US20090317237A1 - System and method for reduction of unsteady pressures in turbomachinery - Google Patents
System and method for reduction of unsteady pressures in turbomachinery Download PDFInfo
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- US20090317237A1 US20090317237A1 US12/142,940 US14294008A US2009317237A1 US 20090317237 A1 US20090317237 A1 US 20090317237A1 US 14294008 A US14294008 A US 14294008A US 2009317237 A1 US2009317237 A1 US 2009317237A1
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- blades
- subset
- geometric parameters
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- turbomachinery
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- 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
- F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
- F01D5/12—Blades
- F01D5/14—Form or construction
- F01D5/141—Shape, i.e. outer, aerodynamic form
- F01D5/146—Shape, i.e. outer, aerodynamic form of blades with tandem configuration, split blades or slotted blades
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- 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
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- 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
- F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
- F01D5/12—Blades
- F01D5/26—Antivibration means not restricted to blade form or construction or to blade-to-blade connections or to the use of particular materials
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- 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
- F04D29/26—Rotors specially for elastic fluids
- F04D29/32—Rotors specially for elastic fluids for axial flow pumps
- F04D29/321—Rotors specially for elastic fluids for axial flow pumps for axial flow compressors
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- 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
- F04D29/52—Casings; Connections of working fluid for axial pumps
- F04D29/54—Fluid-guiding means, e.g. diffusers
- F04D29/541—Specially adapted for elastic fluid pumps
- F04D29/542—Bladed diffusers
- F04D29/544—Blade shapes
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- 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
- F04D29/666—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps by means of rotor construction or layout, e.g. unequal distribution of blades or vanes
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- 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
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T50/00—Aeronautics or air transport
- Y02T50/60—Efficient propulsion technologies, e.g. for aircraft
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T29/00—Metal working
- Y10T29/49—Method of mechanical manufacture
- Y10T29/49316—Impeller making
- Y10T29/4932—Turbomachine making
- Y10T29/49321—Assembling individual fluid flow interacting members, e.g., blades, vanes, buckets, on rotary support member
Definitions
- the invention relates generally to turbomachines and, more particularly, to reducing unsteady pressures generated therein.
- One of the common noise sources includes noise generated by the turbomachinery within the gas turbine engine.
- the turbomachinery noise results from a relative motion of adjacent sets of blades, typical of those found in compressors (including fans) and turbines.
- a compressor comprises multiple bladed stages, each stage including a rotatable blade row and possibly a stationary blade row.
- one of the principal noise sources is the interaction between the wakes of upstream blades and downstream blades moving relative to the upstream set of blades. This wake interaction results in noise at the upstream blade passing frequency and at its harmonics, as well as broadband noise covering a wide spectrum of frequencies.
- One of the commonly used methods to reduce this wake interaction noise is to increase the axial spacing between adjacent sets of blades. This modification provides space for the wake to dissipate before reaching the downstream set of blades, resulting in less noise. Increased spacing can generally be applied to turbomachines, however, increases in axial length of the machine may be restricted by weight, aerodynamic performance losses, cost and/or installation and space requirements.
- a turbomachinery system in accordance with an embodiment of the invention, includes a first set of blades and a second set of blades moving relative to the first set of blades.
- the second set of blades includes a first subset of blades comprising multiple first geometric parameters.
- the second set of blades also includes at least a second subset of blades non-uniformly spaced circumferentially and axially relative to the first subset of blades such that unsteady pressures generated from the wakes of the first set of blades interacting with the second set of blades is below an acceptable level, wherein the at least second subset of blades comprising multiple second geometric parameters that are different or identical to the first geometric parameters.
- a method for manufacturing a turbomachine includes providing a first set of blades.
- the method also includes providing a second set of blades moving relative to the first set of blades.
- the second set of blades includes a first subset of blades comprising multiple first geometric parameters.
- the second set of blades also includes at least a second subset of blades non-uniformly spaced circumferentially and axially relative to the first subset of blades such that unsteady pressures generated from the wakes of the first set of blades interacting with the second set of blades is below an acceptable level.
- the second subset of blades comprises multiple second geometric parameters that are different or identical to the multiple first geometric parameters.
