EP2623732A1 - Anlage und Verfahren zur Dämpfung akustischer Schwingungen bei einer entsprechenden Anlage - Google Patents

Anlage und Verfahren zur Dämpfung akustischer Schwingungen bei einer entsprechenden Anlage Download PDF

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Publication number
EP2623732A1
EP2623732A1 EP12153621.3A EP12153621A EP2623732A1 EP 2623732 A1 EP2623732 A1 EP 2623732A1 EP 12153621 A EP12153621 A EP 12153621A EP 2623732 A1 EP2623732 A1 EP 2623732A1
Authority
EP
European Patent Office
Prior art keywords
plant
resonance
steam turbine
pipeline
resonance 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Withdrawn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
EP12153621.3A
Other languages
German (de)
English (en)
French (fr)
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 EP12153621.3A priority Critical patent/EP2623732A1/de
Priority to PCT/EP2012/071999 priority patent/WO2013113417A2/de
Priority to CN201280069012.9A priority patent/CN104093943B/zh
Priority to EP12786933.7A priority patent/EP2795074A2/de
Priority to US14/373,663 priority patent/US20150016951A1/en
Priority to JP2014555099A priority patent/JP5911975B2/ja
Publication of EP2623732A1 publication Critical patent/EP2623732A1/de
Withdrawn legal-status Critical Current

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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 a system, in particular a power plant, comprising a steam turbine and a diverter for bypassing a working medium for the steam turbine around the steam turbine as needed.
  • the invention further relates to a method for damping acoustic vibrations in a corresponding system.
  • a bypass station is also typically provided for the diversion of a working medium for the steam turbine around the steam turbine as required.
  • 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 issuing 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 comprises a steam turbine and a bypass station for the diversion of a working medium for the steam turbine around the steam turbine as required, at least one resonance absorber being provided for the bypass station.
  • 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 those skilled in the art and are used in various technical fields for manipulating the sound emission of devices or the acoustics in rooms. Accordingly, extensive data and empirical values are available, based on which an adaptation of such a Helmholtz resonator to the conditions of the system can be realized with reduced technical effort.
  • the structure of the assembly of pipe and resonance absorber is thus substantially cylindrically symmetrical, the manufacturing cost of a corresponding assembly is kept low.
  • bypass station comprises a pipeline and in which the resonance absorber is essentially formed by a chamber positioned next to the pipeline, which is conductively connected 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 resonant frequency is preferably carried out by varying the volume of a resonator of the Helmholtz resonator, for example, by 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 typically formed by an absorption material such as mineral wool or stainless steel wool, which is introduced into at least one resonance body of at least one resonance absorber.
  • the resonance absorber is positioned between a coolant injection and a condenser, since experience has shown that sound generation takes place in this region.
  • the resonance absorber is preferably arranged at the location of the highest sound pressure.
  • 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. Due to the temperature of the resonator body given for this uniform boundary conditions and consequently also given by the geometry of the resonator body natural frequency spectrum. In exactly this frequency spectrum then takes place the attenuation of the sound emission by the resonance absorber.
  • 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 piping system for the working medium before the cooling medium injection. The removal takes place here in particular with the help of a simple spur line, so that the effort to realize the tempering system is at a very low level.
  • the resonance body for draining condensate has drainage openings.
  • This variant is particularly advantageous if water vapor is used as the working medium, since in this case it can be assumed that otherwise condensate would accumulate in the resonance bodies, whereby the damping characteristic of the resonance absorber would gradually deteriorate.
  • the plant 2 is part of a power plant for generating electrical energy and includes for this purpose a steam generator 4, a condenser 6, a steam turbine 8, a bypass station 10 and a substantially constructed of piping line system 12, which the individual aforementioned assemblies connects and which is used for the management of a working medium, here water and water vapor.
  • a working medium here water and water vapor.
  • conduit system 12 for the water or water vapor, wherein in a load operation, the steam is passed through the steam turbine 8 and wherein in a no-load operation, the steam is passed through the bypass station 10.
  • FIG. 2 A very expedient design variant of the diverter station 10 is in FIG. 2 shown in the manner of a block diagram.
  • the diversion station 10 is constructed from a conduit 14, which is connected to the conduit system 12 via a controllable diverter valve 16.
  • Downstream of the diverter valve 16 is a water injection 18, which is used if necessary for cooling the water vapor flowing through the conduit 14.
  • the steam 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 into the bypass station 10, which, as in FIG. 3 indicated by way of example of three along the conduit 14 juxtaposed Helmholtz resonators 22 is constructed.
  • Each Helmholtz resonator 22 is formed by a hollow cylindrical resonance body or an at least partially circumferential resonant chamber, which is conductively connected to the conduit 14 via a plurality of elongated holes 24 distributed over the circumference of the conduit 14.
  • at least one drainage opening 26 is provided, via which a condensate accumulating in the resonance chamber can flow with gravity support.
  • FIG. 4 An alternative embodiment of the resonance absorber 20 is shown in FIG. 4 shown.
  • 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, as in FIG. 4 indicated designed as a controllable Helmholtz resonator 22, in which the resonant frequency or rather the resonant frequency spectrum is adjustable.
  • the volume of the resonance chamber is varied by a change in position of a punch 30 with the aid of a controlled electric motor 32.
  • the resonance absorber 20 can on the other hand fine tune the structural conditions of Appendix 2 on the one hand and the current operating conditions.
  • water vapor if necessary with the aid of a controllable pump 34, is introduced into the resonance chamber of the Helmholtz resonator 22, wherein the corresponding water vapor is taken from the conduit 14 via a branch line 36 at a position in front of the water injection 18.
  • the walls of the Helmholtz resonator 22 are tempered with relatively little technical effort such that a uniform temperature for the entire Helmholtz resonator 22 is given and the penetration of steam / water mixture or steam with possibly changing temperature is prevented in the resonator.

