EP2681454B1 - Silencieux à résonateur pour une turbomachine radiale, en particulier pour un compresseur radial - Google Patents

Silencieux à résonateur pour une turbomachine radiale, en particulier pour un compresseur radial Download PDF

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Publication number
EP2681454B1
EP2681454B1 EP12704743.9A EP12704743A EP2681454B1 EP 2681454 B1 EP2681454 B1 EP 2681454B1 EP 12704743 A EP12704743 A EP 12704743A EP 2681454 B1 EP2681454 B1 EP 2681454B1
Authority
EP
European Patent Office
Prior art keywords
radial
diffuser
circumferential groove
substantially annularly
annularly encircling
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.)
Not-in-force
Application number
EP12704743.9A
Other languages
German (de)
English (en)
Other versions
EP2681454A1 (fr
Inventor
Sven KÖNIG
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
Siemens Corp
Original Assignee
Siemens AG
Siemens Corp
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, Siemens Corp filed Critical Siemens AG
Publication of EP2681454A1 publication Critical patent/EP2681454A1/fr
Application granted granted Critical
Publication of EP2681454B1 publication Critical patent/EP2681454B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL-COMBUSTION ENGINES
    • F01N1/00—Silencing apparatus characterised by method of silencing
    • F01N1/02—Silencing apparatus characterised by method of silencing by using resonance
    • 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
    • F01D1/00—Non-positive-displacement machines or engines, e.g. steam turbines
    • F01D1/02—Non-positive-displacement machines or engines, e.g. steam turbines with stationary working-fluid guiding means and bladed or like rotor, e.g. multi-bladed impulse steam turbines
    • F01D1/06—Non-positive-displacement machines or engines, e.g. steam turbines with stationary working-fluid guiding means and bladed or like rotor, e.g. multi-bladed impulse steam turbines traversed by the working-fluid substantially radially
    • 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
    • F01D9/00—Stators
    • F01D9/02—Nozzles; Nozzle boxes; Stator blades; Guide conduits, e.g. individual nozzles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • F04D29/441—Fluid-guiding means, e.g. diffusers especially adapted for elastic fluid pumps
    • F04D29/444—Bladed diffusers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
    • F04D29/663—Sound attenuation
    • F04D29/665—Sound attenuation by means of resonance chambers or interference
    • 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
    • F05D2250/00—Geometry
    • F05D2250/50—Inlet or outlet
    • F05D2250/52—Outlet
    • 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

