EP1559874B1 - Diffuseur et turbine - Google Patents

Diffuseur et turbine Download PDF

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Publication number
EP1559874B1
EP1559874B1 EP20040002250 EP04002250A EP1559874B1 EP 1559874 B1 EP1559874 B1 EP 1559874B1 EP 20040002250 EP20040002250 EP 20040002250 EP 04002250 A EP04002250 A EP 04002250A EP 1559874 B1 EP1559874 B1 EP 1559874B1
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.)
Expired - Lifetime
Application number
EP20040002250
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German (de)
English (en)
Other versions
EP1559874A1 (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
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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 which extends in the axial direction along a flow, and which limits the expansion of the flow circumferentially in the axial flow direction flow channel.
  • the invention also relates to a turbine.
  • a turbine provides for driving a provided with a blading turbine rotor in front of a high temperature and pressure working medium, which flows against the blading and above it emits its kinetic energy to the turbine rotor, which relaxes the working fluid.
  • steam is used as the working medium, which undergoes the following cycle. Behind the outlet of the turbine and before the introduction of the working medium into the condenser, the expanded working medium is fed to a diffuser in order to set the pressure and temperature conditions necessary for a condenser in the working medium.
  • the condensate is fed to a steam generator, which brings the steam in a superheater to pressures in the range of 300 bar and temperatures in the range of 600 ° C, to then supply the working medium in this form again the steam turbine.
  • excitation frequencies can arise in the acoustic range, which are transmitted to the turbine and its components, in particular a diffuser.
  • This can lead to self-excited vibration instabilities in a turbine and in particular a diffuser.
  • Such self-excited vibration instabilities depend on a large number of parameters, which relate, in particular, to the excitation frequency and amplitude in the working medium and to the operating parameters of the working medium.
  • the transmission behavior of all components in the turbine as a feedback loop of importance.
  • the invention begins, whose task is to provide a diffuser and a turbine, in which the risk of self-excited vibration instability is minimized.
  • a Helmholtz resonator is mounted on the housing, the damping frequency is tuned to a natural frequency of the diffuser, wherein the Helmholtz resonator is in the form of a Helmholtz bottle and the Housing a plurality, that is, a number of Helmholtz bottles of the type mentioned, in particular more than two, wherein the Helmholtz resonator is designed in the form of an annular Helmholtz tube, wherein the Helmholtz tube along a circumference of the housing extends, wherein the Helmholtz resonator is mounted in the form of a slot-shaped Helmholtz opening.
  • the invention is based on the consideration that a diffuser, in particular if it is operated at high flow velocities, can have an abovementioned self-excited oscillation instability in the form of the so-called diffuser drone. It has been shown that the frequency of the diffuser hum is typically in the acoustic range. Usually, such a frequency has a spectrum that reflects the usually frequency-dependent pressure transmission behavior of the perfused through the diffuser. It has now been found that, in the case of a diffuser, a frequency spectrum occurs which, surprisingly, shows a main responsible frequency, albeit with certain drawbacks, which, moreover, is surprisingly relatively constant. Ie.
  • a diffuser drumming is relatively constant, regardless of the fluidic loading of the diffuser with working medium is.
  • the invention is therefore based on the consideration that a diffuser drone is mainly determined by parameters which relate to the diffuser as such.
  • the housing of the diffuser a Helmholtz resonator is mounted, the damping frequency is tuned to a natural frequency of the diffuser ,
  • a diffuser of the type mentioned above is in principle suitable for any type of turbine, in particular for each type of steam turbine.
  • a person skilled in the art distinguishes between a high-pressure, a medium-pressure and a low-pressure steam turbine, which differ, above all, with regard to the temperature and pressure characteristics of the working medium.
  • E-part turbine represents a combination of a medium-pressure and a low-pressure turbine, ie the blading of this turbine is in a first part of the rotor to a flow medium medium pressure and in a second part of the rotor designed a flow medium at low pressure.