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)
EP12153621.3A 2012-02-02 2012-02-02 Anlage und Verfahren zur Dämpfung akustischer Schwingungen bei einer entsprechenden Anlage Withdrawn EP2623732A1 (de)

Priority Applications (6)

Application Number Priority Date Filing Date Title
EP12153621.3A EP2623732A1 (de) 2012-02-02 2012-02-02 Anlage und Verfahren zur Dämpfung akustischer Schwingungen bei einer entsprechenden Anlage
PCT/EP2012/071999 WO2013113417A2 (de) 2012-02-02 2012-11-07 Anlage und verfahren zur dämpfung akustischer schwingungen bei einer entsprechenden anlage
CN201280069012.9A CN104093943B (zh) 2012-02-02 2012-11-07 设施和用于衰减相应的设施中的声振动的方法
EP12786933.7A EP2795074A2 (de) 2012-02-02 2012-11-07 Anlage und verfahren zur dämpfung akustischer schwingungen bei einer entsprechenden anlage
US14/373,663 US20150016951A1 (en) 2012-02-02 2012-11-07 Plant and method for damping acoustic vibrations in a corresponding plant
JP2014555099A JP5911975B2 (ja) 2012-02-02 2012-11-07 対応するプラント内で音響振動を減衰させるためのプラント及び方法

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP12153621.3A EP2623732A1 (de) 2012-02-02 2012-02-02 Anlage und Verfahren zur Dämpfung akustischer Schwingungen bei einer entsprechenden Anlage

Publications (1)

Publication Number Publication Date
EP2623732A1 true EP2623732A1 (de) 2013-08-07

Family

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Family Applications (2)

Application Number Title Priority Date Filing Date
EP12153621.3A Withdrawn EP2623732A1 (de) 2012-02-02 2012-02-02 Anlage und Verfahren zur Dämpfung akustischer Schwingungen bei einer entsprechenden Anlage
EP12786933.7A Withdrawn EP2795074A2 (de) 2012-02-02 2012-11-07 Anlage und verfahren zur dämpfung akustischer schwingungen bei einer entsprechenden anlage

Family Applications After (1)

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EP12786933.7A Withdrawn EP2795074A2 (de) 2012-02-02 2012-11-07 Anlage und verfahren zur dämpfung akustischer schwingungen bei einer entsprechenden anlage

Country Status (5)

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

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2924245A1 (en) * 2014-03-24 2015-09-30 Alstom Technology Ltd Steam turbine with resonance chamber

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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

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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
US20110005237A1 (en) * 2007-07-27 2011-01-13 Utc Power Corporation Oil removal from a turbine of an organic rankine cycle (orc) system

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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
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US20110005237A1 (en) * 2007-07-27 2011-01-13 Utc Power Corporation Oil removal from a turbine of an organic rankine cycle (orc) system
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

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2924245A1 (en) * 2014-03-24 2015-09-30 Alstom Technology Ltd Steam turbine with resonance chamber
US9920628B2 (en) 2014-03-24 2018-03-20 General Electric Technology Gmbh Steam turbine with resonance chamber

Also Published As

Publication number Publication date
JP5911975B2 (ja) 2016-04-27
JP2015505589A (ja) 2015-02-23
US20150016951A1 (en) 2015-01-15
EP2795074A2 (de) 2014-10-29
WO2013113417A3 (de) 2014-03-20
WO2013113417A2 (de) 2013-08-08
CN104093943A (zh) 2014-10-08
CN104093943B (zh) 2016-06-15

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