Definitions

  • the invention relates to a diffuser for a radial compressor, which diffuser has a substantially annular cavity, which is delimited at least by a first radial side surface.
  • Radial compressors are known, for example from the EP 1 356 168 B1 or the EP 1 602 810 A1 ,
  • DE 601 20769 T2 and US 2009/229280 A1 Diffusers shown have a circumferential groove, which is filled or covered with a material and so does not form a resonator.
  • the DE 601 14 484 T2 shows an empty circumferential groove in the diffuser.
  • Such radial compressors consist of a compressor stage forming, rotating about a rotation axis impeller with a - with respect to the axis of rotation of the impeller - axial inlet and a radial outlet. Gas to be compressed flows axially into the impeller of the compressor stage and is then deflected outwards (radial, radial seal), leaving the impeller at high speed.
  • Kinetic energy of the high-velocity gas to be compressed is then converted into potential energy in the form of pressure in a diffuser.
  • Such a diffuser is usually formed by two non-rotating, an annular cavity or an annular space forming rings, which annular space radially adjoins the impeller outlet and which rings or annular walls / side surface radially adjoin the impeller outlet Sense and perpendicular to the axis of rotation or to this at a very obtuse angle (radial annular space walls / radial side surfaces).
  • the gas exiting the impeller is guided radially outward in this annular space between these two annular walls and reaches a collector.
  • diffusers have wings, d. H. a blading, for steering and better control of the slowing down of the flow.
  • dominant sound sources in a centrifugal compressor are typically generated at the impeller and diffuser inlet or diffuser vanes due to the high velocity of the fluids flowing through these regions, as well as the interaction of rotor and stator components.
  • radial compressors produce at an outlet from the radial compressor (pressure side), for example at local pressure nozzles, complex, unsteady, three-dimensional, rotating and / or pulsating pressure fields or sound fields whose sound waves are undisturbed in the pipes connecting to the pressure nozzles spread.
  • Mufflers in general are devices for reducing noise emissions. Different types of silencers are distinguished, which reduce a generated sound power due to different mechanisms of action. For example, a distinction is made between absorption and reflection / resonator silencers.
  • An absorption silencer as for example from the EP 1 602 810 A1 is known for a radial compressor, contains porous (absorption) material, usually rock wool, glass wool or glass fiber, which partially absorbs sound energy, ie, converts into heat. Absorption in the muffler mainly dampens upper frequencies of the sound medium.
  • DE601 20769 T2 and US 2009/229280 A1 proposed.
  • the DE 601 14 484 T2 discloses a circumferential groove whose depth is increased to more than 1.5 times the axial width of the recessed portion of the compressor wheel.
  • Absorption mufflers have the disadvantage that they are usually unsuitable for high pressures, since - connected to the high pressures - high energy inputs act on the absorbent material or high heat inputs are absorbed by the absorbent material, resulting in damage to the porous material, as can lead to a dissolution of the absorbent material.
  • Resonator silencers or reflection silencers which use the principle of sound reflection, usually contain a plurality of cavities or chambers, past which the sound medium passes, which leads to reflections.
  • the multiple passages through the chambers of the chambers through the sound medium leads to a reduction of sound pressure peaks of different frequencies.
  • These reflections are - constructively - generated by baffles, cross-sectional widening and narrowing. By reflection, any frequencies of the sound medium can be damped in the muffler.
  • Such a resonator muffler, based on a Helmholtz resonator principle, for a centrifugal compressor is known from EP 1 356 168 B1 or from the EP 1 443 217 A2 known.
  • the local diffuser has an acoustic lining in the form of a field with numerous holes, which act as Helmholtz resonators on.
  • a radial compressor In addition to such a radial compressor is known as a further form of a radial flow machine, a radial turbine.
  • Such a radial turbine such as from the DE 44 38 611 C1 is known, based on a reversal of the physical principle of a centrifugal compressor and is accordingly - in the same components - as in a radial compressor - flows in the reverse flow direction as in this.
  • a radial turbine typically at the location of the impeller or a turbine wheel (both also referred to below as impeller) and a Turbinenleitkranzes upstream of the turbine or any Leitschranzschaufeln generated.
  • the object is achieved by a diffuser for a radial flow machine, in particular a centrifugal compressor, with the features according to the independent claim.
  • This diffuser has a substantially annular cavity, an annular space, which is bounded at least by a first radial side surface. According to the invention, at least one substantially annular circumferential groove is formed in this side surface.
  • This at least one substantially annular circumferential, groove open to the annular space acts as an acoustic resonator, in particular lambda / 4 - resonator - shortly hereinafter also only resonator - so that the groove passing sound waves, the same Have frequency as an (acoustic) Eigen- or Resonant frequency of this groove, reflected in a region of Nutausgangs and thus a sound propagation across the groove or the resonator away are reduced.
  • the sound propagation in the annular space can be reduced and an effective sound attenuation in the diffuser - and the radial flow machine or the radial compressor - can be achieved.
  • the substantially annular circumferential groove in particular by a depth of the groove, by a width / height of the groove or the Nutausgangs, by a radial position of the groove in the radial side surface, eigenform (eigenmode) or Knot diameter and natural or resonance frequency of the groove determined.