  • K-part turbine whose blading in a first Part of the rotor is designed for a flow medium at high pressure and in a second part to a flow medium at medium pressure.
  • the above-mentioned ripple frequency may differ, in particular in terms of its amplitude, for a diffuser of the above type, since such a diffuser is necessarily subjected to working medium at different speeds.
  • the natural frequency depends on the design of the diffuser. It has been found that the above-mentioned diffuser dribble occurs particularly in a diffuser for a low-pressure steam turbine. A diffuser is subjected to particularly high speeds, especially in low-pressure turbines.
  • a low-pressure turbine is usually with steam, which has a pressure at about 8 bar and a temperature at about 250 ° C when entering the low-pressure turbine, and at the outlet essentially as saturated steam at a temperature of about 30 ° C and pressures in the range from 0.05 to 0.1 bar, operated.
  • the diffuser hum is particularly pronounced in this type of low-pressure steam turbine. This leads to the fact that further components of the low-pressure steam turbine are excited by the diffuser hum, what the self-excited vibration instability on important components of the turbine, z. B. the blading, can transfer and then endanger the reliability of the turbine.
  • a new diffuser would have to be installed, which is typically performance-reducing.
  • a Helmholtz resonator may be formed according to various embodiments.
  • the Helmholtz tube can completely enclose the housing. It may also be advantageous to mount a Helmholtz tube only on a part of the housing periphery.
  • a Helmholtz aperture of the aforementioned type has the effect of a Helmholtz resonator leading to the dissipation of vibrational energy and thus attenuating effect. Similar to the Helmholtz tube, it proves to be particularly useful to attach the slot-shaped Helmholtz opening along a circumference of the housing.
  • a particularly advantageous combination proves to be a combination of the Helmholtz tube with a slot-shaped Helmholtz opening.
  • the Helmholtz resonator in particular the Helmholtz resonator according to the above-explained three embodiments, a resonator and a Resonatorhals is assigned.
  • the resonator neck corresponds to the bottleneck and the resonator chamber corresponds to the bottle body.
  • the resonator neck ultimately corresponds to the slot dimension of the Helmholtz tube and the resonator chamber corresponds to the tube volume located behind it.
  • the above slot-shaped Helmholtz opening corresponds the resonator neck substantially the slit dimension and the resonator chamber substantially corresponds to the effective volume behind the slot as a damping volume.
  • a volume of the resonator chamber and / or a length and / or a cross section of the resonator neck for tuning the damping frequency individually or in combination is variably adjustable.
  • a volume of the Resonatorraums can be dimensioned in different ways and also be made variably adjustable by appropriate measures. The same applies to the length of the resonator neck and the cross section of a resonator neck.
  • the adjustment of the dimensions of the resonator chamber and the resonator neck can lead either to a Helmholtz resonator with a fixed damping frequency or, with variable adjustment, to a Helmholtz resonator with a variably adjustable damping frequency.
  • the Helmholtz resonator mounts on the housing circumference, so that in this case a resonator neck forms an opening to the flow channel.
  • the opening is arranged at a position of the housing circumference, which corresponds to a position of an acoustic pressure belly in the diffuser.
  • the damping frequency of the Helmholtz resonator is particularly effectively coupled to the natural frequency of the diffuser, so that the present in the natural frequency of the diffuser vibration energy is effectively dissipated in the Helmholtz resonator and thus leads to a finite limitation of the diffuser drone in the case of resonance.
  • the diffuser has proven to be a particularly useful embodiment of the diffuser to provide the diffuser with a detachable attachment to the housing. Ie.
  • the diffuser is replaceable attached to the housing. In this way, a diffuser of the type mentioned can be easily retrofitted or replaced for servicing.
  • a ripple frequency behavior of a diffuser changes, either a Helmholtz resonator with fixed damping frequency can be replaced or a Helmholtz resonator with variable damping frequency can be adjusted.
