EP2795074A2 - Installation et procédé d'amortissement de vibrations acoustiques pour une installation correspondante - Google Patents

Installation et procédé d'amortissement de vibrations acoustiques pour une installation correspondante

Info

Publication number
EP2795074A2
EP2795074A2 EP12786933.7A EP12786933A EP2795074A2 EP 2795074 A2 EP2795074 A2 EP 2795074A2 EP 12786933 A EP12786933 A EP 12786933A EP 2795074 A2 EP2795074 A2 EP 2795074A2
Authority
EP
European Patent Office
Prior art keywords
plant
resonance
pipeline
steam turbine
absorber
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Withdrawn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
EP12786933.7A
Other languages
German (de)
English (en)
Inventor
Stephan Minuth
Peter Berenbrink
Frank Deidewig
Holger Gedanitz
Dirk Huckriede
Bernd Prade
Horst Uwe Rauh
Stephan Schestag
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 EP12786933.7A priority Critical patent/EP2795074A2/fr
Publication of EP2795074A2 publication Critical patent/EP2795074A2/fr
Withdrawn legal-status Critical Current

Links

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
    • F01D25/04—Antivibration arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K13/00—General layout or general methods of operation of complete plants
    • F01K13/006—Auxiliaries or details not otherwise provided for
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K27/00—Plants for converting heat or fluid energy into mechanical energy, not otherwise provided for
    • G—PHYSICS
    • G10—MUSICAL INSTRUMENTS; ACOUSTICS
    • G10K—SOUND-PRODUCING DEVICES; METHODS OR DEVICES FOR PROTECTING AGAINST, OR FOR DAMPING, NOISE OR OTHER ACOUSTIC WAVES IN GENERAL; ACOUSTICS NOT OTHERWISE PROVIDED FOR
    • G10K11/00—Methods or devices for transmitting, conducting or directing sound in general; Methods or devices for protecting against, or for damping, noise or other acoustic waves in general
    • G10K11/16—Methods or devices for protecting against, or for damping, noise or other acoustic waves in general
    • G10K11/172—Methods or devices for protecting against, or for damping, noise or other acoustic waves in general using resonance effects
    • 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
    • F05D2260/963—Preventing, counteracting or reducing vibration or noise by Helmholtz resonators

