EP1559874A1 - Diffuseur et turbine - Google Patents

Diffuseur et turbine Download PDF

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Publication number
EP1559874A1
EP1559874A1 EP04002250A EP04002250A EP1559874A1 EP 1559874 A1 EP1559874 A1 EP 1559874A1 EP 04002250 A EP04002250 A EP 04002250A EP 04002250 A EP04002250 A EP 04002250A EP 1559874 A1 EP1559874 A1 EP 1559874A1
Authority
EP
European Patent Office
Prior art keywords
diffuser
helmholtz
resonator
housing
turbine
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
Application number
EP04002250A
Other languages
German (de)
English (en)
Other versions
EP1559874B1 (fr
Inventor
Heinrich Dr. Stüer
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
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Filing date
Publication date
Application filed by Siemens AG filed Critical Siemens AG
Priority to EP20040002250 priority Critical patent/EP1559874B1/fr
Publication of EP1559874A1 publication Critical patent/EP1559874A1/fr
Application granted granted Critical
Publication of EP1559874B1 publication Critical patent/EP1559874B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F01D25/30—Exhaust heads, chambers, or the like
    • 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
    • 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
    • F05D2260/962—Preventing, counteracting or reducing vibration or noise by means of "anti-noise"

Definitions

  • the invention relates to a diffuser with a housing, the extending in the axial direction along a flow, and that for the expansion of the flow in an axial Flow direction widening flow channel circumferentially limited.
  • the invention also relates to a turbine.
  • a turbine looks to drive one with a blading provided turbine rotor under high temperature and Pressure working medium, which flows against the blading and above that its kinetic energy to the turbine rotor releases, with the working fluid relaxes.
  • Steam is used as a working medium in a steam turbine goes through the following cycle. Behind the exit of the Turbine and before the introduction of the working medium in the condenser the relaxed working fluid is fed to a diffuser, to the necessary for a capacitor pressure and Adjust temperature conditions in the working medium.
  • the condensate is fed to a steam generator, which is the steam in a superheater at pressures in the range of 300 bar and temperatures in the range of 600 ° C brings to the working medium then in turn in this form the Supply steam turbine.
  • a steam generator which is the steam in a superheater at pressures in the range of 300 bar and temperatures in the range of 600 ° C brings to the working medium then in turn in this form the Supply steam turbine.
  • Desirable would be a diffuser in which a self-excited Vibration instability is largely avoided.
  • the invention begins, whose task it is to provide a diffuser and a turbine in which the Danger of self-excited vibration instability possible is low.
  • the invention is based on the consideration that a diffuser, especially when operated at high flow velocities is an above-mentioned self-excited vibration instability in the form of the so-called Diffusorbrummens have can. It has been shown that the frequency of the diffuser drone typically in the acoustic range. Usually, such a frequency has a spectrum, that usually frequency-dependent pressure transmission behavior reflected by the diffuser. It has It has now been shown that in the case of a diffuser, a frequency spectrum which, although with some drawbacks, surprisingly shows a main responsible frequency which, surprisingly, is also relatively constant. Ie.
  • a Helmholtz resonator on the housing of the diffuser is attached, the damping frequency to a natural frequency the diffuser is tuned.
  • a diffuser of the above type is in principle for every kind of a turbine, in particular for any type of steam turbine suitable.
  • a specialist makes a difference thereby between a high-pressure, a medium-pressure and a low-pressure steam turbine, which is mainly in terms of the temperature and pressure properties of the working medium differ.
  • the skilled person is one known as e-part turbine, which is a combination of a Medium-pressure and a low-pressure turbine represents, d. H.
  • the blading of this turbine is in a first part of the Rotor on a flow medium at medium pressure and in one second part of the rotor to a flow medium at low Pressure designed.