- FIG. 1 is a diagrammatic illustration of a gas turbine engine in accordance with the invention
- FIG. 2 is a schematic top view of a two-dimensional cross-section through an exemplary first set of blades and a second set of blades in the turbomachinery system of FIG. 1 ;
- FIG. 3 is a schematic graphical illustration of nullification of an exemplary acoustic wave in accordance with an embodiment of the invention.
- FIG. 4 is a flow chart representing steps in a method for manufacturing a turbomachine in accordance with an embodiment of the invention.
- embodiments of the invention include a system and method for reduction of unsteady pressures in turbomachinery.
- the system and method are applicable to various types of turbomachinery applications having blade-wake interactions resulting in unsteady pressures.
- the term ‘unsteady pressures’ as used herein refers to air unsteady pressures and acoustics as well as blade surface unsteady pressures that are also referred to as ‘aeromechanical loading’.
- Non-limiting examples of such turbomachinery applications include turbojet, turbofan, turbo propulsion engines, aircraft engines, gas turbines, steam turbines, wind turbines, or water/hydro turbines.
- FIG. 1 is a schematic illustration of an exemplary turbofan gas turbine engine assembly 10 in accordance with the invention and having a centerline axis 12 .
- engine assembly 10 includes a fan assembly 13 , a booster compressor 14 , a core gas turbine engine 16 , and a low-pressure turbine 26 that is coupled to fan assembly 13 and booster compressor 14 .
- Fan assembly 13 includes a plurality of rotor fan blades 11 that extend substantially radially outward from a fan rotor disk 15 , as well as a plurality of stator vanes 21 that are positioned downstream of fan blades 11 .
- Core gas turbine engine 16 includes a high-pressure compressor 22 , a combustor 24 , and a high-pressure turbine 18 .
- Booster compressor 14 includes a plurality of rotor blades 40 that extend substantially radially outward from a compressor rotor disk 20 coupled to a first drive shaft 31 .
- Compressor 22 and high-pressure turbine 18 are coupled together by a second drive shaft 29 .
- Engine assembly 10 also includes an intake side 28 , a core engine exhaust side 30 , and a fan exhaust side 31 .
- air entering engine 10 through intake side 28 is compressed by fan assembly 13 .
- the airflow exiting fan assembly 13 is split such that a portion 35 of the airflow is channeled into booster compressor 14 and a remaining portion 36 of the airflow bypasses booster compressor 14 and core turbine engine 16 and exits engine 10 through fan exhaust side 31 .
- This bypass air 36 flows past and interacts with the stators vanes 21 creating unsteady pressures on the stator surfaces as well as in the surrounding airflow that radiate as acoustic waves.
- the plurality of rotor blades 40 compress and deliver compressed airflow 35 towards core gas turbine engine 16 .
- Airflow 35 is further compressed by the high-pressure compressor 22 and is delivered to combustor 24 .
- Airflow 35 from combustor 24 drives rotating turbines 18 and 26 and exits engine 10 through exhaust side 30 .
- FIG. 2 is a schematic top view of a two dimensional cross-section through an exemplary first set of blades 52 and a second set of blades 54 in the turbomachinery system 10 of FIG. 1 .
- the first set of blades 52 and the second set of blades 54 may be located in the fan 11 , booster 14 , core compressor 22 , or a turbine stage 18 , 26 .
- the compressor or turbine stage is axial.
- the turbomachinery stage is radial.
- the turbomachinery stage is mixed (radial and axial).
- the first set of blades 52 is rotating and the second set of blades 54 is stationary.
- first set of blades 52 may be stationary, while the second set of blades 54 rotates.
- first set of blades and the second set of blades may be counter rotating.
- the second set of blades 54 includes a first subset of blades 58 and at least a second subset of blades 60 . It should be noted that the second set of blades 54 may include a third subset of blades and so forth.
- the second subset of blades 60 are non-uniformly spaced circumferentially, as referenced by numeral 64 and axially, referenced by numeral 66 , relative to the first subset of blades 58 such that unsteady pressures generated from the wakes of the first set of blades interacting with the second set of blades is below an acceptable level.
