EP3117148B1 - Brenneranordnung mit resonator - Google Patents

Brenneranordnung mit resonator Download PDF

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Publication number
EP3117148B1
EP3117148B1 EP15719643.7A EP15719643A EP3117148B1 EP 3117148 B1 EP3117148 B1 EP 3117148B1 EP 15719643 A EP15719643 A EP 15719643A EP 3117148 B1 EP3117148 B1 EP 3117148B1
Authority
EP
European Patent Office
Prior art keywords
resonator
annular space
end plate
plate
volume
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.)
Active
Application number
EP15719643.7A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP3117148A1 (de
Inventor
Christian Beck
Olga Deiss
Patrick Ronald Flohr
Anna KNÖDLER
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
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Siemens AG
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Publication of EP3117148A1 publication Critical patent/EP3117148A1/de
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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
    • F23R3/28—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
    • 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
    • F23R3/02—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 assembly having a combustion chamber, a plurality of merging into the combustion chamber mixing channels, in which during normal operation initiated combustion air and introduced 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 an exciting oscillation coincides with a resonant frequency of the burner arrangement or its components, components can be destroyed. The excitation of the burner assembly and its components in the range of such resonance frequencies must be avoided accordingly.
  • the publication EP 1 481 195 B1 proposes to arrange resonators between a fuel introduction position and the combustion chamber.
  • this represents a direct influence on the fuel mass flow, which is considered disadvantageous.
  • resonators formed in this way are not suitable for covering a wide frequency range.
  • the EP 0 597 138 A1 describes a gas turbine combustor, which has circumferentially distributed and air-purged resonators in the region of the combustion chamber inlet. Again, however, there is the problem that the cooling air is not directly available for combustion and thus increase the NOx emissions. From the patent US 8 438 851 B1 Another burner arrangement is known. In an end wall, a fuel plenum and adefluidplenum are arranged.
  • the mixing channels are formed by mixing tubes which extend axially through an annulus, defined between a tubular outer wall, a tubular inner wall spaced radially from the outer wall, an upstream annular face plate, and a downstream annular face plate, the face plates being provided with through holes receiving and / or continuing the mixing tubes
  • the at least one resonator are designed as air channels which extend through at least one of the end plates, and that the resonator volume of the at least one 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. In addition, it is provided on the cold side of the burner assembly, which is why it requires no cooling.
  • At least one annular partition plate is provided between the upstream end plate and the downstream end plate, which has the through-openings receiving the mixing tubes and divides the annulus into partial annuli. Thanks to such a partition plate, the resonator volume of the at least one resonator can be set exactly.
  • both the upstream faceplate and the downstream faceplate have air channels, so that the partial ring spaces have 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 partial annular space defined between the at least one partition plate and the downstream end plate has a smaller volume than the partial annular space defined between the upstream end plate and the partition 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 above-described resonator disposed adjacent to the combustion chamber is again 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 volume of the chambers is advantageously different, in order to be able to specifically cover different frequency ranges.
  • the upstream end plate is formed as a support plate accommodating the weight of the mixing tubes and carrying the weight thereof, which is fixed to, for example, a flange plate which fixes the entire burner assembly to a machine housing or the like.
  • 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 mixing tube assembly 4 with a plurality of mixing tubes 5, which open into the combustion chamber 2, a plurality of fuel injectors 6, which project into the mixing tubes 5 to a suitable position, and a mounting plate 7 which receives the mixing tube assembly 4 and serves to fasten the burner assembly 1 to a machine housing, not shown.
  • the mixing tube assembly 4 comprises a tubular outer wall 8, a tubular inner wall 9 spaced radially from the outer wall 8, an upstream annular end plate 10 and a downstream face plate 11 defining an annulus 12 through which the mixing tubes 5 extend in the axial direction , Furthermore, the mixing tube assembly 4 comprises an annular partition plate 13, which divides the annular space 12 into two partial annular spaces 14 and 15.
  • the defined between the partition plate 13 and the downstream face plate 11 partial annulus 15 has a much smaller volume than the partial annulus space 14 which is defined between the upstream end plate 10 and the partition plate 13. In the present case, 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 passage openings 16 in the present case define two hole circles with mutually different pitch circle diameters, wherein the through holes 16 of the first pitch circle and the through holes 16 of the second pitch circle are arranged offset from one another in the radial direction.
  • the end plate 10 has a plurality of air channels 17, which extend in the axial direction and are distributed over the annular surface of the end plate 10. 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 end plate 10 forms the support plate of the entire mixing tube assembly 4, which is why it is designed correspondingly solid.
  • a mounting device 18 is attached, which serves to attach the mixing tube assembly 4 to the mounting plate 7 of the burner assembly 1.
  • the partition plate 13 is analogous to the end plate 10 is provided with through holes 19 which are aligned with the through holes 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.
  • 500 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 Spülluftkanäle 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 arranged face plate 11 comprises analogous to the face plate 10 and the partition plate 13 through holes 23 which are aligned axially with the through holes 16 of the end plate 10 and the through holes 19 of the partition plate 13. Further, axially extending air channels 24 are formed in the end plate 11, which connect the partial annular space 15 with the combustion chamber 2 fluidly.
  • the partitions 21 of the partition plate 13 are at the front plate 11 to form the aforementioned chambers 22.
  • the chambers 22 each define resonator volumes of high-frequency resonators whose resonator openings 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 22 are chosen differently, the high-frequency resonators attenuate 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 purge air channels 20 provided in the partition plate 13 define scavenging 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 volume of the middle frequency resonator can be chosen, for example, such that a resonator frequency in the range of 170 Hz is established.
  • 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 plurality 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 to the high-frequency resonators via the purge air channels 20 provided in the partition plate 13. 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 act simultaneously in different directions, to the plenum on the one hand and the combustion chamber on the other.
  • 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 regard 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)
EP15719643.7A 2014-05-19 2015-04-17 Brenneranordnung mit resonator Active EP3117148B1 (de)

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 EP3117148A1 (de) 2017-01-18
EP3117148B1 true 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 (zh)
EP (1) EP3117148B1 (zh)
CN (1) CN106461222B (zh)
WO (1) WO2015176887A1 (zh)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
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 (en) * 2018-03-23 2021-05-05 Ansaldo Energia Switzerland AG Gas turbine having a damper
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 (en) * 2021-12-20 2023-06-21 General Electric Company Combustor with 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

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Also Published As

Publication number Publication date
CN106461222A (zh) 2017-02-22
US10605457B2 (en) 2020-03-31
EP3117148A1 (de) 2017-01-18
WO2015176887A1 (de) 2015-11-26
CN106461222B (zh) 2019-03-15
US20170082287A1 (en) 2017-03-23

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