EP1213538B1 - Dispositif pour gaz d'échappement comprenant un résonateur de Helmholtz - Google Patents

Dispositif pour gaz d'échappement comprenant un résonateur de Helmholtz Download PDF

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Publication number
EP1213538B1
EP1213538B1 EP01811076A EP01811076A EP1213538B1 EP 1213538 B1 EP1213538 B1 EP 1213538B1 EP 01811076 A EP01811076 A EP 01811076A EP 01811076 A EP01811076 A EP 01811076A EP 1213538 B1 EP1213538 B1 EP 1213538B1
Authority
EP
European Patent Office
Prior art keywords
exhaust gas
helmholtz resonator
gas system
helmholtz
chimney
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.)
Expired - Lifetime
Application number
EP01811076A
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German (de)
English (en)
Other versions
EP1213538A2 (fr
EP1213538A3 (fr
Inventor
Günter Kudernatsch
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.)
General Electric Technology GmbH
Original Assignee
Alstom Technology 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 Alstom Technology AG filed Critical Alstom Technology AG
Publication of EP1213538A2 publication Critical patent/EP1213538A2/fr
Publication of EP1213538A3 publication Critical patent/EP1213538A3/fr
Application granted granted Critical
Publication of EP1213538B1 publication Critical patent/EP1213538B1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23J—REMOVAL OR TREATMENT OF COMBUSTION PRODUCTS OR COMBUSTION RESIDUES; FLUES 
    • F23J13/00—Fittings for chimneys or flues 
    • 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
    • F01D25/30—Exhaust heads, chambers, or the like
    • 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
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2260/00—Function
    • F05D2260/96—Preventing, counteracting or reducing vibration or noise
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23J—REMOVAL OR TREATMENT OF COMBUSTION PRODUCTS OR COMBUSTION RESIDUES; FLUES 
    • F23J2900/00—Special arrangements for conducting or purifying combustion fumes; Treatment of fumes or ashes
    • F23J2900/13003—Means for reducing the noise in smoke conducing ducts or systems

