EP1356169B1 - Zweischichtiger akustischer überzug und fluiddruckbeaufschlagungsvorrichtung - Google Patents

Zweischichtiger akustischer überzug und fluiddruckbeaufschlagungsvorrichtung Download PDF

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Publication number
EP1356169B1
EP1356169B1 EP01996188A EP01996188A EP1356169B1 EP 1356169 B1 EP1356169 B1 EP 1356169B1 EP 01996188 A EP01996188 A EP 01996188A EP 01996188 A EP01996188 A EP 01996188A EP 1356169 B1 EP1356169 B1 EP 1356169B1
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Prior art keywords
plate
openings
extending
chamber
wall
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EP01996188A
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English (en)
French (fr)
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EP1356169A1 (de
EP1356169A4 (de
Inventor
Zheji Liu
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Dresser Rand Co
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Dresser Rand Co
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Priority claimed from US09/745,862 external-priority patent/US6550574B2/en
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Publication of EP1356169A4 publication Critical patent/EP1356169A4/de
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Classifications

    • 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
    • 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
    • F04D29/4213—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps suction ports
    • 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
    • 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
    • F05D2250/00—Geometry
    • F05D2250/50—Inlet or outlet
    • F05D2250/51—Inlet
    • 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

Definitions

  • This invention relates to an acoustic liner of two layers and a fluid pressurizing device and method utilizing same.
  • Fluid pressurizing devices such as centrifugal compressors
  • centrifugal compressors are widely used in different industries for a variety of applications involving the compression, or pressurization, of a gas.
  • a typical compressor produces a relatively high noise level which is an obvious nuisance to the people in the vicinity of the device. This noise can also cause vibrations and structural failures.
  • the dominant noise source in a centrifugal compressor is typically generated at the locations of the impeller exit and the diffuser inlet, due to the high velocity of the fluid passing through these regions.
  • the noise level becomes higher when discharge vanes are installed in the diffuser to improve pressure recovery, due to the aerodynamic interaction between the impeller and the diffuser vanes.
  • acoustic liners have been developed which are placed in the compressors, or similar devices, for controlling noise inside the gas flow paths.
  • These liners are often based on the well-known Helmholtz resonator principle according to which the liners dissipate the acoustic energy when the sound waves oscillate through perforations in the liners, and reflect the acoustic energy upstream due to the local impedance mismatch caused by the liner.
  • Helmholtz resonators are disclosed in U.S. patent Nos. 4,100,993; 4,135,603; 4,150,732; 4,189,027; 4,443,751; 4,944,362; and 5.624,518.
  • a typical Helmholtz array acoustic liner is in the form of a three-piece sandwich structure consisting of honeycomb cells sandwiched between a perforated facing sheet and a back plate.
  • the perforated facing sheet becomes loose, it not only makes the acoustic liners no longer functional but also causes excessive aerodynamic losses, and even the possibility of mechanical catastrophic failure, caused by the potential collision between the break-away perforated sheet metal and the spinning impeller.
  • US Patent 442 1455 discloses an inlet duct lining that is generally tubular and formed of a plurality of separate, concentric layers. Specifically, the lining is formed of a radially innermost layer of a wire cloth, a second layer of a perforate metal sheet, a third layer of a metal honeycomb structure, and a radially-outermost layer of nonperforate back sheet.
  • the duct lining is disposed in a generally tubular air inlet of a centrifugal compressor of a combustion turbine engine (28).
  • US Patent 450 4188 teaches a pressure variation absorber for a centrifugal compressor formed of an annular or disk-like porous sheet of absorbing material attached to an annular structure that includes inner and outer end dividers and a disk-like backplate, such that an annular resonant cavity is bounded radially by the two end dividers and axially by the material sheet and backplate.
  • the resonant cavity is divided into a series of separate cavities by a single helical divider or plurality of concentric rings, and the separate cavities are filled with damping material such as fiberglass.
  • GB patent 1, 511,625 discloses a muffled axial flow ventilator that includes a motor, a rotor attached to the motor, a cowling surrounding the blades of the rotor and providing an inlet, and a muffler surrounding the motor and providing an outlet.