Definitions

  • the invention relates to an installation, in particular a motor ⁇ plant comprising a steam turbine and a bypass station as needed 'diversion of working medium for the steam turbine to the steam turbine.
  • the invention further relates to a method for damping acoustic vibrations in a corresponding system.
  • Steam turbines used it is also typically a Um ⁇ control station for the diversion of a working medium for the steam turbine around the steam turbine provided as needed.
  • a bypass station comprises a pipeline, with the aid of which the working medium is passed directly into a condenser instead of through the steam turbine.
  • the pressurized working fluid in the pipeline often generates low-frequency sound with a frequency between 125 Hz and 8 kHz, which is transmitted via the pipeline into the condenser.
  • the condenser acts like a loudspeaker, which emits the sound to the environment. This can not only lead to the annoyance of adjacent residential areas, but in the worst case to exceeding the permissible limits, which precludes granting the operating permit of the power plant.
  • the present invention seeks to provide a simpler solution for reducing the noise emission of power plants.
  • the plant is in particular a power plant for the generation of electrical energy or an assembly of a corresponding power plant.
  • the plant in this case comprises a steam turbine and a diverter for diverting needs ⁇ have a working medium for the steam turbine to the steam turbine around, wherein at least one resonance absorber is provided for the diverter.
  • Resonance absorbers as they are known in principle to those skilled in the art, are used primarily when it is expected that a sound emission with individual discrete frequencies or a few narrow frequency bands.
  • resonance absorbers are suitable for use in such installations with relative simple technical means to attenuate the noise emission frequency selective, so that the characteristic of the sound absorber modified by the modified sound emission is changed so far that on the one hand, the prescribed limits are exceeded and on the other hand noise pollution adjacent residential areas is avoided.
  • the resonance absorber is designed as a Helmholtz resonator.
  • Corresponding Helmholtz resonators are well known to the skilled person. Known and used in a variety of technical fields for manipulating the noise emission of devices or the acoustics in rooms. Accordingly, available to ⁇ sive data and experience, on the basis of an adaptation of such a Helmholtz resonator to the realities of the system with reduced technical complexity can be realized.
  • the construction of the construction ⁇ group of pipeline and resonance absorber is thus substantially cylindrically symmetrical, the manufacturing cost of a corresponding assembly is kept low.
  • a variant of the system is provided in which the bypass station comprises a pipeline and in which the resonance absorber is essentially formed by a chamber positioned next to the pipeline, which chamber is connected in a sound conducting manner to the pipeline via a resonator neck. This variant can be realized with a relatively ⁇ low technical effort.
  • an embodiment of the system is advantageous in which the Helmholtz resonator is designed as a controllable Helmholtz resonator, wherein the resonance frequency of the Helmholtz resonator is adjustable.
  • the adjustment of the resonance frequency is preferably carried out by varying the volume of a Helmholtz resonator Reso ⁇ nanz stresses of, by example, a piston is displaced in a cylinder.
  • the resonance absorber in the installed state on the system in which it is installed vote, so that according to the common parts principle for different systems, a single resonance absorber type can be used.
  • an embodiment of the system is expedient in which a plurality of resonance absorbers are provided for damping one frequency or one narrow frequency band.
  • the resonance absorbers are additionally coupled with absorption silencers, so that a specific damping behavior which is particularly well tuned to the respective installation is provided.
  • the absorption silencers are thereby formed typically by an absorbent material such as mineral wool or stainless steel wool ⁇ comprising at ⁇ least one resonance absorber is incorporated in at least one resonant body.
  • the resonance absorber between a cooling medium injection and a capacitor is positioned, as in this particular Be ⁇ experience has shown that the sound generation is rich.
  • the resonance absorber is preferably at the location of the highest
  • Another advantage is a variant of the system in which the resonance absorber has a resonator and wherein a tempering system is provided for the resonant body, with a substantially uniform temperature for the entire resonator is specified.
  • the resonance body to specify the uniform temperature is flowed through an additional supply line from the working fluid.
  • the working medium used to specify the uniform temperature for the resonant body is preferably taken from a position in the line system for the working medium before the cooling medium injection. The removal takes place here in particular dere with the help of a simple spur line, so that the effort to realize the tempering plant is at a very low level.
  • the resonance body for draining condensate has drainage openings. This variant is especially advantageous if as
  • FIG 1 in a block diagram representation of a bypass station with a resonance absorber
  • FIG 2 in a sectional view of the structure of the resonance absorber
  • FIG 3 shows a sectional view of an alternative diverter station with an alternative resonance absorber.
  • the On ⁇ position 2 is part of a power plant for generating electrical energy and for this purpose comprises a steam generator 4, a condenser 6, a steam turbine 8, a diverter 10 and a substantially constructed from piping management system 12, which comprises connects individual previously mentioned modules together and which is used to conduct a working ⁇ medium, here water and water vapor.
  • a working ⁇ medium here water and water vapor.
  • FIG 1 are given by the conduit system 12 for the water or the What ⁇ serdampf two possible routes, being passed in a load operation of the steam through the steam turbine 8 and wherein in a load-free operation of the water vapor through the diverter station 10 is headed.
  • FIG 2 A very expedient design variant of the Umleitsta ⁇ tion 10 is shown in FIG 2 in the manner of a block diagram Darge ⁇ represents. Constructed, the diverter station 10 from a Lei ⁇ processing pipe 14, which is connected via a controllable diverter valve 16 to the conduit system 12th By an appropriate control of the diverter valve 16, a Wech ⁇ sel between the two relevant here operating modes of the system 2, ie load operation and no-load operation, make so if necessary, the steam generated in the steam generator 4 instead of the steam turbine 8 through the Umleitsta ⁇ tion 10 and thus passed through the conduit 14. Downstream of the diverter valve 16 is a Wassereinsprit ⁇ tion 18, which is used if necessary for cooling the water vapor flowing through the conduit 14. After this
  • the water vapor is introduced into the condenser 6 and brought there for condensation. Finally, the water thus returned to the condenser 6 is subsequently returned to the steam generator 4 by means of a water pump.
  • a resonance absorber 20 is integrated, which as indicated in FIG 3 by way of example of three along the Lei ⁇ tung tube 14 arranged in a row Helmholtz resonators is constructed 22nd
  • Each Helmholtz resonator 22 is formed by a hollow-cylindrical resonating body or an at least partially circumferential resonance chamber, which is connected in a sound-conducting manner to the conduit 14 via a plurality of elongated holes 24 distributed over the circumference of the conduit 14.
  • each resonator chamber of the corresponding Helmholtz resonator 22 at least one drainage tion opening 26 is provided, via which a resulting in the resonance chamber condensate can flow with gravity support.
  • An alternative embodiment of the resonance absorber 20 is shown in FIG.
  • a single Helmholtz resonator 22 is provided with a single cylindrical resonance chamber, which is positioned between the water injection 18 and the condenser 6, as viewed in the flow direction of the steam, and is arranged next to the conduit 14.
  • the Helmholtz resonator 22 is in this embodiment via a single acting as a resonator neck 28 opening conductively connected to the conduit 14 sound conducting.
  • the Helmholtz resonator 22 is embodied as a controllable Helmholtz resonator 22 in which the resonant frequency or rather the resonant frequency spectrum can be set.
  • the volume of the resonance chamber is varied by a change in position of a stamp 30 by means of a controlled electric motor to ⁇ 32nd.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Multimedia (AREA)
  • Soundproofing, Sound Blocking, And Sound Damping (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
  • Control Of Turbines (AREA)