  • the configuration or the (three-dimensional) geometry of the circumferential groove - in itself - are so far no limits, as formed by the circumferential groove, a cavity or a cavity, which acts as an acoustic resonator.
  • circumferential grooves with any groove shapes such as circumferential grooves with a rectangular, V-shaped or trapezoidal cross-section, circumferential grooves with outwardly slanted wall and / or circumferential grooves as dovetail and / or circumferential grooves with - have area or completely - smooth and / or curved walls and / or circumferential grooves with undercuts and / or be realized with chambers. Wavy circumferential grooves or circumferential grooves with a stepped groove bottom are also possible.
  • a sound wave passing by the groove thus has the same eigenform or a same nodule diameter as a same acoustic eigenform in the resonator or the groove on and / or has the groove passing the groove sound wave at the same natural frequency as that of the groove, the reflection is particularly effective.
  • D. h. By suitable (three-dimensional) dimensioning of the groove, the natural acoustic frequency and the natural shape of the groove on a sound wave to be reflected, d. H. be tuned to their frequency and eigenform, and thus targeted frequencies - are attenuated by the dimensioning of the groove.
  • the shape of these passing acoustic pressure patterns can be estimated, for example, via analytical correlations, such as according to a formula according to Tyler & Sofrin.
  • the geometry of a circumferential groove is easy to manufacture and, due to the smaller number of free parameters such as height, width, depth, or shape, offers the possibility of integration into an optimization process.
  • the invention achieves a robust maintenance-free (sound damping) solution that is not subject to wear even at high pressures and temperatures. It offers a distinct advantage over absorption material based approaches.
  • the "muffler" according to the invention near the sound source (impeller and possibly bladed diffuser / possibly bladed Leitkranz) is used, with proper dimensioning Also, the excitation of the impeller can be reduced by acoustic pressure pattern.
  • the at least one first radial side surface has a plurality of essentially annular, in particular concentric, grooves lying on one another. Through several such circumferential grooves, the efficiency of the muffler can be increased.
  • circumferential grooves can be particularly preferably designed such that they each have different dimensions, in particular different depth and / or width. For example, it may be provided here that with a growing radial distance in the annular cavity or annular space to the outside, the depth and the width of the circumferential grooves are each smaller.
  • a frequency band to be damped of 700 Hertz - 2000 Hertz, 700 Hertz - 4000 Hertz or 700 Hertz - 6000 Hertz can be realized.
  • the efficiency of the "resonator muffler" can be further increased if the annular cavity is delimited by one of the first radial side surface axially opposite, second radial side surface, which second radial side surface also a substantially annular circumferential groove or - with further increase in efficiency - more having substantially annular circumferential, in particular concentric with each other, grooves.
  • the one substantially annular circumferential groove of the first radial side surface of a substantially annular circumferential groove of the second radial side surface directly, d. H. at the same radial height, axially opposite.
  • the one substantially annular circumferential groove of the first radial side surface of a substantially annular circumferential groove of the second radial side surface radially offset, d. H. with different radial height, opposite. This may be particularly advantageous if, due to arranged in the annular cavity or annulus elements, such as a blading, a place for a "directly axially opposite arrangement" of the circumferential grooves is not available.
  • Such a directly axially opposing arrangement as well as a radially offset arrangement of circumferential grooves can also be provided in each case with a plurality of essentially annular, concentric grooves in the two radial side surfaces. Again, the space conditions in the annulus (bladed annulus) may be crucial to provide instead of a "directly axially opposite arrangement" radially offset circumferential grooves.
  • the natural frequency of the at least one substantially annular circumferential groove is tuned to a frequency to be reflected. More preferably, the frequency to be reflected may be a blade passing frequency of a radial compressor or a second harmonic or third harmonic or fourth harmonic to the impeller revolution frequency of the centrifugal compressor.
  • the eigenform of the at least one substantially annular circumferential groove is tuned to the natural shape of a sound wave to be reflected.
  • the substantially annular cavity has a blading.
  • the at least one substantially annular circumferential groove or a plurality of such circumferential grooves is or are arranged in an area of the blading in the annular space.
  • the at least one substantially annular circumferential groove or a plurality of such circumferential grooves is arranged outside the region of the Beschauflung in annular space or are.
  • the at least one substantially annular circumferential groove has interruptions. This can be provided, for example, when the annular space has a blading, which prevents a completely circumferential groove.
  • the "(resonator) silencer" - as a local diffuser - is used or realized in a radial compressor.
  • the "silencer” can be used in a radial turbine at a turbine runner upstream of a turbine runner of the radial turbine or implemented there.
  • FIGS. 1 to 3 show various embodiments of centrifugal compressors 100, each with a resonator muffler 1 realized or integrated in the diffuser.