  • the muffler includes a tubular body with an inner surface lined with a plurality of resonator elements, a damping layer of mineral wool covering the interior of the resonator elements, and a perforated sheet covering the inner surface of the damping layer.
  • European patent application 0573 895 A 1 discloses a muffler device located in a volute chamber of a compressor device.
  • the present invention seeks to improve over the solution offered by the aforementioned four prior art documents by providing improved acoustic muffling employing complex acoustic attenuation means.
  • an acoustic liner is provided, as well as a fluid processing device, wherein the liner attenuates noise and consists of one or more acoustic liners each including a plurality of cells formed in a plate in a manner to form an array of resonators.
  • Fig. 1 depicts a portion of a high pressure fluid pressurizing device, such as a centrifugal compressor, including a casing 10 defining an impeller cavity 10a for receiving an impeller 12 which is mounted for rotation in the cavity. It is understood that a power-driven shaft (not shown) rotates the impeller 12 at a high speed, sufficient to impart a velocity pressure to the gas drawn into the compressor via the inlet.
  • a power-driven shaft (not shown) rotates the impeller 12 at a high speed, sufficient to impart a velocity pressure to the gas drawn into the compressor via the inlet.
  • the impeller 12 includes a plurality of impeller blades 12a arranged axi-symmetrically around the latter shaft for discharging the gas into a diffuser passage, or channel 14 formed in the casing 10 radially outwardly from the chamber 10a and the impeller 12.
  • the channel 14 receives the high pressure fluid from the impeller 12 before it is passed to a volute, or collector,16.
  • the diffuser channel 14 functions to convert the velocity pressure of the gas into static pressure which is coupled to a discharge volute, or collector 16 also formed in the casing and connected with the channel.
  • the discharge volute 16 couples the compressed gas to an outlet of the compressor.
  • a mounting bracket 20 is secured to an inner wall of the casing 10 defining the diffuser channel 14 and includes a base 22 disposed adjacent the outer end portion of the impeller and a plate 24 extending from the base and along the latter wall of the casing.
  • Two one-piece, unitary, annular acoustic liners 28 and 30 are mounted in a groove in the plate 24 of the bracket 20 in a abutting relationship and each is annular in shape and extends around the impeller 12 for 360 degrees.
  • the upper section of the liner 28 is shown in detail in Figs. 2 and 3, and is formed of an annular, relatively thick, unitary shell, or plate 32 preferably made of steel.
  • the plate 32 is attached to the bracket plate 24 in any conventional manner, such as by a plurality of bolts, or the like.
  • a series of relatively large cells, or openings, 34 are formed through one surface of the plate 32 and extend through a majority of the thickness of the plate but not through its entire thickness.
  • a series of relatively small cells 36 extend from the bottom of each cell 34 to the opposite surface of the plate 32.
  • Each cell 34 is shown having a disc-like cross section and each cell 36 is in the form of a bore for the purpose of example, it being understood that the shapes of the cells 34 and 36 can vary within the scope of the invention.
  • each cell 34 is formed by drilling a relative large-diameter counterbore through one surface of the plate 32, which counterbore extends through a majority of the thickness of the plate but not though the complete thickness of the plate.
  • Each cell 36 is formed by drilling a bore, or passage, through the opposite surface of the plate 32 to the bottom of a corresponding cell 34 and thus connects the cell 34 to the diffuser channel 14.
  • the cells 34 are formed in a plurality of annular extending rows along the entire annular area of the plate 32, with the cells 34 of a particular row being staggered, or offset, from the cells of its adjacent row(s).
  • a plurality of cells 36 are associated with each cell 34 and the cells 36 can be randomly disposed relative to their corresponding cell 34, or, alternately, can be formed in any pattern of uniform distribution.
  • the liner 30 is similar to the liner 28 and, as such, is formed of an annular, relatively thick, unitary shell, or plate 42 (Fig. 1), preferably made of steel, and is attached to the liner 28 in any conventional manner such as by a plurality of bolts, or the like.
  • a series of relatively large cells, or openings, 44 are formed through one surface of the plate 42 and a series of relatively small cells 46 extend from the bottom of each cell 34 to the opposite surface of the plate 32. Since the cells 44 and 46 are similar to the cells 34 and 36, respectively, they will not be described in further detail.
  • the liners 30 and 28 can be of different thickness.