Abstract

L'invention concerne une installation (2), en particulier une centrale (2) comportant une turbine à vapeur (8) et une unité de dérivation (10) permettant de dévier, si nécessaire, un milieu de travail destiné la turbine à vapeur (8), autour de ladite turbine à vapeur (8), au moins un absorbeur de résonance (20) étant prévu pour l'unité de dérivation (10).
EP12786933.7A 2012-02-02 2012-11-07 Installation et procédé d'amortissement de vibrations acoustiques pour une installation correspondante Withdrawn EP2795074A2 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP12786933.7A EP2795074A2 (fr) 2012-02-02 2012-11-07 Installation et procédé d'amortissement de vibrations acoustiques pour une installation correspondante

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
EP12153621.3A EP2623732A1 (fr) 2012-02-02 2012-02-02 Installation et procédé destinés à amortir des vibrations acoustiques dans une installation associée
PCT/EP2012/071999 WO2013113417A2 (fr) 2012-02-02 2012-11-07 Installation et procédé d'amortissement de vibrations acoustiques pour une installation correspondante
EP12786933.7A EP2795074A2 (fr) 2012-02-02 2012-11-07 Installation et procédé d'amortissement de vibrations acoustiques pour une installation correspondante

Publications (1)

Publication Number Publication Date
EP2795074A2 true EP2795074A2 (fr) 2014-10-29

Family

ID=47178657

Family Applications (2)

Application Number Title Priority Date Filing Date
EP12153621.3A Withdrawn EP2623732A1 (fr) 2012-02-02 2012-02-02 Installation et procédé destinés à amortir des vibrations acoustiques dans une installation associée
EP12786933.7A Withdrawn EP2795074A2 (fr) 2012-02-02 2012-11-07 Installation et procédé d'amortissement de vibrations acoustiques pour une installation correspondante

Family Applications Before (1)

