EP3117148A1 - Brenneranordnung mit resonator - Google Patents
Brenneranordnung mit resonatorInfo
- Publication number
- EP3117148A1 EP3117148A1 EP15719643.7A EP15719643A EP3117148A1 EP 3117148 A1 EP3117148 A1 EP 3117148A1 EP 15719643 A EP15719643 A EP 15719643A EP 3117148 A1 EP3117148 A1 EP 3117148A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- resonator
- end plate
- plate
- annular space
- combustion chamber
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
- F23M—CASINGS, LININGS, WALLS OR DOORS SPECIALLY ADAPTED FOR COMBUSTION CHAMBERS, e.g. FIREBRIDGES; DEVICES FOR DEFLECTING AIR, FLAMES OR COMBUSTION PRODUCTS IN COMBUSTION CHAMBERS; SAFETY ARRANGEMENTS SPECIALLY ADAPTED FOR COMBUSTION APPARATUS; DETAILS OF COMBUSTION CHAMBERS, NOT OTHERWISE PROVIDED FOR
- F23M20/00—Details of combustion chambers, not otherwise provided for, e.g. means for storing heat from flames
- F23M20/005—Noise absorbing means
-
- 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
- F23R3/28—Continuous combustion chambers using liquid or gaseous fuel characterised by the fuel supply
- F23R3/286—Continuous combustion chambers using liquid or gaseous fuel characterised by the fuel supply having fuel-air premixing devices
-
- 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
- F23R3/02—Continuous combustion chambers using liquid or gaseous fuel characterised by the air-flow or gas-flow configuration
- F23R3/04—Air inlet arrangements
- F23R3/10—Air inlet arrangements for primary air
-
- 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
- F23R2900/00013—Reducing thermo-acoustic vibrations by active means
-
- 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
- F23R2900/00014—Reducing thermo-acoustic vibrations by passive means, e.g. by Helmholtz resonators
-
- 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
- F23R3/42—Continuous combustion chambers using liquid or gaseous fuel characterised by the arrangement or form of the flame tubes or combustion chambers
Definitions
- the present invention relates to a burner arrangement having a combustion chamber, a multiplicity of mixing channels opening into the combustion chamber, in which combustion air introduced during normal operation and mixed fuel are mixed, and at least one resonator having a defined resonator volume and resonator openings.
- Burner arrangements are known in the prior art in various configurations.
- a burner arrangement such as, for example, a gas turbine
- thermoacoustically induced combustion oscillations occur in the combustion chamber. These can excite components of the burner assembly to vibrate. If a stimulating oscillation coincides with a resonance frequency of the burner arrangement or its components, this can lead to the destruction of components.
- the excitation of the burner assembly and its components in the range of such resonance frequencies must be avoided accordingly. It is already known the acoustic properties of
- EP 2 559 942 A1 discloses a resonator which is arranged in the combustion chamber hood or in the region of the cooling air feed.
- a disadvantage of such an arrangement is that the damping does not take place directly at the source of vibration in the area of the combustion chamber and thus has a low Ef ⁇ ficiency.
- EP 1 792 123 B1 proposes introducing compressor air into the combustion chamber through resonator devices integrated into the combustion chamber wall.
- the advantage of this design is the coupling of wall cooling and resonator purging as well as the integration of medium and high frequency resonators in the combustion chamber wall.
- a disadvantage is the double-walled design of the combustion chamber wall, which entails a great design effort and high costs.
- EP 0 597 138 A1 describes a gas turbine combustion chamber which has circumferentially distributed and air-purged resonators in the region of the combustion chamber inlet. Again, however, the problem arises that the cooling ⁇ air is not directly available for combustion and thus increase the NOx emissions.
- the present invention provides a burner assembly of the type mentioned above, which is characterized in that the mixing channels are formed by mixing tubes ge ⁇ extending axially through an annulus, between a tubular outer wall, a tubular inner wall spaced radially from the outer wall, an upstream annular end plate, and a downstream annular one
- Face plate is defined, wherein the end plates are provided with through ⁇ openings, which receive the mixing tubes and / or continue that the resonator openings of the at least one resonator are formed as air channels extending through at least one of the end plates, and that the resonator volume of at least a resonator is formed by at least a part of the annular space.
- the structure of the burner assembly according to the invention is on the one hand to the advantage that thanks to the fact that the mixing channels are not formed by a massive nozzle carrier but by individual mixing tubes, material, cost and weight can be saved.
- the annulus is used as a resonator volume for the at least one resonator, whereby a resonator with a simple and inexpensive construction is formed.