  • the liners 28 and 30 are mounted in the bracket plate 24 with the surface of the liner 28 through which the cells 34 extend abutting the surface of the liner 30 through which the cells 46 extend. Also, the cells 34 of the liner 28 are in alignment with the cells 44 of the liner 30. The open ends of the cells 44 of the liner 30 are capped by the underlying wall of the plate 24 of the bracket 20, and the open ends of the cells 34 of the liner 28 are capped by the corresponding surface of the liner 30. The cells 34 of the liner 28 and the cells 44 of the liner 30 are connected by the cells 46 of the liner 30, due to their alignment.
  • the cells Due to the firm contact between the liners 28 and 30, and between the liner 30 and the corresponding wall of the plate 24 of the bracket 20, and due to the cells 36 and 46 connecting the cells 34 and 44 to the diffuser channel 14, the cells work collectively as an array of acoustic resonators in series.
  • the liners 28 and 30 attenuate the sound waves generated in the casing 10 by the fast-rotation of the impeller 12, and by its associated components, and eliminate, or at least minimize, the possibility that the noise will by-pass the liners and pass through a different path.
  • the dominant noise component commonly occurring at the blade passing frequency, or other high frequency can be effectively lowered by tuning the liners 28 and 30 so that the maximum sound attenuation occurs around the latter frequency.
  • This can be achieved by varying the volume of the cells 34 and 44, and/or the cross-section area, the number, and/or the length of the cells 36 and 46.
  • the provision of the two liners 28 and 30 enables them to attenuate noise in a much wider frequency range than if a single liner were used, thus enabling a maximum amount of attenuation of the acoustic energy generated by the rotating impeller 12 and its associated components to be achieved.
  • two one-piece, unitary, annular liners 48 and 50 are secured in a groove formed in the internal wall of the casing 10 opposite to the liners 28 and 30.
  • the liner 48 extends in the bottom of the groove and is connected to the structure forming the groove in any conventional manner, such as by a plurality of bolts, or the like; and the liner 50 extends in the groove in an abutting relationship to the liner 48 and is connected to the liner 48 in any conventional manner, such as by a plurality of bolts, or the like.
  • the liner 50 partially defines, with the liner 30, the diffuser channel 14. Since the liners 48 and 50 are similar to, and functions the same as, the liners 28 and 30, they will not be described in any further detail.
  • the cells Due to the firm contact between the liners 48 and 50, and between the liner 48 and the corresponding wall of the casing 10, and due to the arrangement of the respective cells of the liners, the cells work collectively as arrays of acoustic resonators in series. As such, the liners 48 and 50 attenuate the sound waves generated in the casing 10 by the fast-rotation of the impeller 12, and by its associated components, and eliminate, or at least minimize, the possibility that the noise will by-pass the liners and pass through a different path.
  • the dominant noise component commonly occurring at the blade passing frequency, or other high frequency can be effectively lowered by tuning the liners 48 and 50 so that the maximum sound attenuation occurs around the latter frequency. This can be achieved by varying the volume and/or the cross-section area, the number, and/or the length of their respective cells.
  • the provision of the two liners 48 and 50 enables them to attentuate noise in a much wider frequency range than if a single liner were used, thus enabling a maximum amount of attenuation of the acoustic energy generated by the rotating impeller 12 and its associated components to be achieved.
  • two one-piece, unitary, annular liners 54 and 56 are mounted in a groove formed in the casing 10 to the rear of the impeller 12.
  • the liner 54 extends in the bottom of the groove and is connected to the structure forming the groove in any conventional manner, such as by a plurality of bolts, or the like; and the liner 56 extends in the groove in an abutting relationship to the liner 54 and is connected to the liner 54 in any conventional manner, such as by a plurality of bolts, or the like.
  • the liner 56 partially defines, with the liner 52, the chamber in which the impeller 12 rotates.
  • the liners 54 and 56 have a smaller outer diameter than the liners 28, 30, 48 and 50, but otherwise are similar to, and are mounted in the same manner as, the latter liners.
  • the cells Due to the firm contact between the liners 54 and 56, and between the liner 54 and the corresponding wall of the casing 10, and due to the arrangement of the respective cells of the liners, the cells work collectively as arrays of acoustic resonators in series. As such, the liners 54 and 56 attenuate the sound waves generated in the casing 10 by the fast-rotation of the impeller 12, and by its associated components, and eliminate, or at least minimize, the possibility that the noise will by-pass the liners and pass through a different path.