Application Number Title Priority Date Filing Date
EP12153621.3A Withdrawn EP2623732A1 (fr) 2012-02-02 2012-02-02 Installation et procédé destinés à amortir des vibrations acoustiques dans une installation associée

Country Status (5)

Country Link
US (1) US20150016951A1 (fr)
EP (2) EP2623732A1 (fr)
JP (1) JP5911975B2 (fr)
CN (1) CN104093943B (fr)
WO (1) WO2013113417A2 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2924245B1 (fr) * 2014-03-24 2017-03-01 General Electric Technology GmbH Turbine à vapeur avec chambre de résonance
JP7429488B2 (ja) 2020-05-19 2024-02-08 ダイハツ工業株式会社 車両のルーフ構造
CN113776724B (zh) * 2021-08-12 2024-05-14 中国船舶重工集团公司第七一九研究所 压力测量装置

Family Cites Families (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4979587A (en) * 1989-08-01 1990-12-25 The Boeing Company Jet engine noise suppressor
JPH0724595Y2 (ja) * 1990-04-25 1995-06-05 三菱重工業株式会社 複合プラントのバイパス煙突
JPH0710460U (ja) * 1993-07-22 1995-02-14 愛知機械工業株式会社 レゾネータ構造
DE4414232A1 (de) * 1994-04-23 1995-10-26 Abb Management Ag Vorrichtung zur Dämpfung von thermoakustischen Schwingungen in einer Brennkammer
JPH0861605A (ja) * 1994-08-26 1996-03-08 Mitsubishi Heavy Ind Ltd タービンバイパス蒸気温度制御装置
JP3209889B2 (ja) * 1995-07-04 2001-09-17 川崎重工業株式会社 ガスタービンシステムの排ガス逆流防止装置および排ガス逆流防止方法
JP4115021B2 (ja) * 1999-01-13 2008-07-09 株式会社大気社 消音装置
DE10026121A1 (de) * 2000-05-26 2001-11-29 Alstom Power Nv Vorrichtung zur Dämpfung akustischer Schwingungen in einer Brennkammer
EP1213538B1 (fr) * 2000-12-08 2006-09-06 Alstom Technology Ltd Dispositif pour gaz d'échappement comprenant un résonateur de Helmholtz
US7055324B2 (en) * 2003-03-12 2006-06-06 Fisher Controls International Llc Noise abatement device and method for air-cooled condensing systems
US7337875B2 (en) * 2004-06-28 2008-03-04 United Technologies Corporation High admittance acoustic liner
JP2006188996A (ja) * 2005-01-06 2006-07-20 Mitsubishi Heavy Ind Ltd 蒸気タービン施設の騒音低減装置
JP4469346B2 (ja) * 2006-02-28 2010-05-26 日立Ｇｅニュークリア・エナジー株式会社 沸騰水型原子炉
CA2694678C (fr) * 2007-07-27 2014-09-16 Utc Power Corporation Retrait d'huile d'une turbine d'un systeme a cycle de rankine organique (orc)
CN101713387A (zh) * 2008-10-07 2010-05-26 赵玉天 麦克斯韦妖热源与制冷与空调新概念
US8061961B2 (en) * 2009-01-23 2011-11-22 Dresser-Rand Company Fluid expansion device and method with noise attenuation
GEP20105105B (en) * 2009-04-01 2010-10-25 Device for protection against water hammer
FR2950112B1 (fr) * 2009-09-11 2011-10-07 Hutchinson Dispositif d'attenuation acoustique pour ligne d'admission d'un moteur thermique, et ligne d'admission l'incorporant

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2013113417A2 *

Also Published As

Publication number Publication date
JP5911975B2 (ja) 2016-04-27
JP2015505589A (ja) 2015-02-23
US20150016951A1 (en) 2015-01-15
WO2013113417A3 (fr) 2014-03-20
WO2013113417A2 (fr) 2013-08-08
CN104093943A (zh) 2014-10-08
CN104093943B (zh) 2016-06-15
EP2623732A1 (fr) 2013-08-07

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