  • K sub-turbine whose blading in a first Part of the rotor on a flow medium at high pressure and in a second part on a medium flow medium Pressure is designed.
  • the above mentioned hum may, depending on the nature of such a steam turbine, for a Differentiate the diffuser of the above kind, especially in terms of their amplitude, there inevitably such a diffuser with working medium acted upon at different speeds becomes. In essence, the natural frequency of the Type of diffuser dependent.
  • a diffuser will especially at low pressure turbines with very high speeds applied.
  • a low-pressure turbine will usually with steam entering the low-pressure turbine a pressure at about 8 bar and a temperature at about 250 ° C, and at the exit substantially as saturated steam at a temperature of about 30 ° C and Press in the range of 0.05 to 0.1 bar, operated. This causes the diffuser hum in this type of Low-pressure steam turbine is particularly pronounced. This This leads to other components of the low-pressure steam turbine be stimulated by the diffuser hum, what the self-excited vibration instability on important components the turbine, z. B.
  • a Helmholtz resonator according to various Embodiments be formed.
  • the Helmholtz resonator in the form of a Helmholtz bottle.
  • the housing a or more, so a number of Helmholtz bottles of the mentioned Art, in particular more than two, has.
  • the Helmholtz resonator in Be executed form of an annular Helmholtz tube.
  • the Helmholtz tube extends along a circumference of the housing. It can do that Helmholtz tube completely enclose the housing. It can also be beneficial, a Helmholtz tube only at one Part of the housing circumference to install.
  • a Helmholtz resonator also attached in the form of a slit-shaped Helmholtz opening his.
  • a Helmholtz opening of the aforementioned type has the Dissipation of vibrational energy leading and thus dampening Effect of a Helmholtz resonator. Similar to the Helmholtz tube proves to be particularly appropriate, the slit-shaped Helmholtz opening along a circumference of the housing to install.
  • the Helmholtz resonator in particular the Helmholtz resonator according to the above-explained three Embodiments, a resonator cavity and a resonator neck assigned.
  • the resonator neck corresponds the bottleneck and the resonator space the bottle body.
  • the Helmholtz tube corresponds to the resonator neck ultimately the slot dimension of the Helmholtz tube and the resonator chamber the pipe volume located behind it.
  • the above slot-shaped Helmholtz opening corresponds the resonator neck substantially the slot dimension and the resonator space substantially corresponds to behind the slot effective volume as the damping volume.
  • a volume the resonator space and / or a length and / or a cross section the resonator neck for tuning the damping frequency individually or in combination is variably adjustable.
  • a volume of the resonator cavity can be in different ways be dimensioned and beyond by appropriate Measures are made variable adjustable. The same applies to the length of the resonator neck and the cross section a resonator neck.
  • the adjustment of the dimensions of the Resonatorraums and the Resonatorhalses, in particular for the above three embodiments, can either be one Helmholtz resonator with a fixed damping frequency, or, with variable adjustment, to a Helmholtz resonator with a variably adjustable damping frequency.
  • the Helmholtz resonator it has proved to be particularly advantageous to the Helmholtz resonator to attach to the housing circumference, so that there a resonator neck forms an opening to the flow channel.
  • the opening at one point of the housing circumference arranged with a position of an acoustic Pressure belly in the diffuser corresponds.
  • the diffuser with a detachable attachment to the To provide housing. Ie.
  • the diffuser is replaceable attached to the housing. This way you can Diffuser of the type mentioned later easily for servicing be installed or replaced.
  • a hum behavior of a diffuser can change, either a Helmholtz resonator with fixed Damping frequency replaced or a Helmholtz resonator be adjusted with variable attenuation frequency.