  • the damping frequency of the Helmholtz resonator is tuned to a blade frequency. It has been shown that a Helmholtz resonator of the type mentioned can be used preventively to avoid an excitation of endangered natural frequencies of blades, which are acoustically excited by the above-mentioned mechanism. In this way, it is possible to protect any blade stage or blade that is at risk in a turbine for a self-excited vibration instability in the event of resonance.
  • a simple, fast and cost-effective solution for the Diffusorbrummproblem can be provided, which can also be retrofitted in case of service. It should be emphasized that the attachment of a Helmholtz resonator on a diffuser guarantees a performance of the diffuser, while in a previously customary and necessary replacement of a diffuser a performance penalty of the diffuser had to be taken into account, as a replaced diffuser usually not optimal on a turbine or a foreign machine is adjusted.
  • the invention also leads to a turbine with a diffuser for receiving a flow, wherein according to the invention, the diffuser is designed according to one of the above-mentioned developments. It has proven to be particularly advantageous to provide a turbine in the form of a low-pressure turbine with a diffuser according to one of the above-mentioned developments.
  • low-pressure steam turbine 1 can come to a self-excited vibration instability in the form of the so-called diffuser drone.
  • the low-pressure steam turbine (ND steam turbine) 1 has a rotor 3 which is provided 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 are provided on a housing 11 of the LP steam turbine.
  • a flow M of a working medium flows through a flow channel 13 surrounding the rotor 3 and provided with the blade stages 5, 7, 9, 10.
  • the flow channel opens into a further flow channel 15 of a diffuser 17 attached to the output end of the LP steam turbine 1.
  • the diffuser 17 has a housing 19 which extends in the axial direction along a flow M 'of the working medium in the diffuser 17.
  • the housing 19 delimits to widen the flow M 'in the axial direction 21 widening flow channel 15 circumferentially.
  • the frequency of the diffuser hum is typically in the range of 32 to 35 Hertz. This is especially the case for half-speed turbines.
  • Half-speed turbines run at half the grid frequency - ie at 25 Hz.
  • an associated generator is then wound differently, namely usually 4-pole.
  • a turbine system with a half-turn turbine and a diffuser is typically designed for relatively large mass flows M, M 'and is mainly used in a nuclear power plant.
  • FIG. 1a shown Helmholtz resonator is designed in the form of a Helmholtz bottle 23a and will be explained in detail below.
  • a housing 19 may also have an in FIG. 1b shown Helmholtz resonator in the form of an annular, slotted Helmholtz tube 23b or in the form of an in 1c shown Helmholtz opening 23 c are arranged.
  • the Helmholtz tube 23b is formed as a circumferentially circumferential tube. It can be associated with a resonator neck 35 and a resonator chamber 37, similar to a Helmholtz bottle 23a.
  • the Helmholtz opening 23 c is formed as a circumferentially circumferential, rectangular tube having a box-like cross-section. It can, similar to a Helmholtz bottle 23a, a strongly shortened resonator neck 35, be assigned in the form of a slot, and a resonator 37.
  • the ripple frequency lies in the range between 32 and 35 hertz. This frequency is usually in the range of a rotational frequency of a blading.
  • the Doppler frequency ie the sum of ripple frequency and rotational frequency, may be in the range of the natural frequency of a last rotor blade stage 7 and thus directly jeopardize the reliability of an above ND turbine 1.
  • the excitation of the last blade stage 7 by acoustic waves, which is caused by a shock-boundary layer interaction is caused by a shock-boundary layer interaction.
  • the damping frequency of the diffuser is thus advantageously matched to a frequency between 32 and 35 hertz as the natural frequency of the diffuser 17.
  • the attenuation of the diffuser drone proves to be particularly important since the in FIG. 1 shown embodiment, a ND steam turbine 1, the Doppler frequency of the hum, ie a sum of hum and rotational frequency of the rotor 3 in the range 60 to 65 Hertz and thus approaching dangerously close to a natural frequency of the last blade stage 7.
  • the Doppler frequency of the hum ie a sum of hum and rotational frequency of the rotor 3 in the range 60 to 65 Hertz and thus approaching dangerously close to a natural frequency of the last blade stage 7.