Definitions

  • the invention relates to an exhaust system for industrial gas turbines with an exhaust pipe and an adjoining fireplace, according to the preamble of claim 1.
  • absorption silencers have been incorporated into the exhaust gas system of the gas turbine plants, as mentioned, for example, in DE-A1-44 19 604 and DE-A1-40 09 072. This is intended to reduce the low-frequency noise at the place where its radiation into the environment takes place. But while sound in the high and medium frequency range can be absorbed relatively well with absorption silencers, low-frequency noise is difficult to control, since conventional silencers show only low sound attenuation at low frequencies. To be able to reduce the low-frequency noise, therefore, large absorption silencers with insulating mats of up to 800mm thickness must be installed in the exhaust system of the plants. This increases the footprint of the exhaust system, possibly reduces their performance due to pressure drop in the system and is also very expensive to install and maintain. The exhaust system is very expensive.
  • the object of the invention is therefore to provide an exhaust system of the type mentioned, are efficiently reduced in the low-frequency noise emissions without the performance of the system is significantly impaired and is also easy and economical to install and Watung.
  • a Helmholtz resonator is acoustically coupled to the flow channel.
  • the Helmholtz resonator is exactly tuned to the low frequency that is to be damped. It takes up less space than an absorption silencer.
  • the installation of a Helmholtz resonator is very simple and its durability at high flow rate in relation to absorption silencers much higher.
  • the use of Helmholtz resonators causes no reduction in performance of the system. For these reasons, the exhaust system can be installed and maintained more easily and the entire system can be operated more economically.
  • the Helmholtz resonator is arranged with its inlet opening in the range of a maximum pressure of an acoustic mode in the exhaust system, its efficiency is greatest
  • the Helmholtz resonator it is very advantageous to arrange the Helmholtz resonator in the transition region between the exhaust duct and the chimney, since there are usually hardly any space problems. It is particularly advantageous to provide the Helmholtz resonator on the rear wall of the chimney which delimits the exhaust gas channel in the flow direction, since this allows a particularly simple assembly.
  • the dimensions of the exhaust duct and the chimney are selected so that a pressure maximum of the acoustic mode occurs in the transition regions between the exhaust duct and the chimney. In this way, the Helmholtz resonator, as described above, can be mounted very easily and is also extremely efficient.
  • a heat insulation of the Helmholtz resonator to the outside ensures an approximately constant temperature of the Helmholtz resonator and thus a frequency stability of its absorption properties.
  • the Helmholtz resonator has a neck which is adjustable in its length and / or its cross section, the Helmholtz resonator can be better adjusted to the frequencies to be absorbed.
  • the Helmholtz resonator has an adjustable volume. This also provides a simple possibility of adaptation to the frequencies to be absorbed.
  • the adjustable volume can be realized very simply by making the height of the side walls adjustable by means of a sliding floor.
  • the temperature of the Helmholtz resonator is adjustable, it can be particularly easily adapted to the frequency to be absorbed.
  • the adjustability of the temperature can be realized, for example, simply by attaching heating elements to the outer walls of the Helmholtz resonator.
  • Another cost-effective option is to make the Helmholtz resonator flow around, so that either hot exhaust gases are diverted from the exhaust system for temperature regulation and passed to the outer walls of the Helmholtz resonator or the same is flowed around with cold air.
  • the Helmholtz resonator is acoustically transparent shielded from the flow in the flow channel. This allows a better sound absorption of the Helmholtz resonator.
  • a shield can be implemented very simply and expediently by means of an absorption silencer arranged between the inlet opening of the Helmholtz resonator and the flow.
  • an absorption silencer which has approximately the following structure: A first hole cover is part of a wall bounding the flow channel. A flow-resistant fabric arranged on the side of the hole covering facing away from the flow passage and a layer of damping material adjoin this first hole cover. This is followed by a second hole cover on the side facing away from the flow passage. Laterally, the absorption silencer is comprised of sidewalls. Such an absorption silencer has a good load capacity adjacent to a flow channel with high flow velocities.
  • Helmholtz resonators in the exhaust system. These may then be located at different locations in the exhaust system, e.g. in each case where maxima of the sound modes occur. They can also be tuned to different, low frequencies and thus contribute to an even more effective reduction of low-frequency noise. For this they can be arranged at different locations of the exhaust system or also close to each other. To ensure good sound absorption, however, the Helmholtz resonators should be separated from each other in a gas-tight manner.
  • FIG. 1 shows the sketch of an exhaust system 10 for a gas turbine plant (not shown) with an exhaust passage 12 and a chimney 14.
  • the exhaust passage 12 and the chimney 14 together form a flow channel 16.
  • the flow direction of the exhaust gas 18 in the flow channel 16 is indicated by arrows S.
  • a transition region 20 between the exhaust duct 12 and the chimney 14 the exhaust duct 12 is bounded by a rear wall 22 of the chimney 14 in its flow direction S.
  • a Helmholtz resonator 24 is arranged on the rear wall 22 of the chimney 14.
  • the Helmholtz resonator 24 is shielded by the flow in the flow channel 16 through a hole cover 26, which forms part of the rear wall 22 of the chimney 14, and arranged behind the hole cover 26 from the flow channel 16, acoustically transparent tissue.
  • the exhaust gas channel 12 and the chimney 14 are dimensioned such that a pressure maximum of a sound mode lies in the transition region 20 or in the inlet region 30 of the Helmholtz resonator 24.
  • the Helmholtz resonator 24 is thermally insulated to the outside so that it assumes an approximately constant temperature during operation.