  • a Helmholtz resonator of the type mentioned prevent can be used to stimulate endangered natural frequencies of blades that are acoustically above the above Mechanism to be stimulated to avoid. In this way can be any, in a turbine for a self-excited Vibration instability at resonance endangered Shovel steps or shovel protect.
  • the invention also leads to a turbine with a diffuser for receiving a flow, wherein according to the invention the diffuser executed according to one of the above developments is. It has proved to be particularly advantageous, a Turbine in the form of a low-pressure turbine with a diffuser to provide according to one of the above developments.
  • the low-pressure steam turbine (LP steam turbine) 1 has a rotor 3, the with a number of blade stages 5, and in particular a last blade stage 7, is provided.
  • the blade stages 5.7 engage between vane stages 9, and a last vane stage 10, which on a housing 11 of the ND steam turbine are provided.
  • a flow M of a working medium flows through a, surrounding the rotor 3 and with the blade stages 5, 7, 9, 10 provided flow channel 13.
  • the flow channel opens into a further flow channel 15 of an output side end of the LP steam turbine. 1 mounted diffuser 17.
  • the diffuser 17 has a housing 19 on, extending in the axial direction along a flow M 'of the working medium in the diffuser 17 extends.
  • the housing 19 limits itself to the expansion of the flow M 'a in the axial direction 21 widening flow channel 15 circumferentially.
  • the frequency is diffuser drift typically in the range at 32 to 35 hertz. This is especially the case for half-speed Turbines.
  • Half-speed turbines run at half grid frequency - ie at 25 Hz.
  • an associated generator then different accordingly wrapped, namely usually 4-pin.
  • a turbine plant with a half-turn turbine and a diffuser is typical designed for relatively large mass flows M, M 'and is mainly used in a nuclear power plant.
  • the ripple frequency is, especially in the above range, relatively constant. This leads to the consideration that such a relatively constant frequency is particularly effective manner with a Helmholtz resonator 23a, 23b, 23c which can be suppressed in the one shown in FIG 1a, 1b, 1c Embodiment attached to the housing 19 of the diffuser 17 is.
  • the Helmholtz resonator shown in FIG. 1a is in the form of a Helmholtz bottle 23a is executed and will be explained in detail below explained. Additionally or alternatively to a Helmholtz bottle 23a can also be attached to a housing 19 in FIG. 1b shown Helmholtz resonator in the form of an annular, slotted Helmholtz tube 23b or in the form of a in FIG 1c shown Helmholtz opening 23 c are arranged.
  • the Helmholtz tube 23b is formed as a circumferentially circumferential tube. He can, similar to a Helmholtz bottle 23a, a resonator neck 35 and a resonator 37 associated his.
  • the Helmholtz opening 23c is designed as a circumferential, rectangular tube formed, which is a box-like Cross section has. He can, like one Helmholtz bottle 23a a strongly shortened resonator neck 35, in the form of a slot, and associated with a resonator 37 his.
  • the ripple frequency is in the range between 32 and 35 Hertz lies.
  • This frequency is usually in Range of a rotational frequency of a blading.
  • the Doppler frequency i. H. the Sum of hum and frequency
  • a last blade stage 7 can lie and thus immediately the reliability of an above mentioned ND turbine 1 can endanger.
  • the excitation of the last blade stage 7 caused by acoustic waves caused by a shock-barrier interaction is caused.
  • a diffuser 17 for an ND turbine 1 is the damping frequency the diffuser so advantageous to a frequency between 32 and 35 Hertz as the natural frequency of the diffuser 17th Voted. This has the advantage of being one with one Helmholtz resonator 23a, 23b, 23c equipped diffuser 17th the reliability of the above last blade stage 7 and thus the reliability of the entire LP turbine 1 not at risk.
  • the attenuation of the diffuser drone proves as particularly important, since in the one shown in FIG Embodiment of a LP steam turbine 1, the Doppler frequency the ripple frequency, d. H. a sum of hum and Rotational frequency of the rotor 3 in the range 60 to 65 hertz is and thus dangerously close to a natural frequency of last blade stage 7 approaches.
  • the Doppler frequency the ripple frequency, d. H. a sum of hum and Rotational frequency of the rotor 3 in the range 60 to 65 hertz is and thus dangerously close to a natural frequency of last blade stage 7 approaches.