  • Such radial compressors 100 as shown have an impeller 10 which rotates about an axis 11 at high speed.
  • the impeller 10 has a hub 12 and radially projecting blades 13th
  • the hub 12 has a first region 12a that is substantially cylindrical, a transition region 12b in which the hub radius widens, and an end region 12c that is substantially perpendicular to the axis 11.
  • the - with flow direction 3 - axially flowing gas 2 is rotated by the impeller 10 in rotation and leaves the impeller 10 in the radial flow direction 3 to the axis 11 and at an obtuse angle to the axis eleventh
  • the blades 13 are attached to a common back plate 14 of the hub 12.
  • the impeller 10 is located in a housing 15 whose wall 16 is adapted to the outer contour of the impeller.
  • the fan formed by the impeller 10 has an axial inlet 17 and a radial outlet 18 extending around the circumference of the impeller 10.
  • the diffuser 20 connects, which is fixedly connected to the housing 15 and does not rotate.
  • the diffuser 20 has a substantially radial support wall 21, to which vanes 22 (diffuser blades) are attached, which guide the flow passing through the outlet 18.
  • the radial support wall of the diffuser 20 axially spaced opposite is another substantially radial wall 23, whereby the diffuser 20 forms an annular space occupied by the blading 22, the annular space 30.
  • the wings 22 extend substantially radially to the axis 11. Between the wings 22 diffuser channels are formed, the cross-sectional area increases from the inside to the outside.
  • the purpose of the diffuser 20 is to slow down the accelerated by the impeller 10 gas, which has a high kinetic energy and convert the kinetic energy in pressure.
  • piping system 29 pressure side 27
  • centrifugal compressors 100 as shown cause high levels of noise emissions that can (noise) affect an environment of the centrifugal compressor 100, vibration, structure-related malfunction, as well as pipe vibrations in / on piping systems can cause which pipe vibrations to damage to the pipes to failure of the Run radial compressor 100.
  • Dominant sound sources of such emissions are generated at the location of the impeller 10 and the diffuser inlet 25 or any diffuser vanes 22 due to the high velocity of the fluids flowing through these regions.
  • the radial compressors 100 - as shown in FIGS. 1 to 3 - each provide a resonator muffler 1 realized or integrated in the diffuser or in the annular space 30 there.
  • one or more circumferential annular grooves 50 extending annularly about the axis 11 in the radial support wall 21 and / or in the radial Wall 23 attached, which act as acoustic resonators, in particular as lambda / 4 - resonators.
  • These circumferential grooves 50 may also be arranged only in the region of the blading 22 of the diffuser or only in the region outside the blading 22 of the diffuser 20 and also in and outside the region of the blading 22 of the diffuser 20.
  • FIG. 1 shows an embodiment of this resonator muffler 1, which has two each concentric to the axis 11 annular circumferential grooves 50.
  • One of the two circumferential grooves 50 is arranged on the radial support wall 21. Approximately at the same radial distance from the axis 11, the second of the two circumferential grooves in the radial wall 23 is arranged. Both circumferential grooves 50, which are identical in shape, width and depth and have a U-shaped cross-section, are therefore directly, d. H. at the same radial height, axially opposite.
  • FIG. 2 shows a further embodiment of a resonator muffler 1 in the diffuser 20, which has a plurality each concentric with the axis 11 annular circumferential grooves 50.
  • a first part of these circumferential grooves 50 is arranged on the radial support wall 21 in the region of the blading 22 of the diffuser 20.
  • These circumferential grooves 50 directly axially, d. H. each at the same radial height or in each case the same radial distance from the axis 11, opposite a second part of the circumferential grooves 50, also four circumferential grooves 50, on the radial wall 23 - thus also in the bladed region 22 of the diffuser 20 and annulus 30 - arranged.
  • circumferential grooves 50 are identical in each case in shape, width and depth.
  • the width and the depth of the circumferential grooves 50 decrease with increasing distance from the axis 11.
  • the circumferential grooves 50 become narrower and less deep. All circumferential grooves 50 have a U-shaped cross-section.
  • FIG. 3 shows a further embodiment of a resonator muffler 1 in the diffuser 20 with also a plurality each concentric with the axis 11 annular circumferential grooves 50th
  • FIG. 3 are all circumferential grooves 50, here four circumferential grooves 50, concentric with each other and arranged concentrically to the axis 11 on the radial wall 23 in the region of the blading 22 of the diffuser 20.
  • the width and the depth of the circumferential grooves 50 decrease.
  • the circumferential grooves 50 narrower and narrower and less deep.
  • All circumferential grooves 50 here also have a U-shaped cross-section.
  • FIG. 4 shows an example of an acoustic eigenmode 60 in such acting as a resonator annular groove 50th
  • FIG. 4 shows 24 pressure maxima 61. Further, this eigen- or acoustic mode 60 is characterized by 12 so-called knot diameter 62 and a specific natural frequency. At the circumferential groove 50 passing sound waves, which are characterized by this natural frequency are reflected and the sound propagation over or past the circumferential groove 50 over.
  • the reflection process is particularly effective.
  • Such resonator silencers 1 as described have an extremely efficient effect, in particular because they are used close to the sound source, impeller 10 and (optionally bladed 22) diffuser 20, so that further elaborate soundproofing measures, in particular for the entire piping system 29 of the radial compressor 100, are dispensed with can.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Claims (10)