  • rotor blade stages 5 or vane stages 9 in particular the last blade stage 7 or the last vane stage 10 or a single vane thereof, which are closest to the diffuser 17 may be affected.
  • the ND Turbine 1 Due to the coincidence of said Doppler frequency with the natural frequency of the last blade stage 7, in particular with a natural frequency of a blade in the blade stage 7, it may cause a self-excited vibration instability due to this resonance case, thus directly the stability of the last blade stage 7 at risk and thus the reliability
  • the ND Turbine 1 The excitation of a blade in a blade stage 7 is performed by acoustic waves.
  • the acoustic wave is caused by a shock-boundary layer interaction.
  • This damping mechanism provided via the Helmholtz resonator 23a, 23b, 23c has an integral damping measure which reduces the pressure amplitudes to such an extent that the excitation of a last blade stage, and in particular of a blade in the blade stage 7, is prevented and thus the reliability of the last Rotor blade stage 7 and the LP turbine 1 is guaranteed.
  • FIG. 2 The position 25 of the Helmholtz resonator 23a, 23b, 23c on the housing circumference 27 of the diffuser 17 is in FIG. 2 schematically explained.
  • the design of the Helmholtz resonator as Helmholtz bottle 23a is in FIG. 3 explained.
  • FIG. 2 schematically is the course of a pressure amplitude along the flow direction 22 of the flow M 'in the in FIG. 1 shown diffuser 17 indicated.
  • the course of the pressure amplitude is much more complicated. This can be simulated or measured in the context of elaborate simulation calculations, depending on the geometry of the diffuser 17 and as a function of the flow parameters of the flow M, M '. It can be seen here that the acoustic pressure profile 29 along the flow direction 22 in the diffuser 17 generally has pressure maxima and pressure minima which are locally limited and may possibly also change over the cross section of the diffuser 17. A maximum pressure is shown in the present case as a pressure belly 31, 31 '.
  • a pressure minimum of the pressure amplitude 29 is shown here as a pressure node 33, 33 ', 33''.
  • the in FIG. 2 Pressure curve 29 shown representative of a pressure profile along the axial direction 21 of FIG. 1 , which would then correspond to the flow direction 22.
  • the in FIG. 2 shown pressure curve 29 also be representative of a pressure curve along the housing circumference 27 of the diffuser 17.
  • the flow direction 22 would then correspond to a dimension along a suitable direction of the housing circumference 27 in FIG FIG. 2 ,
  • the flow direction 22 could also run along a housing boundary from the entrance to the outlet of the diffuser 17.
  • a pressure curve such as that designated 29, also occurs in the circumferential direction, and especially in the form of a circumferentially on the housing circumference 27 rotating, standing wave.
  • a standing wave is practically anchored on the housing circumference 27 when a Helmholtz resonator is being installed.
  • the Helmholtz resonator shown is designed in the form of a Helmholtz bottle 23a, which has a resonator neck 35 and a resonator volume 37.
  • An opening 39 of the resonator neck 35 is presently arranged at a position 25 of the housing periphery 27, which corresponds to a position of an acoustic pressure belly 31 in the diffuser 17.
  • the energy at the natural frequency of the diffuser 17 can be coupled as effectively as possible to the Helmholtz bottle 23a via the opening 39 of the resonator neck 35 and transmitted to the Helmholtz bottle 23a - thus damping in the result.
  • a standing wave or a pressure curve 29 as explained above is generally anchored in practice by the installation of a first Helmholtz resonator 23a, 23b, 23c on the housing circumference 27 or on a housing boundary, is preferably a second and are If appropriate, a plurality of further Helmholtz resonators 23a, 23b, 23c relative to the first Helmholtz resonator on a pressure belly or possibly the other pressure bellies 31, 31 'are arranged.
  • FIG. 3 schematically shows the structure of in FIG. 1a shown Helmholtz resonator in the form of a Helmholtz bottle 23a.
  • This has a resonator chamber 37 and a resonator neck 35.
  • the resonator 37 can be assigned a volume V.
  • the resonator neck can be assigned a length L and a cross section A.
  • the damping frequency of the Helmholtz bottle 23a can advantageously be tuned to the natural frequency of the diffuser 17 as an example of a Helmholtz resonator 23a, 23b, 23c.
  • An exemplary statement about the damping frequency can be z.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)
  • Soundproofing, Sound Blocking, And Sound Damping (AREA)