- the resonator is arranged adjacent to the combustion chamber, so that it acts directly at the origin of the vibrations and thus effectively. Since ⁇ over, he is provided on the cold side of the burner assembly, which is why it needs no refrigeration.
- both the upstream face plate and the downstream face plate have air channels, so that the partial ring spaces resonator volumes of at least define two resonators, which act on the one hand in the cold plenum space and on the other hand in the hot combustion chamber at different frequencies.
- the resonator facing the plenum chamber can act on pressure fluctuations of the compressor.
- the at least one partition plate is provided with a plurality of scavenging air passages through which cold air can enter at least one resonator facing the combustion chamber and flush it.
- the cold air also prevents hot combustion gases from entering the resonator.
- the part annular space defined between the at least one Trennplat ⁇ te and the downstream end plate has a smaller volume than the portion of annular space which is defined between the upstream end plate and the separator plate.
- the resonator with the smaller resonator volume is arranged as a high-frequency resonator directly adjacent to the combustion chamber in order to dampen the high-frequency oscillations that predominantly occur in the combustion chamber.
- the second resonator with the larger resonator volume provided adjacent to the upstream faceplate is designed as a middle frequency resonator.
- the volume of the partial annular space defined between the partition plate and the downstream end plates is not more than 20% of the volume of that partial annular space defined between the upstream end plate and the partition plate. With this size distribution very good results were achieved.
- the partial annular space defined between the at least one partition plate and the downstream end plate is divided into a plurality of chambers by radially extending partitions.
- the Re ⁇ sonator previously described disposed adjacent to the combustion chamber-yet once divided into a plurality of smaller resonators.
- the air channels provided in the downstream end plate, which form the resonator openings of these resonators, may vary as required in terms of their number and diameter from one resonator to another.
- the upstream face plate is as the mixing tubes receiving and carrying their weight carrier plate, which is attached, for example, to a flange plate with which the entire burner assembly to a machine housing or the like is attached.
- Figure 1 is a schematic sectional view of a Bren ⁇ neranix according to an embodiment of the present invention
- Figure 2 is a sectional view of a mixing tube assembly of the burner assembly shown in Figure 1;
- Figure 3 is a partial rear view of the Darge in Figure 2 ⁇ presented mixing tube assembly;
- Figure 4 is a view of a partition plate of the mixing tube assembly shown in Figure 2.
- Figure 5 is a view of a downstream arranged
- the figures show a burner assembly 1 according to an embodiment of the present invention or components thereof.
- the burner assembly 1 comprises a combustion chamber 2, a centrally located pilot burner 3, a Mischrohran- order 4 with a plurality of mixing tubes 5, which open into the combustion chamber 2, a plurality of Brennstoffinj sectors 6, up to a suitable position in the mixing tubes. 5 protrude, and a mounting plate 7, which receives the Mischrohranord ⁇ tion 4 and serves to attach the burner assembly 1 to a nem not shown machine housing.
- the mixing tube assembly 4 comprises a tubular outer wall 8, a tubular inner wall 9 spaced radially from the outer wall 8, an annular annular end plate 10 disposed upstream, and a downstream one
- the mixing tube arrangement 4 comprises an annular partition plate 13, which divides the annular space 12 into two partial annular spaces 14 and 15.
- the space defined between the partition plate 13 and the downstream ⁇ Windier arranged end plate 11 part of annular space 15 has a considerably smaller volume than the portion of annular space 14 which is defined between the upstream end plate 10 and the partition plate. 13
- the volume of the partial annular space 15 corresponds to approximately 1/10 of the partial annular space 14.
- the upstream face plate 10 includes a plurality of through holes 16 which receive and / or continue the mixing tubes 5.
- the through-openings 16 define present two hole circles with each other, various ⁇ which pitch circle diameters, wherein the through-holes offset 16 of the first hole circle, and the through holes 16 of the two ⁇ th hole circle in the radial direction are mutually arranged arrival.
- the end plate 10 has a plurality of air channels 17, which extend in the axial direction and distributed over the annular surface of the face plate 10 are arranged on ⁇ . In the present case 45 air channels 17 with a 5 mm diameter, just to name one example. It should be understood, however, that the number and diameter of the air channels 17 may be varied as needed.
- the face plate 10 forms the support plate of the entire
- the partition plate 13 is analogous to the end plate 10 provided with through ⁇ openings 19 which are aligned with the passage openings 16 of the end plate 10 in the axial direction. Further, the partition plate 13 is provided with a plurality of scavenging air channels 20 which are arranged distributed over the annular surface of the partition plate 13 and connect the partial annular space 14 with the partial annular space 15 fluidly.