- a chord length, referenced by numeral 72 for the second subset of blades 60 relative to the first subset of blades 58 may be varied.
- an inclination angle relative to axial direction referred to as ‘stagger’ referenced by numeral 74 and/or curvature of the blade referred to as ‘camber’, respectively, may be varied relative to the first subset of blades 58 .
- a thickness of the first subset of blades and the second subset of blades may be varied.
- a chordwise distribution of camber and/or thickness may be varied.
- the second set of blades 54 may include a radial or spanwise distribution of the foregoing parameters over different sets of blades.
- one of the principal sources of unsteady pressures in turbomachinery is the interaction between the wakes of the first set of blades 52 and the second set of blades 54 , moving relative to each other.
- the wakes are defined as the region of reduced momentum behind an airfoil evidenced by the aerodynamic drag of the blade.
- the first set of blades 52 shed a wake 82 that is impacted by representative second set of blades 54 .
- the wake interaction will occur at different and non-uniformly distributed instants of time.
- first subset of blades 58 and the second subset of blades 60 may be optimally spaced such that the acoustic waves resulting from such an interaction destructively interfere to produce less overall noise, as described below.
- first subset of blades 58 and the second subset of blades 60 may be optimally spaced to reduce unsteady surface pressure loads on the blades 58 , 60 .
- FIG. 3 is a schematic graphical illustration 90 of nullification of an exemplary acoustic wave by non-uniform spacing of the second set of blades 54 ( FIG. 2 ).
- An exemplary acoustic signal 92 representative of an acoustic wave is generated from the interaction between the first set of blades 52 ( FIG. 2 ) and a subset 58 of the second set of blades 54 ( FIG. 2 ) prior to variation of geometric parameters.
- An optimal shift in the circumferential and axial position of the second subset 60 of the second set of blades 54 relative to 58 induces acoustic radiation resulting in a signal 94 out of phase with the signal 92 .
- the signals 92 and 94 cancel each other resulting in a signal 96 devoid of the acoustic energy originally generated, a phenomenon commonly referred to as wave destructive interference.
- wave destructive interference a phenomenon commonly referred to as wave destructive interference. It will be appreciated that the illustrated embodiment is an ideal case. However, non-ideal cases may also result in a significant or desirable reduction in noise.
- FIG. 4 is a flow chart representing steps in a method 110 for manufacturing a turbomachine.
- the method 110 includes providing a first set of blades in step 112 .
- a rotating first set of blades is provided.
- a second set of blades is provided in step 114 that moves relative to the first set of blades.
- a stationary second set of blades is provided.
- the second set of blades includes a first subset of blades having multiple first geometric parameters and at least a second subset of blades non-uniformly spaced circumferentially and axially relative to the first set of blades such that unsteady pressures generated from the wakes of the first set of blades interacting with the second set of blades is below an acceptable level.
- the at least second subset of blades has multiple second geometric parameters that are different or identical to the plurality of first geometric parameters.
- the second set of blades further includes a third subset of blades non-uniformly spaced circumferentially and axially relative to the first subset of blades and the second subset of blades.
- the second set of blades further includes any number of subsets of blades non-uniformly spaced circumferentially and axially relative to the all other subsets of blades, up to and including the point where every blade in the second set of blades is uniquely spaced circumferentially and axially and uniquely defined by the multiple second geometric parameters relative to every other blade in the second set.
- the various embodiments of a system and method for reduction of unsteady pressures in turbomachinery described above thus provide a convenient and efficient means to reduce aerodynamic noise and/or aeromechanical loading caused by interaction of wakes between sets of blades moving relative to each other.
- the technique provides non-uniform spacing between blades in a set of blades resulting in a reduction in unsteady blade loading that also results in reduced noise signals and/or a noise field that superimposes in a way to reduce peak noise signals.
- the technique can also be used to improve fuel bum by redesigning other system or geometric parameters (e.g., reducing the separation distance between adjacent sets of interacting turbomachinery blades, thereby also reducing system weight) in such a way to improve system efficiency, and employing the technique described in this invention to maintaining desirable noise levels.