Claims (9)

  1. Diffuseur (17) ayant un carter (19) qui s'étend dans une direction (21) axiale le long d'un écoulement (M') et qui, pour élargir l'écoulement (M'), délimite dans une grande mesure un canal (15) pour un écoulement s'élargissant dans la direction (21) axiale, dans lequel
    il est mis sur le carter (19) un résonateur (23a,23b,23c) d'Helmholtz dont la fréquence d'amortissement est accordée à une fréquence propre du diffuseur (17)
    caractérisé en ce que
    le résonateur d'Helmholtz est constitué sous la forme de l'un des modes de réalisation suivant :
    sous la forme d'une bouteille (23a) d'Helmholtz, la carter (19) ayant notamment un certain nombre de bouteilles (23a) d'Helmholtz ;
    sous la forme d'un tube (23b) d'Helmholtz annulaire fendu, le tube (23b) d'Helmholtz s'étendant le long du pourtour du carter (19) ;
    sous la forme d'une ouverture (23c) d'Helmholtz en forme de fente sur le carter (19) qui s'étend notamment le long du pourtour (17) du carter.
  2. Diffuseur (17) suivant la revendication 1,
    caractérisé en ce que
    le résonateur (23a,23b,23c) d'Helmholtz est associé à un espace (37) de résonateur et un col (35) de résonateur.
  3. Diffuseur (17) suivant l'une des revendications 1 à 2,
    caractérisé en ce que
    un volume (V) de l'espace (37)de résonateur, une longueur (L) et une section (A) transversale du col (35) de résonateur sont réglable de manière variable, individuellement ou en combinaison pour l'adaptation de la fréquence d'amortissement.
  4. Diffuseur (17) suivant l'une des revendications 1 à 3,
    caractérisé en ce que
    le résonateur (23a,23b,23c) d'Helmholtz est mis sur un pourtour (17) du carte de manière à ce qu'un col (35) de résonateur forme une ouverture (39) allant vers le canal (15) d'écoulement.
  5. Diffuseur (17) suivant l'une des revendications 1 à 4,
    caractérisé en ce que
    l'ouverture (39) est disposée en un point du pourtour (27) du carter, qui correspond à une position d'un vent (31,31',31") de pression acoustique dans le diffuseur (17).
  6. Diffuseur (17) suivant l'une des revendications 1 à 5,
    caractérisé en ce que
    il est mis de manière amovible sur le carter (19).
  7. Diffuseur (17) suivant l'une des revendications 1 à 6,
    caractérisé en ce que
    la fréquence d'amortissement est adaptée à une fréquence propre d'une aube.
  8. Turbine comprenant un diffuseur (17) suivant l'une des revendications précédentes pour la réception d'un écoulement (M').
  9. Turbine suivant la revendication 8 sous la forme d'une turbine (1) basse pression.
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

Publications (2)

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

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Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8313286B2 (en) 2008-07-28 2012-11-20 Siemens Energy, Inc. Diffuser apparatus in a turbomachine
US8061961B2 (en) * 2009-01-23 2011-11-22 Dresser-Rand Company Fluid expansion device and method with noise attenuation
EP2700068A4 (fr) 2011-04-20 2016-01-13 Dresser Rand Co Groupement de résonateurs à multiples degrés de liberté
EP2924245B1 (fr) * 2014-03-24 2017-03-01 General Electric Technology GmbH Turbine à vapeur avec chambre de résonance
FR3142509A1 (fr) * 2022-11-25 2024-05-31 Safran Helicopter Engines Turbomoteur comprenant un echangeur de chaleur et un attenuateur acoustique

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE59208193D1 (de) * 1992-07-03 1997-04-17 Abb Research Ltd Nachbrenner
DE19851636A1 (de) * 1998-11-10 2000-05-11 Asea Brown Boveri Dämpfungsvorrichtung zur Reduzierung der Schwingungsamplitude akustischer Wellen für einen Brenner
EP1213538B1 (fr) * 2000-12-08 2006-09-06 Alstom Technology Ltd Dispositif pour gaz d'échappement comprenant un résonateur de Helmholtz

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