  • the last blade stage 7 or the last vane stage 10 or a single Shovel thereof closest to the diffuser 17, to be affected could be affected.
  • This is available via the Helmholtz resonator 23a, 23b, 23c Asked damping mechanism has an integral Dämpfungshack, which reduces the pressure amplitudes so far that the Excitation of a last blade stage, and in particular a blade in the blade stage 7, prevented is and thus the reliability of the last blade stage 7 and the LP turbine 1 is guaranteed.
  • the position 25 of the Helmholtz resonator 23a, 23b, 23c at the housing periphery 27 of the diffuser 17 is schematically illustrated in FIG.
  • the execution of the Helmholtz resonator as a Helmholtz bottle 23a is explained in FIG.
  • FIG 2 is a schematic of the course of a pressure amplitude along the flow direction 22 of the flow M 'at the in 1 shown diffuser 17 indicated.
  • the Course of the pressure amplitude much more complicated. This can be used as part of complex simulations, depending on the geometry of the diffuser 17 and in dependence the flow parameters of the flow M, M 'are simulated or measured.
  • the acoustic Pressure curve 29 along the flow direction 22 in the diffuser 17 usually has pressure maxima and pressure minima, which are locally limited and possibly also over the cross section of the diffuser 17 can change.
  • a maximum pressure is shown in the present case as a pressure abdomen 31, 31 '.
  • a pressure minimum of the pressure amplitude 29 is present as Print nodes 33, 33 ', 33' 'shown.
  • pressure curve 29 representative of a Pressure curve along the axial direction 21 of FIG 1
  • the then the flow direction 22 would correspond.
  • the pressure profile 29 shown in FIG. 2 is also representative of a pressure curve along the housing circumference 27 of the diffuser 17 be.
  • the flow direction 22 would then correspond to one Measure along a suitable direction of the housing circumference 27th in the FIG 2.
  • the flow direction 22 could also along a housing boundary from the entrance to the outlet of the diffuser 17 gone.
  • the Helmholtz resonator shown in FIG. 1a is in the form of a Helmholtz bottle 23 a executed, the resonator neck 35th and a resonator volume 37.
  • An opening 39 of the resonator neck 35 is present at a location 25 of the housing periphery 27 arranged with a position of an acoustic Pressure belly 31 in the diffuser 17 corresponds. To this This is because the energy can be at the natural frequency the diffuser 17 as effectively as possible to the Helmholtz bottle 23 a via the opening 39 of the Resonatorhalses 35 couple and transferred to the Helmholtz bottle 23a - in the result so dampen.
  • a first Helmholtz resonator 23a, 23b, 23c is preferably a second and are possibly several more Helmholtz resonators 23a, 23b, 23c relative to the first Helmholtz resonator on a pressure belly or possibly the other pressure bellies 31, 31 'arranged.
  • FIG 3 schematically shows the structure of the one shown in FIG 1a Helmholtz resonator in the form of a Helmholtz bottle 23a.
  • This has a resonator chamber 37 and a resonator neck 35 on.
  • the resonator 37 can be assigned a volume V.
  • the resonator neck may have a length L and a cross section A be assigned.
  • the damping frequency can be the Helmholtz bottle 23a as an example of a Helmholtz resonator 23a, 23b, 23c advantageous to the natural frequency of the diffuser 17 vote.
  • An exemplary statement about the damping frequency can be z.
  • a turbine in particular in a steam turbine 1 or at a diffuser 17 with a housing 19 extending in the axial Direction 21 along a flow M 'extends, and the Widening of the flow M 'one in the axial direction 21st widening flow channel 15 circumferentially limited, sees that new concept that on the housing 19 a Helmholtz resonator 23a, 23b, 23c is mounted, the attenuation frequency on a natural frequency of the diffuser 17 is tuned.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Soundproofing, Sound Blocking, And Sound Damping (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)
EP20040002250 2004-02-02 2004-02-02 Diffuseur et turbine Expired - Lifetime EP1559874B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP20040002250 EP1559874B1 (fr) 2004-02-02 2004-02-02 Diffuseur et turbine

