connection points between the heat shield element 1 and the support structure 27.
  • FIG. 3 shows a cross section through the heat shield element according to FIG. 2, on which the distribution system 9 and the outlets 15 of the channels 11 are shown in detail.
  • the coolant K flows through the supply channels 31 into the heat shield element 1 one. From there, it passes through the distributor system 9, which extends deeper in the direction of the wall 3 to be cooled with respect to the sectional plane shown in FIG. 3, to the first side region 17 of the heat shield element 1.
  • the first side region 17 are the inlets (see FIG ) of thedeka ⁇ ducts 11.
  • the first side portion 17 is also limited by its outer edge 17A.
  • the second side region 19 Opposite the first side region 17 on the wall 3 is the second side region 19.
  • the second side region 19 has an outer edge 19A.
  • the coolant K which is within the cooling channels 11 from the first Be ⁇ ten Scheme 17 to the second side portion 19 flows of the cooling channels escapes through the outlets 15 of 11 from the heat shield element 1.
  • FIG 3 also has a mounting opening 29B to detect.
  • the attachment opening 29B is concentrically surrounded by a plurality of supply channels 31 and thus they are equidistant from the attachment opening.
  • the annular seal 41 is placed around the supply channels 31 so that the entire system of supply channels 31 and the fastening bolt 29 that surrounds them is sealed by the environment.
  • FIG. 4 shows a cross section through a heat shield element 1 according to FIG. 2, with a sectional plane deeper than in FIG. 3 with respect to the wall 3 to be cooled.
  • the distributor system 9 encloses the attachment opening 29B and is in flow communication with the inlets 13 of the cooling channels IIA.
  • the inlets 13 are arranged in the first side area 17.
  • the off ⁇ outlets 15 are arranged in the second side region 19.
  • the cooling channels IIA from the first side portion 17 extend directly, in particular straight, to the second side portion 19 along the wall to be cooled 3.
  • the coolant K generates in this arrangement a direct flow of coolant K from the first side portion 17 to the second side portion 19, where the Coolant K flows out of the heat shield element 1.
  • the coolant K can also be used after the cooling task for blocking against hot gases M, in order to protect the support structure from a hot gas attack.
  • 5 shows a cross section through one half of a heat shield element 1 with cooling channels IIB, which generate a counter flow of coolant K in the wall to be cooled.
  • the second side portion 19 close to the outer edge 19A to the cooling ducts IIB a U-turn 21, whereindemit ⁇ K tel changes direction and flows back toward the first side portion 17th
  • the outlets 15 of the cooling channels IIB are in the present arrangement in the first side region 17 in a space separated from the distribution system 9 and are closer to the outer edge 17A than the inlets 13.
  • inlets 13 and outlets 15 are offset from each other in the first Side area 17 is arranged. From the distribution system 9, the inlets 13 are acted upon by coolant K.
  • FIG 6 is a cross section through one half of a heat shield member 1 is with respect to FIG 5 alternative Ausgestal ⁇ the cooling channels HC tung shown.
  • the coolant K which is introduced from the distributor system 9 into the inlets 13 of the cooling channels HC, flows from the first side region 17 along the wall 3 to be cooled in the direction of the second side region 19.
  • the cooling channels In the second side region 19, the cooling channels have a U-turn 21.
  • the coolant K changes its flow direction for the first time.
  • the cooling channels HC again reach the first side region 17, they turn around again and have a second turnaround 21 at the location.
  • adjacent channels are flowed through in opposite directions, so that a countercurrent of coolant K is generated.
  • the outlets 15 of the cooling channels HC are arranged in this case in the second side region 19.
  • ⁇ have at both configurations at least one reciprocal turn 21, and thereby a counterflow of coolant K is ER- testifies.
  • a multiplicity of reversing applications 21 can thus be provided in order to achieve a serpentine-shaped cooling structure.
  • ⁇ dene cooling arrangements in which the straightdekanä- Ie IIA and serpentine cooling channels IIB and HC are combined together with a heat shield element. 1
  • the present invention proposes a novel, particularly efficient cooling of a heat shield element.
  • the basic idea is that cooling channels are provided within the wall of the heat shield element to be cooled.
  • the wall which is acted upon during operation with hot medium, are cooled very convective convective.
  • the convective cooling which is achieved in the wall itself, on the one hand ensures a very efficient use of coolant and on the other hand for a very uniform temperature distribution of the wall to be cooled.
  • the En ⁇ is achieved of the supply channel, an additional cooling in the Particularly critical areas of the heat shield element by the adjustable impingement cooling.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)

Abstract

L'invention concerne un écran thermique (1) qui comprend une paroi (3) présentant un côté chaud (5) pouvant être exposé à un fluide chaud (M) et un côté froid (7) opposé au côté chaud (5), ainsi qu'un système distributeur (9) associé au côté froid (7) pour assurer la distribution d'un agent de refroidissement (K). Selon l'invention, pour que cet écran thermique (1) puisse être refroidi par convection de façon particulièrement efficace, une pluralité de canaux de refroidissement (11A, 11B, 11C) s'étendant le long du côté chaud (5) sont disposés à l'intérieur de la paroi (3). Ces canaux de refroidissement (11A, 11B, 11C) sont en communication fluidique avec le système distributeur (9) de sorte que l'agent de refroidissement (K) puisse être réparti entre les canaux de refroidissement (11A, 11B, 11C) individuels au moyen du système distributeur (9). Cet écran thermique (1) à refroidissement par convection peut être utilisé de façon particulièrement avantageuse comme revêtement thermorésistant d'une chambre de combustion (23), en particulier d'une chambre de combustion (23) d'une installation à turbine à gaz (33).
EP05821767A 2004-12-16 2005-12-15 Ecran thermique Withdrawn EP1836442A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP05821767A EP1836442A1 (fr) 2004-12-16 2005-12-15 Ecran thermique

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
EP04029874A EP1672281A1 (fr) 2004-12-16 2004-12-16 Elément de protection thermique
PCT/EP2005/056814 WO2006064038A1 (fr) 2004-12-16 2005-12-15 Ecran thermique
EP05821767A EP1836442A1 (fr) 2004-12-16 2005-12-15 Ecran thermique

Publications (1)

Publication Number Publication Date
EP1836442A1 true EP1836442A1 (fr) 2007-09-26

Family

ID=34927813

Family Applications (2)

Application Number Title Priority Date Filing Date
EP04029874A Withdrawn EP1672281A1 (fr) 2004-12-16 2004-12-16 Elément de protection thermique
EP05821767A Withdrawn EP1836442A1 (fr) 2004-12-16 2005-12-15 Ecran thermique

Family Applications Before (1)

Application Number Title Priority Date Filing Date
EP04029874A Withdrawn EP1672281A1 (fr) 2004-12-16 2004-12-16 Elément de protection thermique

Country Status (3)

Country Link
US (1) US20080127652A1 (fr)
EP (2) EP1672281A1 (fr)
WO (1) WO2006064038A1 (fr)

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EP1672281A1 (fr) 2006-06-21

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