  • absorption mufflers 32 are arranged to sound in the range of high and to absorb medium frequencies.
  • the Helmholtz resonator 24 As indicated by dashed lines in Fig. 1, it is possible to the Helmholtz resonator 24 at other locations of the exhaust system 10 or even several Helmholtz resonators 24, 24 ', 24 ", ... to arrange at different locations of the exhaust system 10. In order to achieve good sound absorption efficiency, the Helmholtz resonator or resonators 24, 24 ', 24 ",... Should be arranged in the exhaust system 10 where a pressure maximum of a sound mode lies.
  • FIGS. 2 and 3 a portion of an exhaust system 10 is shown in various views, in which three Helmholtz resonators 24, 24 ', 24 "are arranged side by side in the transition region 20 between the exhaust duct 12 and the chimney 14 on the rear wall 22 of the chimney 14
  • the exhaust gas channel 12 and the chimney 14 are in turn dimensioned such that the maximum pressure of a sound mode lies in the transition region 20 or in the inlet region 30 of the Helmholtz resonators 24, 24 ', 24 ".
  • an intermediate wall 38 is arranged in the hollow cylinder 34, which encloses a gap 44 together with the absorption silencer 36.
  • the hollow cylinder 34 is closed by a bottom 40 against the outside gas-tight. The entire hollow cylinder 34 and the bottom 40 are thermally insulated from the outside, so that the hollow cylinder 34 assumes approximately the temperature in operation, which prevails in the flow channel 16.
  • the absorption silencer 36 has essentially the usual structure: Against the flow channel 16 of the absorption silencer 36 is delimited by a hole cover 26, which forms part of the rear wall 22 of the chimney 14.
  • the hole cover 26 is backed with a flow resistant and wear resistant fabric 28 that is acoustically transparent, such as a metal mesh.
  • the layer 28 is followed on the fabric 28 by a layer of damping material 46, which can be constructed in one or more layers adapted to the frequency range to be absorbed. The material and the thickness of the damping material 46 are determined as required.
  • a further hole cover 48 is arranged against the gap 44 through a further hole cover 48 arranged.
  • the jacket of the hollow cylinder 34 also forms the side walls for the absorption silencer 36.
  • the remaining between the intermediate wall 38 and the bottom 40 cavity of the hollow cylinder 34 is divided by means of walls 42 into three sectors, which form the volumes 25, 25 ', 25 "of the three Helmholtz resonators 24, 24', 24".
  • the walls 42 close off the Helmholtz resonators 24, 24 ', 24 "in a gastight manner against each other.
  • Each Helmholtz resonator 24, 24', 24" is acoustically connected to the one between the two through a tubular neck 47, which is guided through the intermediate wall 38 connected upstream absorption silencer 36 and the intermediate wall 38 intermediate space 44.
  • Low-frequency sound that is not absorbed by the absorption silencer 36 is conducted into the gap 44 and further into the three Helmholtz resonators 24, 24 ', 24 ".
  • the number and shape of the Helmholtz resonators 24, 24', 24" shown here can be changed as needed.
  • a Helmholtz resonator 24, two, three, four, or even more resonators 24, 24 ', 24 ", ... can be arranged side by side, and the shape can also vary as desired
  • one or more Helmholtz resonators 24, 24 ', 24 ",... can be arranged next to one another at other locations of the exhaust system 10 as well.
  • the three Helmholtz resonators 24, 24 ', 24 "by means of adjustable in length and / or in cross-section necks 47 and by means of an adjustable volume 25, 25', 25" set to slightly different, low frequencies , which preferably also differ from the frequency which is attenuated in the intermediate space 44. In this way, the low-frequency noise can be reduced with high efficiency.
  • FIG. 4 shows in section the principle of an adaptable Helmholtz resonator 24a.
  • the neck 47a has two tubes 50, 52 inserted into one another. But it can also be chosen any other cross-sectional shapes.
  • the outer tube 50 with the larger diameter is firmly anchored in the intermediate wall 30. It may be welded to the intermediate wall 30, for example.
  • the outer tube 50 has on its inside, in its two end regions in each case on circular discs, radially inwardly extending projections 54. Between the projections 54, a seal 56 is arranged, which comprises the inner tube 52 with the slightly smaller diameter gas-tight.
  • the inner tube 52 is concentric in the outer tube 50 and slidably mounted against the resistance of the seal 56.
  • the inner tube 52 has radially outwardly bent ends 53 which, brought into abutment with the projections 54, prevent the inner tube 52 from being pulled too far out of the outer tube 50.
  • the neck 47a of the Helmholtz resonator 24a is slidable in length.
  • An adjustability of the neck diameter can be established, for example, by forming the neck with a polygonal cross-section and by pivoting the side walls of the polygon towards one another.
  • the volume 25a of the Helmholtz resonator 24a is adjustable by means of height-adjustable side walls 58.
  • the height of the side walls 58 is variable by means of a sliding floor 60.
  • the displaceable bottom 60 is cup-shaped and comprises a bottom plate 62 and of this approximately perpendicular protruding bottom walls 64 which engage around the side walls 58 of the Helmholtz resonator 24a side.
  • the bottom walls 64 are bent radially inwardly. Distanced from the bent ends 66, a radially inwardly extending collar 68 is provided on the bottom walls 64.
  • a bottom seal 70 is arranged, which comprises the side walls 58 of the Helmholtz resonator 24 a gas-tight.
  • the side walls 58 have on their the bottom 60 side facing radially outwardly bent edges 72, which can be brought into abutment with the collar 68, and thus prevent the bottom of the side walls 58 of the Helmholtz resonator 24a is deductible.
  • the volume 25a of the Helmholtz resonator 24a is thus in the context of the displacement of the bottom 60 from the stop of the bottom plate 62 to the edges 72 of the side walls 58 up to stop the edges 72 of the side walls 58 with the collar 68 of the bottom walls 64 adjustable.
  • the Helmholtz resonator 24a can be adjusted very precisely to the frequency to be damped by the adjustable neck 47a and the adjustable volume 25a.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Exhaust Silencers (AREA)
  • Soundproofing, Sound Blocking, And Sound Damping (AREA)
  • Chimneys And Flues (AREA)