- redesigning other system or geometric parameters e.g., reducing the separation distance between adjacent sets of interacting turbomachinery blades, thereby also reducing system weight
- a third subset of blades described with respect to one embodiment may include a geometric variation in stagger, camber and thickness relative to a first subset and a second subset of blades described with respect to another.
- This concept can also be extended to the point where every blade in the set is designed uniquely relative to all other blades in the set.
- the various features described, as well as other known equivalents for each feature can be mixed and matched by one of ordinary skill in this art to construct additional systems and techniques in accordance with principles of this disclosure.
Abstract
A turbomachinery system is provided. The system includes a first set of blades and a second set of blades moving relative to the first set of blades, wherein the second set of blades includes a first subset of blades having multiple first geometric parameters. The second set of blades also includes at least a second subset of blades non-uniformly spaced circumferentially and axially relative to the first subset of blades such that unsteady pressures generated from the wakes of the first set of blades interacting with the second set of blades is below an acceptable level. Further, the at least second subset of blades include multiple second geometric parameters that are different or identical to the multiple first geometric parameters.
Description
- The invention relates generally to turbomachines and, more particularly, to reducing unsteady pressures generated therein.
- With increased public concern over aircraft-generated noise, aircraft gas turbine engine manufacturers are faced with the problem of developing new ways of effectively reducing noise. One of the common noise sources includes noise generated by the turbomachinery within the gas turbine engine. The turbomachinery noise results from a relative motion of adjacent sets of blades, typical of those found in compressors (including fans) and turbines. For example, a compressor comprises multiple bladed stages, each stage including a rotatable blade row and possibly a stationary blade row. It has long been recognized that in turbomachines one of the principal noise sources is the interaction between the wakes of upstream blades and downstream blades moving relative to the upstream set of blades. This wake interaction results in noise at the upstream blade passing frequency and at its harmonics, as well as broadband noise covering a wide spectrum of frequencies.
- One of the commonly used methods to reduce this wake interaction noise is to increase the axial spacing between adjacent sets of blades. This modification provides space for the wake to dissipate before reaching the downstream set of blades, resulting in less noise. Increased spacing can generally be applied to turbomachines, however, increases in axial length of the machine may be restricted by weight, aerodynamic performance losses, cost and/or installation and space requirements.
- Therefore, an improved means of reducing the wake interaction effect is desirable.
- In accordance with an embodiment of the invention, a turbomachinery system is provided. The system includes a first set of blades and a second set of blades moving relative to the first set of blades. The second set of blades includes a first subset of blades comprising multiple first geometric parameters. The second set of blades also includes at least a second subset of blades non-uniformly spaced circumferentially and axially relative to the first subset of blades such that unsteady pressures generated from the wakes of the first set of blades interacting with the second set of blades is below an acceptable level, wherein the at least second subset of blades comprising multiple second geometric parameters that are different or identical to the first geometric parameters.
- In accordance with another embodiment of the invention, a method for manufacturing a turbomachine is provided. The method includes providing a first set of blades. The method also includes providing a second set of blades moving relative to the first set of blades. The second set of blades includes a first subset of blades comprising multiple first geometric parameters. The second set of blades also includes at least a second subset of blades non-uniformly spaced circumferentially and axially relative to the first subset of blades such that unsteady pressures generated from the wakes of the first set of blades interacting with the second set of blades is below an acceptable level. Further, the second subset of blades comprises multiple second geometric parameters that are different or identical to the multiple first geometric parameters.
- These and other features, aspects, and advantages of the present invention will become better understood when the following detailed description is read with reference to the accompanying drawings in which like characters represent like parts throughout the drawings, wherein:
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FIG. 1 is a diagrammatic illustration of a gas turbine engine in accordance with the invention; -
FIG. 2 is a schematic top view of a two-dimensional cross-section through an exemplary first set of blades and a second set of blades in the turbomachinery system ofFIG. 1 ; -
FIG. 3 is a schematic graphical illustration of nullification of an exemplary acoustic wave in accordance with an embodiment of the invention; and -
FIG. 4 is a flow chart representing steps in a method for manufacturing a turbomachine in accordance with an embodiment of the invention. - As discussed in detail below, embodiments of the invention include a system and method for reduction of unsteady pressures in turbomachinery. As used herein, the system and method are applicable to various types of turbomachinery applications having blade-wake interactions resulting in unsteady pressures. Further, the term ‘unsteady pressures’ as used herein refers to air unsteady pressures and acoustics as well as blade surface unsteady pressures that are also referred to as ‘aeromechanical loading’. Non-limiting examples of such turbomachinery applications include turbojet, turbofan, turbo propulsion engines, aircraft engines, gas turbines, steam turbines, wind turbines, or water/hydro turbines.