  • the dominant noise component commonly occurring at the blade passing frequency, or other high frequency can be effectively lowered by tuning the liners 54 and 56 so that the maximum sound attenuation occurs around the latter frequency. This can be achieved by varying the volume and/or the cross-section area, the number, and/or the length of their respective cells.
  • the provision of the two liners 54 and 56 enables them to attenuate noise in a broader frequency range than if a single liner were used, thus enabling a maximum amount of attenuation of the acoustic energy generated by the rotating impeller 12 and its associated components to be achieved.
  • FIG. 5 depicts an inlet conduit 60 that introduces gas to the inlet of the impeller 12.
  • the upper portion of the conduit 60 is shown extending above the centerline C/L of the conduit and the casing 10, as viewed in Fig. 5.
  • a one-piece, unitary, liner 64 is flush-mounted on the inner wall of the conduit 60 with the radial outer portion being shown.
  • the liner 64 is in the form of a curved shell, preferably cylindrical or conical in shape, is disposed in an annular groove formed in the inner surface of the conduit 60, and is secured in the groove in any known manner. Since the liner 64 is otherwise similar to the liners 28, 30, 48, 50, 52, 54, and 56, it will not be described in further detail.
  • a one-piece, unitary, liner 66 is also disposed in the latter annular groove and extends around the liner 64 with its inner surface abutting the outer surface of the liner 64.
  • the liner 66 is in the form of a curved shell, preferably cylindrical or conical in shape having a diameter larger than the diameter of the liner 64 and is secured to the liner 64 in any conventional manner, such as by a plurality of bolts, or the like. Since the liners 64 and 66 are otherwise similar to the liners 28, 30, 48, 50, 52, 54, and 56, and function in the same manner to significantly reduce the noise in the casing 10, they will not be described in further detail.
  • the cells Due to the firm contact between the liners 64 and 66, and between the liner 66 and the corresponding wall of the casing 10 defining the latter groove, and due to the arrangement of the respective cells of the liners, and their location relative the inlet conduit 60, the cells work collectively as arrays of acoustic resonators in series.
  • the liners 64 and 66 attenuate the sound waves generated in the casing 10 by the fast-rotation of the impeller 12, and by its associated components, and eliminate, or at least minimize, the possibility that the noise will by-pass the liners and pass through a different path.
  • the dominant noise component commonly occurring at the blade passing frequency, or other high frequency can be effectively lowered by tuning the liners 64 and 66 so that the maximum sound attenuation occurs around the latter frequency. This can be achieved by varying the volume and/or the cross-section area, the number, and/or the length of their respective cells.
  • the provision of the two liners 64 and 66 enables them to attenuate noise in a broader frequency range than if a single liner were used, thus enabling a maximum amount of attenuation of the acoustic energy generated by the rotating impeller 12 and its associated components to be achieved.
  • the number of the smaller cells per each larger cell of each liner can be varied spatially across the liners so that the entire liner is effective to attenuate noise in a broader frequency band. Consequently, the liners 28, 30, 48, 50, 52, 54, 56, 64, and 66 can efficiently and effectively attenuate noise, not just in constant speed machines, but also in variable speed compressors, or other fluid pressurizing devices.
  • the one-piece unitary construction of the liners in the above embodiments renders the liners mechanically stronger when compared to the composite designs discussed above.
  • the liners provide a very rigid inner wall to the internal flow in the fluid pressurizing device, and have less or no deformation when subj ect to mechanical and thermal loading, and thus have no adverse effect on the aerodynamic performance of a fluid pressurizing device, such as a centrifugal compressor, even when they are installed in the narrow passages such as the diffusor channels, or the like.
  • liners in accordance with the above embodiments are not limited to the number shown.
  • the liners to either side of the diffuser channel and/or the impeller and/or the inlet conduit.
  • a one-piece liner can be formed in which the cells are molded in their respective plates.
  • the relative dimensions, shapes, numbers and the pattern of the cells of each liner can vary.
  • the liners are not limited to use with a centrifugal compressor, but are equally applicable to other fluid pressurizing devices in which aerodynamic effects are achieved with movable blades.
  • Each liner can extend for degrees around the axis of the impeller and the inlet conduit as disclosed above; or each liner can be formed into segments which extend an angular distance less than 360 degrees.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Multimedia (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Soundproofing, Sound Blocking, And Sound Damping (AREA)