- purge air channels 20 are formed with a diameter in the range of 1 - 1.3 mm in the partition plate 13, to name just one example, wherein the number and the diameter of the scavenging air channels 20 may vary as needed.
- radially extending partition walls 21 are formed on the partition plate 13, which divide the partial annular space 15 into a plurality of chambers 22, which have different volumes from each other.
- the downstream face plate 11 comprises analogous to the face plate 10 and the partition plate 13 through openings 23, the axial c with the passage openings 16 of the face plate 10 and the through holes 19 of the partition plate 13 th. Furthermore, axially extending air channels 24 are formed in the end plate 11 that fluidly connect the partial annular space 15 with the combustion chamber 2.
- the chambers 22 each define
- Resonator volumina of high frequency resonators whose
- Resonatorö réelleen are formed by the air channels 24, which connect the partial annular space 15 with the combustion chamber 2. Due to the fact that the volumes of the individual chambers are chosen to be different 22 attenuate the high-frequency resonators ⁇ factors different frequencies. For example, high frequency resonators can be used to attenuate frequencies between 1000 Hz and 5000 Hz, to name but one example.
- the number and diameter of the air channels 17 provided per chamber varies as needed as a function of the frequencies to be damped.
- the scavenging air ducts 20 provided in the partition plate 13 define flushing air openings for the high-frequency resonators, which on the one hand prevent the entry of hot air into the partial annular space 14 and on the other hand ensure sufficient cooling.
- the partial annular space 14 defines the resonator volume of a medium-frequency resonator acting on the cold plenum chamber, the resonator openings of which form the air channels 17 of the end plate 10.
- the scavenging air passages 20 formed in the partition plate 13 provide broadening of the frequency range to be attenuated.
- the resonator of the Mittelfrequenzresonators may be selected for play ⁇ such that a
- Resonator frequency in the range of 170 Hz sets is in the range of 170 Hz sets.
- a significant advantage of the burner assembly 1 described above is that a plurality of resonators is formed integrally with the mixing tube assembly 4. Thus, an effective damping is achieved at very different frequencies, which manages without additional space and is associated with low costs.
- the resonators provide damping both upstream and downstream, which can prevent damage to components. Thanks to the division of the resonators into a middle frequency resonator and a multiplicity of high frequency resonators and thanks to the choice of the arrangement of the resonators damping is provided in each case where it is needed immediately.
- the middle frequency resonator works on the cold side in the direction of the plenum chamber to low-frequency pressure fluctuations, while the high-frequency resonators act on high-frequency pressure fluctuations in the combustion chamber.
- the middle frequency resonator is coupled via the provided in the partition plate 13 scavenge air channels 20 with the Hochfrequenzresona ⁇ gates. It is particularly important that this coupling does not affect the frequencies of the individual resonators. Rather, all resonators can be individually and independently set to predetermined frequencies. This effect is achieved in that the acoustically effective openings simultaneously act in different directions, to the plenum on the one hand and the combustion chamber on the other hand.
- the purge air mass flow which can be set via the design, fulfills several tasks.
- the attenuation spectra of the individual resonators are broadened with respect to their frequency.
- the high-frequency resonators are blocked against the penetration of hot gas from the combustion chamber.
- the temperature of the resonators is controlled. Further, the mixing tube assembly is cooled on the hot side.