  1. Diffuseur ( 20 ) pour un compresseur ( 100 ) radial, lequel diffuseur ( 20 ) a une cavité ( 30 ) sensiblement annulaire qui est délimitée au moins par une première surface ( 21, 23 ) latérale radiale,
    caractérisé en ce que
    la au moins une première surface ( 21, 23 ) latérale radiale a au moins une rainure ( 50 ) périphérique vide, faisant sensiblement le tour annulairement et qui constitue un résonateur acoustique, une dimension de la au moins une rainure ( 50 ) périphérique vide, faisant sensiblement le tour annulairement, déterminant une fréquence propre et/ou une forme ( 60 ) propre de la rainure ( 50 ) périphérique vide, faisant sensiblement le tour annulairement et la fréquence propre et/ou la forme ( 60 ) propre de la au moins une rainure ( 50 ) périphérique vide, faisant sensiblement le tour annulairement étant accordée à une fréquence à réfléchir et/ou à une onde sonore à réfléchir.
  2. Diffuseur ( 20 ) suivant au moins l'une des revendications précédentes,
    caractérisé en ce que
    la au moins une première surface ( 21, 23 ) latérale radiale a plusieurs rainures ( 50 ) périphériques vides, faisant sensiblement le tour annulairement, notamment concentriques les unes aux autres, qui ont notamment respectivement des dimensions différentes, notamment des profondeurs différentes et/ou des largeurs différentes.
  3. Diffuseur ( 20 ) suivant au moins l'une des revendications précédentes,
    caractérisé en ce que
    la cavité ( 30 ) annulaire est délimitée par une deuxième surface ( 21, 23 ) latérale radiale opposée axialement à la première surface ( 21, 23 ) latérale radiale, laquelle deuxième surface ( 21, 23 ) latérale radiale a une rainure ( 50 ) périphérique vide, faisant sensiblement le tour annulairement ou plusieurs rainures ( 50 ) périphériques vides, concentriques les unes aux autres et faisant sensiblement le tour annulairement.
  4. Diffuseur ( 20 ) suivant au moins la revendication précédente,
    caractérisé en ce que
    la rainure ( 50 ) périphérique vide faisant sensiblement le tour annulairement de la première surface ( 21, 23 ) latérale radiale, est opposée en étant décalée axialement ou radialement à la une rainure ( 50 ) périphérique, vide et faisant sensiblement le tour annulairement, de la deuxième surface ( 21, 23 ) latérale radiale ou en ce que les plusieurs rainures ( 50 ) périphériques vides concentriques les unes aux autres et faisant sensiblement le tour annulairement de la première surface ( 21, 23 ) latérale radiale et plusieurs rainures ( 50 ) périphériques vides concentriques les unes aux autres et faisant sensiblement le tour annulairement de la deuxième surface ( 21, 23 ) latérale radiale sont opposées en étant décalées axialement ou radialement.
  5. Diffuseur ( 20 ) suivant au moins l'une des revendications précédentes,
    caractérisé en ce que
    la dimension déterminant la fréquence propre ou la forme propre est une largeur et/ou une profondeur et/ou une position radiale de la rainure ( 50 ) périphérique vide, faisant sensiblement le tour annulairement.
  6. Diffuseur ( 20 ) suivant au moins la revendication précédente,
    caractérisé en ce que
    la fréquence propre et/ou la forme ( 60 ) propre de la au moins une rainure ( 50 ) périphérique vide, faisant sensiblement le tour annulairement est accordée à une fréquence de passage de pale ( « blade passing frequency » ) du compresseur radial ou à un deuxième harmonique ou à un troisième harmonique ou à un quatrième harmonique de la fréquence de passage de pale du compresseur ( 100 ) radial.
  7. Diffuseur ( 20 ) suivant au moins l'une des revendications précédentes,
    caractérisé en ce que
    la cavité ( 30 ) sensiblement annulaire a un aubage ( 22 ).
  8. Diffuseur ( 20 ) suivant au moins la revendication précédente,
    caractérisé en ce que
    la au moins une rainure ( 60 ) vide, faisant sensiblement le tour annulairement ou chaque rainure ( 50 ) périphérique vide, faisant sensiblement le tour annulairement, est disposée dans une région de l'aubage ( 22 ) ou en ce que la au moins une rainure ( 50 ) périphérique vide, faisant sensiblement le tour annulairement ou chaque rainure ( 50 ) périphérique vide, faisant sensiblement le tour annulairement, est disposée en dehors de la région de l'aubage ( 22 ).
  9. Diffuseur ( 20 ) suivant au moins l'une des revendications précédentes,
    caractérisé en ce que
    la au moins une rainure ( 50 ) périphérique vide, faisant sensiblement le tour annulairement a des interruptions.
  10. Diffuseur ( 20 ) suivant au moins l'une des revendications précédentes, utilisé dans un compresseur ( 100 ) radial ou utilisé dans une turbine radiale pour une couronne directrice de turbine montée en amont d'une roue de la turbine radiale.
EP12704743.9A 2011-03-03 2012-02-09 Silencieux à résonateur pour une turbomachine radiale, en particulier pour un compresseur radial Not-in-force EP2681454B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102011005025A DE102011005025A1 (de) 2011-03-03 2011-03-03 Resonatorschalldämpfer für eine radiale Strömungsmaschine, insbesondere für einen Radialverdichter
PCT/EP2012/052160 WO2012116880A1 (fr) 2011-03-03 2012-02-09 Silencieux à résonateur pour une turbomachine radiale, en particulier pour un compresseur radial