Claims (17)

  1. Eine Vorrichtung zum unter Druck setzen einer Flüssigkeit, umfassend
    Ein Gehäuse, dass einen Eingang und einen Ausgang aufweist, das eine Kammer (10a) definiert, die eine interne Wand zwischen dem Eingang und dem Ausgang aufweist;
    Ein Flügelrad (12), das in der Kammer (10a) montiert und angepasst ist zu rotieren, um Flüssigkeit von dem Eingang durch die Kammer und Diffusor-Kanal und zu dem Ausgang zum Abfließen aus dem Gehäuse fließen zu lassen; und
    eine erste Platte (42, 48, 54), die an der internen Wand montiert ist, oder ein Bügel (20), der mit der Wand verbunden ist und eine Vielzahl von Durchgangsöffnungen (34, 36) aufweist, die sich von einer Fläche der Platte zur anderen erstrecken, wobei die eine Wand oder der Bügel ein Ende der Öffnungen bedeckt;
    eine zweite Platte (32, 50, 56), die an der erste Platte montiert ist und eine Vielzahl von Durchgangsöffnungen (44, 46) aufweist, die sich von einer Fläche der zweiten Platte zu einer anderen Fläche dieser erstrecken:
    die Öffnungen schwächen die in der Kammer erzeugte akustische Energie ab.
  2. Die Vorrichtung nach Anspruch 1, wobei die Öffnungen von jeder Platte eine Vielzahl von Kavitäten (34), die sich von einer Fläche der Platte erstrecken, wobei die Kavitäten der ersten Platte durch die Montierung an die interne Wand oder den Bügel bedeckt sind, und eine Vielzahl von Resonator-Ausflußöffnungen (36), die sich von der entgegen gesetzten Fläche von jeder Platte zu jeder Kavität (34) erstrecken, umfassen.
  3. Die Vorrichtung nach Anspruch 2, wobei die Durchmesser der Resonator-Ausflußöffnungen (36) kleiner sind als die Durchmesser der Kavitäten (34) .
  4. Die Vorrichtung nach Anspruch 1, wobei eine der Flächen der Platte (32) an der Wand oder dem Bügel angrenzt.
  5. Die Vorrichtung nach Anspruch 1, wobei das Flügelrad (12) eine Vielzahl Fluß-Passagen (16) aufweist, die in Strömungsverbindung mit der Kammer sind, so dass die Flüssigkeit durch die Passagen (14) fließt.
  6. Die Vorrichtung nach Anspruch 1, wobei die Kammer ein Gebiet zum Aufnehmen des Flügelrads (12) und eines Diffusor-Kanals (14), der mit dem Gebiet kommuniziert, enthält, wobei die erste Platte an einer Wand montiert ist, die den Difussor-Kanal (14) definiert; und wobei die Flüssigkeit von dem Gebiet zu dem Diffusor-kanal (14) fließt.
  7. Die Vorrichtung nach Anspruch 1, wobei die Öffnungen (34, 36) gleichmäßig in jeder Platte verteilt sind.
  8. Die Vorrichtung nach Anspruch 1, wobei die Anzahl und Größe der Öffnungen (34, 36) ausgewählt sind, um den Einsatz einzustellen, die beherrschende Lärmkomponente der akustischen Energie abzuschwächen.
  9. Die Vorrichtung nach Anspruch 1, ferner umfassend eine weitere Platte (52), die an einer anderen Wand entgegen gesetzt zu der internen Wand montiert ist und eine Vielzahl von relativen Durchgangsöffnungen aufweist, die sich von einer Fläche der weiteren Platte (52) zur anderen erstrecken; wobei eine andere interne Wand ein Ende der Öffnungen in der weiteren Platte bedeckt, um ein Array von Resonatoren zu bilden, um die in der Kammer erzeugte akustische Energie abzuschwächen.
  10. Die Vorrichtung nach Anspruch 9, wobei die Öffnungen in der weiteren Platte eine Vielzahl von Kavitäten aufweisen, die sich von einer Fläche der weiteren Platte erstrecken, die von einer anderen internen Wand bedeckt sind; und eine Vielzahl von Resonator-Ausflußöffnungen, die sich von der entgegen gesetzten Fläche der weiteren Platte zu jeder Kavität in der weiteren Platte erstrecken.
  11. Die Vorrichtung nach Anspruch 10, wobei die Durchmesser der letzteren Resonator-Auslußöffnungen in der weiteren Platte kleiner sind als die Durchmesser der Kavitäten in der weiteren Platte.