Claims (11)

  1. Système de gaz d'échappement pour turbines à gaz industrielles comprenant une conduite de gaz d'échappement (12) et une cheminée (14) s'y raccordant, qui forment conjointement un canal d'écoulement continu (16), et comprenant un dispositif de réduction du bruit, caractérisé en ce que pour l'atténuation des basses fréquences du bruit, on prévoit un résonateur de Helmholtz (24, 24', 24", 24a) qui est disposé avec sa zone d'entrée (30) dans la plage d'un maximum de pression d'un mode acoustique dans cette plage de fréquences.
  2. Système de gaz d'échappement selon la revendication 1, caractérisé en ce que les dimensions du canal de gaz d'échappement (12) et de la cheminée (14) sont choisies de telle sorte que le maximum de pression du mode acoustique se produise dans la zone de transition (20) entre le canal de gaz d'échappement (12) et la cheminée (14).
  3. Système de gaz d'échappement selon l'une quelconque des revendications 1 ou 2, caractérisé en ce que le résonateur de Helmholtz (24, 24', 24", 24a) est disposé dans la zone de transition (20) entre le canal de gaz d'échappement (12) et la cheminée (14), et ce de préférence sur la paroi arrière (22) de la cheminée (14) adjacente au canal de gaz d'échappement (12) dans la direction de l'écoulement (s).
  4. Système de gaz d'échappement selon l'une quelconque des revendications précédentes, caractérisé en ce que le résonateur de Helmholtz (24, 24', 24", 24a) est isolé thermiquement par rapport à l'extérieur.
  5. Système de gaz d'échappement selon l'une quelconque des revendications précédentes, caractérisé en ce que le résonateur de Helmholtz (24, 24', 24", 24a) présente un col (47, 47a) qui est réglable en longueur et/ou en section transversale, et/ou en ce que le résonateur de Helmholtz (24, 24', 24", 24a) présente un volume (25, 25', 25", 25a) qui est réglable, et ce de préférence en ajustant la hauteur de ses parois latérales (58) au moyen d'un fond coulissant (40, 60).
  6. Système de gaz d'échappement selon l'une quelconque des revendications précédentes, caractérisé en ce que la température du résonateur de Helmholtz (24) est ajustable.
  7. Système de gaz d'échappement selon l'une quelconque des revendications précédentes, caractérisé en ce que la zone d'entrée (30) du résonateur de Helmholtz (24, 24', 24", 24a) est protégée de manière acoustiquement transparente contre l'écoulement dans le canal d'écoulement (16), et ce de préférence au moyen d'un silencieux d'absorption (36) disposé entre le col (47, 47a) du résonateur de Helmholtz (24, 24', 24", 24a) et l'écoulement (S).
  8. Système de gaz d'échappement selon la revendication 7, caractérisé en ce que le silencieux d'absorption (36) présente un premier recouvrement perforé (26) qui forme de préférence une partie d'une paroi (22) limitant le canal d'écoulement (16), et en ce qu'il comprend un tissu (28) résistant à l'écoulement, disposé du côté du recouvrement perforé (26) opposé au canal d'écoulement (16), une couche de matériau d'atténuation (46) adjacente au tissu (28) et un deuxième recouvrement perforé (48) opposé au premier recouvrement perforé (26) ainsi que des parois latérales.
  9. Système de gaz d'échappement selon la revendication 7 ou 8, caractérisé en ce que l'on prévoit entre le silencieux d'absorption (36) et le col (47, 47a) du résonateur de Helmholtz (24, 24', 24", 24a) un espace intermédiaire (44).
  10. Système de gaz d'échappement selon l'une quelconque des revendications précédentes, caractérisé en ce que l'on prévoit plusieurs résonateurs de Helmholtz (24, 24', 24", 24a) qui sont de préférence ajustés à différentes fréquences ou différents modes.
  11. Système de gaz d'échappement selon la revendication 10, caractérisé en ce que les résonateurs de Helmholtz (24, 24', 24", 24a) sont séparés les uns des autres de manière étanche aux gaz.
EP01811076A 2000-12-08 2001-11-08 Dispositif pour gaz d'échappement comprenant un résonateur de Helmholtz Expired - Lifetime EP1213538B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH20002400 2000-12-08
CH24002000 2000-12-08

Publications (3)

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EP1213538A2 EP1213538A2 (fr) 2002-06-12
EP1213538A3 EP1213538A3 (fr) 2002-07-31
EP1213538B1 true EP1213538B1 (fr) 2006-09-06

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US (1) US6705428B2 (fr)
EP (1) EP1213538B1 (fr)
DE (1) DE50110932D1 (fr)

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GB9522724D0 (en) * 1995-11-06 1996-01-10 Acts Ltd A noise attenuator for an induction system or an exhaust system
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EP0974788B1 (fr) 1998-07-23 2014-11-26 Alstom Technology Ltd Dispositif d'atténuation adaptée de bruit dans une turbomachine

Also Published As

Publication number Publication date
US20020108810A1 (en) 2002-08-15
EP1213538A2 (fr) 2002-06-12
EP1213538A3 (fr) 2002-07-31
DE50110932D1 (de) 2006-10-19
US6705428B2 (en) 2004-03-16

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