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Gas Burners (AREA)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102014209446 | 2014-05-19 | ||
PCT/EP2015/058407 WO2015176887A1 (de) | 2014-05-19 | 2015-04-17 | Brenneranordnung mit resonator |
Publications (2)
Publication Number | Publication Date |
---|---|
EP3117148A1 true EP3117148A1 (de) | 2017-01-18 |
EP3117148B1 EP3117148B1 (de) | 2018-06-06 |
Family
ID=53039390
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP15719643.7A Active EP3117148B1 (de) | 2014-05-19 | 2015-04-17 | Brenneranordnung mit resonator |
Country Status (4)
Country | Link |
---|---|
US (1) | US10605457B2 (de) |
EP (1) | EP3117148B1 (de) |
CN (1) | CN106461222B (de) |
WO (1) | WO2015176887A1 (de) |
Families Citing this family (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US10145561B2 (en) * | 2016-09-06 | 2018-12-04 | General Electric Company | Fuel nozzle assembly with resonator |
EP3543610B1 (de) * | 2018-03-23 | 2021-05-05 | Ansaldo Energia Switzerland AG | Gasturbine mit dämpfer |
CN111520747B (zh) * | 2020-03-17 | 2021-10-26 | 西北工业大学 | 一种柔和燃气轮机燃烧室 |
EP4198395A1 (de) * | 2021-12-20 | 2023-06-21 | General Electric Company | Brennkammer mit resonator |
CN115355534B (zh) * | 2022-09-05 | 2024-03-12 | 中国联合重型燃气轮机技术有限公司 | 一种燃气轮机燃料混合系统及燃气轮机 |
Family Cites Families (21)
Publication number | Priority date | Publication date | Assignee | Title |
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US4122674A (en) * | 1976-12-27 | 1978-10-31 | The Boeing Company | Apparatus for suppressing combustion noise within gas turbine engines |
DE3432607A1 (de) | 1984-09-05 | 1986-03-13 | Messerschmitt-Bölkow-Blohm GmbH, 8012 Ottobrunn | Einrichtung zum daempfen von brennkammerschwingungen bei fluessigkeitsraketentriebwerken |
DE59208715D1 (de) | 1992-11-09 | 1997-08-21 | Asea Brown Boveri | Gasturbinen-Brennkammer |
EP1342952A1 (de) | 2002-03-07 | 2003-09-10 | Siemens Aktiengesellschaft | Brenner, Verfahren zum Betrieb eines Brenners und Gasturbine |
DE102004018725B4 (de) | 2004-04-17 | 2015-02-12 | Astrium Gmbh | Dämpfung von Schwingungen einer Brennkammer durch Resonatoren |
US7334408B2 (en) | 2004-09-21 | 2008-02-26 | Siemens Aktiengesellschaft | Combustion chamber for a gas turbine with at least two resonator devices |
US7827797B2 (en) * | 2006-09-05 | 2010-11-09 | General Electric Company | Injection assembly for a combustor |
US8127546B2 (en) * | 2007-05-31 | 2012-03-06 | Solar Turbines Inc. | Turbine engine fuel injector with helmholtz resonators |
US8438853B2 (en) * | 2008-01-29 | 2013-05-14 | Alstom Technology Ltd. | Combustor end cap assembly |
US8516819B2 (en) * | 2008-07-16 | 2013-08-27 | Siemens Energy, Inc. | Forward-section resonator for high frequency dynamic damping |
US8424311B2 (en) * | 2009-02-27 | 2013-04-23 | General Electric Company | Premixed direct injection disk |
US8495881B2 (en) * | 2009-06-02 | 2013-07-30 | General Electric Company | System and method for thermal control in a cap of a gas turbine combustor |
US8789372B2 (en) | 2009-07-08 | 2014-07-29 | General Electric Company | Injector with integrated resonator |
US8616002B2 (en) * | 2009-07-23 | 2013-12-31 | General Electric Company | Gas turbine premixing systems |
JP2011102669A (ja) | 2009-11-10 | 2011-05-26 | Mitsubishi Heavy Ind Ltd | ガスタービン燃焼器及びガスタービン |
US8322143B2 (en) * | 2011-01-18 | 2012-12-04 | General Electric Company | System and method for injecting fuel |
US9341375B2 (en) * | 2011-07-22 | 2016-05-17 | General Electric Company | System for damping oscillations in a turbine combustor |
JP5438727B2 (ja) * | 2011-07-27 | 2014-03-12 | 株式会社日立製作所 | 燃焼器、バーナ及びガスタービン |
EP2559942A1 (de) | 2011-08-19 | 2013-02-20 | Rolls-Royce Deutschland Ltd & Co KG | Brennkammerkopf einer Gasturbine mit Kühlung und Dämpfung |
US8438851B1 (en) * | 2012-01-03 | 2013-05-14 | General Electric Company | Combustor assembly for use in a turbine engine and methods of assembling same |
US9212822B2 (en) | 2012-05-30 | 2015-12-15 | General Electric Company | Fuel injection assembly for use in turbine engines and method of assembling same |
-
2015
- 2015-04-17 WO PCT/EP2015/058407 patent/WO2015176887A1/de active Application Filing
- 2015-04-17 CN CN201580025974.8A patent/CN106461222B/zh active Active
- 2015-04-17 US US15/310,648 patent/US10605457B2/en active Active
- 2015-04-17 EP EP15719643.7A patent/EP3117148B1/de active Active
Also Published As
Publication number | Publication date |
---|---|
US10605457B2 (en) | 2020-03-31 |
US20170082287A1 (en) | 2017-03-23 |
CN106461222A (zh) | 2017-02-22 |
EP3117148B1 (de) | 2018-06-06 |
CN106461222B (zh) | 2019-03-15 |
WO2015176887A1 (de) | 2015-11-26 |
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