Publications (2)

Publication Number Publication Date
EP2681454A1 EP2681454A1 (fr) 2014-01-08
EP2681454B1 true EP2681454B1 (fr) 2015-09-30

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP12704743.9A Not-in-force EP2681454B1 (fr) 2011-03-03 2012-02-09 Silencieux à résonateur pour une turbomachine radiale, en particulier pour un compresseur radial

Country Status (5)

Country Link
US (1) US9086002B2 (fr)
EP (1) EP2681454B1 (fr)
CN (1) CN103403359B (fr)
DE (1) DE102011005025A1 (fr)
WO (1) WO2012116880A1 (fr)

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CN102927052B (zh) * 2012-11-12 2015-03-04 西安交通大学 径向槽机匣处理方法
JP6349645B2 (ja) * 2013-08-06 2018-07-04 株式会社Ihi 遠心圧縮機及び多段圧縮装置
US9644639B2 (en) * 2014-01-27 2017-05-09 Pratt & Whitney Canada Corp. Shroud treatment for a centrifugal compressor
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CN103403359A (zh) 2013-11-20
DE102011005025A1 (de) 2012-09-06
US9086002B2 (en) 2015-07-21
CN103403359B (zh) 2016-12-14
WO2012116880A1 (fr) 2012-09-07
RU2013144381A (ru) 2015-04-10
EP2681454A1 (fr) 2014-01-08
US20140020975A1 (en) 2014-01-23

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