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP20040002250 EP1559874B1 (fr) 2004-02-02 2004-02-02 Diffuseur et turbine

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EP1559874A1 true EP1559874A1 (fr) 2005-08-03
EP1559874B1 EP1559874B1 (fr) 2013-07-31

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Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2010014127A1 (fr) * 2008-07-28 2010-02-04 Siemens Energy, Inc. Appareil diffuseur dans une turbomachine
US8061961B2 (en) * 2009-01-23 2011-11-22 Dresser-Rand Company Fluid expansion device and method with noise attenuation
US8955643B2 (en) 2011-04-20 2015-02-17 Dresser-Rand Company Multi-degree of freedom resonator array
US20150267538A1 (en) * 2014-03-24 2015-09-24 Alstom Technology Ltd Steam turbine with resonance chamber
FR3142509A1 (fr) * 2022-11-25 2024-05-31 Safran Helicopter Engines Turbomoteur comprenant un echangeur de chaleur et un attenuateur acoustique

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5431018A (en) * 1992-07-03 1995-07-11 Abb Research Ltd. Secondary burner having a through-flow helmholtz resonator
US6370879B1 (en) * 1998-11-10 2002-04-16 Alstom Damping device for reducing the vibration amplitude of acoustic waves for a burner
US20020108810A1 (en) * 2000-12-08 2002-08-15 Gunter Kudernatsch Exhaust gas system with helmholtz resonator

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5431018A (en) * 1992-07-03 1995-07-11 Abb Research Ltd. Secondary burner having a through-flow helmholtz resonator
US6370879B1 (en) * 1998-11-10 2002-04-16 Alstom Damping device for reducing the vibration amplitude of acoustic waves for a burner
US20020108810A1 (en) * 2000-12-08 2002-08-15 Gunter Kudernatsch Exhaust gas system with helmholtz resonator

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2010014127A1 (fr) * 2008-07-28 2010-02-04 Siemens Energy, Inc. Appareil diffuseur dans une turbomachine
US8313286B2 (en) 2008-07-28 2012-11-20 Siemens Energy, Inc. Diffuser apparatus in a turbomachine
EP2674575A1 (fr) * 2008-07-28 2013-12-18 Siemens Energy, Inc. Appareil diffuseur dans une turbomachine
EP2674574A1 (fr) * 2008-07-28 2013-12-18 Siemens Energy, Inc. Appareil diffuseur dans une turbomachine
US8061961B2 (en) * 2009-01-23 2011-11-22 Dresser-Rand Company Fluid expansion device and method with noise attenuation
US8955643B2 (en) 2011-04-20 2015-02-17 Dresser-Rand Company Multi-degree of freedom resonator array
US20150267538A1 (en) * 2014-03-24 2015-09-24 Alstom Technology Ltd Steam turbine with resonance chamber
CN104948243A (zh) * 2014-03-24 2015-09-30 阿尔斯通技术有限公司 具有共振腔的蒸汽涡轮
EP2924245A1 (fr) * 2014-03-24 2015-09-30 Alstom Technology Ltd Turbine à vapeur avec chambre de résonance
JP2015183693A (ja) * 2014-03-24 2015-10-22 アルストム テクノロジー リミテッドＡＬＳＴＯＭ Ｔｅｃｈｎｏｌｏｇｙ Ｌｔｄ 共振チャンバを備える蒸気タービン
US9920628B2 (en) 2014-03-24 2018-03-20 General Electric Technology Gmbh Steam turbine with resonance chamber
CN104948243B (zh) * 2014-03-24 2019-03-08 通用电器技术有限公司 具有共振腔的蒸汽涡轮
FR3142509A1 (fr) * 2022-11-25 2024-05-31 Safran Helicopter Engines Turbomoteur comprenant un echangeur de chaleur et un attenuateur acoustique

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Publication number Publication date
EP1559874B1 (fr) 2013-07-31

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