  12. Die Vorrichtung nach Anspruch 1, ferner umfassend eine Leitung (60), die mit dem Eingang verbunden ist, und noch eine weitere Platte, die an der inneren Wand der Leitung (6) gebildet ist und eine Vielzahl von relativen Durchgangsöffnungen aufweist, die sich von einer Fläche der noch einen weiteren Platte zu der anderen erstrecket; wobei die innere Wand der Leitung (60) ein Ende der Öffnungen bedeckt, um ein Array von Resonatoren zu bilden, um die in der Leitung erzeugte akustische Energie abzuschwächen.
  13. Die Vorrichtung nach Anspruch 12, wobei die noch eine weitere Platte gebogen ist, um sich der inneren Fläche der Leitung (60) anzupassen.
  14. Die Vorrichtung nach Anspruch 12, wobei die Öffnungen eine Vielzahl von Kavitäten enthält, die sich von einer Fläche der noch einen weiteren Platte erstrecken, die von der Leitung bedeckt sind; und eine Vielzahl von Resonator-Ausflußöffnungen, die sich von der entgegen gesetzten Fläche der noch einen weiteren Platte zu jeder Kavität in der noch einen weiteren Platte erstrecken.
  15. Die Vorrichtung nach Anspruch 14, wobei die Durchmesser der Resonator-Ausflußöffnungen in der noch einen weiteren Platte kleiner sind als die Durchmesser der Kavitäten in der noch einen weiteren Platte.
  16. Die Vorrichtung nach Anspruch 1, wobei jede Platte einen scheibenartigen Körper oder eine gebogene Hülle enthält.
  17. Eine Vorrichtung zum unter Druck setzen einer Flüssigkeit, umfassend
    Ein Gehäuse, dass einen Eingang und einen Ausgang aufweist, das eine Kammer (10a) definiert, die eine interne Wand zwischen dem Eingang und dem Ausgang aufweist;
    Ein Flügelrad (12), das in der Kammer (10a) montiert und angepasst ist zu rotieren, um Flüssigkeit von dem Eingang durch die Kammer und Diffusor-Kanal und zu dem Ausgang zum Abfließen aus dem Gehäuse fließen zu lassen; und
    eine erste gebogene Hülle (66), die an der internen Wand montiert ist und eine Vielzahl von Durchgangsöffnungen (34, 36) aufweist, die sich von einer Fläche der Hülle zur anderen erstrecken, wobei die eine Wand ein Ende der Öffnungen bedeckt;
    eine zweite gebogene Hülle (64), die an der erste Hülle montiert ist und eine Vielzahl von Durchgangsöffnungen (44, 46) aufweist, die sich von einer Fläche der zweiten Hülle zu einer anderen Fläche dieser erstrecken:
    die Öffnungen schwächen die in der Kammer erzeugte akustische Energie ab.
EP01996188A 2000-12-21 2001-11-08 Zweischichtiger akustischer überzug und fluiddruckbeaufschlagungsvorrichtung Expired - Lifetime EP1356169B1 (de)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
US09/745,862 US6550574B2 (en) 2000-12-21 2000-12-21 Acoustic liner and a fluid pressurizing device and method utilizing same
US745862 2000-12-21
US09/929,193 US6601672B2 (en) 2000-12-21 2001-08-14 Double layer acoustic liner and a fluid pressurizing device and method utilizing same
US929193 2001-08-14
PCT/US2001/047515 WO2002052110A1 (en) 2000-12-21 2001-11-08 Double layer acoustic liner and a fluid pressurizing device and method utilizing same

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EP1356169A1 EP1356169A1 (de) 2003-10-29
EP1356169A4 EP1356169A4 (de) 2004-10-13
EP1356169B1 true EP1356169B1 (de) 2006-06-14

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EP (1) EP1356169B1 (de)
JP (1) JP4088155B2 (de)
CN (1) CN1318710C (de)
CA (1) CA2432094C (de)
DE (2) DE01996188T1 (de)
WO (1) WO2002052110A1 (de)

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CA2432094A1 (en) 2002-07-04
JP4088155B2 (ja) 2008-05-21
EP1356169A1 (de) 2003-10-29
CN1318710C (zh) 2007-05-30
DE60120769T2 (de) 2007-05-24
JP2004525290A (ja) 2004-08-19
CN1489662A (zh) 2004-04-14
WO2002052110A1 (en) 2002-07-04
EP1356169A4 (de) 2004-10-13
DE60120769D1 (de) 2006-07-27
CA2432094C (en) 2010-07-27
DE01996188T1 (de) 2005-07-14

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