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FIG. 1 is a schematic illustration of an exemplary turbofan gasturbine engine assembly 10 in accordance with the invention and having acenterline axis 12. In the exemplary embodiment,engine assembly 10 includes afan assembly 13, a booster compressor 14, a coregas turbine engine 16, and a low-pressure turbine 26 that is coupled tofan assembly 13 and booster compressor 14.Fan assembly 13 includes a plurality ofrotor fan blades 11 that extend substantially radially outward from afan rotor disk 15, as well as a plurality ofstator vanes 21 that are positioned downstream offan blades 11. Coregas turbine engine 16 includes a high-pressure compressor 22, acombustor 24, and a high-pressure turbine 18. Booster compressor 14 includes a plurality ofrotor blades 40 that extend substantially radially outward from acompressor rotor disk 20 coupled to afirst drive shaft 31.Compressor 22 and high-pressure turbine 18 are coupled together by asecond drive shaft 29.Engine assembly 10 also includes anintake side 28, a coreengine exhaust side 30, and afan exhaust side 31. - During operation,
air entering engine 10 throughintake side 28 is compressed byfan assembly 13. The airflow exitingfan assembly 13 is split such that aportion 35 of the airflow is channeled into booster compressor 14 and aremaining portion 36 of the airflow bypasses booster compressor 14 andcore turbine engine 16 andexits engine 10 throughfan exhaust side 31. Thisbypass air 36 flows past and interacts with the stators vanes 21 creating unsteady pressures on the stator surfaces as well as in the surrounding airflow that radiate as acoustic waves. The plurality ofrotor blades 40 compress and delivercompressed airflow 35 towards coregas turbine engine 16.Airflow 35 is further compressed by the high-pressure compressor 22 and is delivered tocombustor 24.Airflow 35 from combustor 24 drives rotatingturbines 18 and 26 andexits engine 10 throughexhaust side 30. -
FIG. 2 is a schematic top view of a two dimensional cross-section through an exemplary first set ofblades 52 and a second set ofblades 54 in theturbomachinery system 10 ofFIG. 1 . The first set ofblades 52 and the second set ofblades 54 may be located in thefan 11, booster 14,core compressor 22, or aturbine stage 18, 26. In one embodiment, the compressor or turbine stage is axial. In an alternative embodiment, the turbomachinery stage is radial. In yet another embodiment, the turbomachinery stage is mixed (radial and axial). In the illustrated embodiment, the first set ofblades 52 is rotating and the second set ofblades 54 is stationary. In an alternative embodiment, the first set ofblades 52 may be stationary, while the second set ofblades 54 rotates. In yet another embodiment, the first set of blades and the second set of blades may be counter rotating. The second set ofblades 54 includes a first subset ofblades 58 and at least a second subset ofblades 60. It should be noted that the second set ofblades 54 may include a third subset of blades and so forth. The second subset ofblades 60 are non-uniformly spaced circumferentially, as referenced bynumeral 64 and axially, referenced bynumeral 66, relative to the first subset ofblades 58 such that unsteady pressures generated from the wakes of the first set of blades interacting with the second set of blades is below an acceptable level. - Various geometric parameters may be varied between the first subset of
blades 58 and the second subset ofblades 60. For example, a chord length, referenced bynumeral 72, for the second subset ofblades 60 relative to the first subset ofblades 58 may be varied. In another embodiment, an inclination angle relative to axial direction referred to as ‘stagger’ referenced bynumeral 74 and/or curvature of the blade referred to as ‘camber’, respectively, may be varied relative to the first subset ofblades 58. In another exemplary embodiment, a thickness of the first subset of blades and the second subset of blades may be varied. In yet another embodiment, a chordwise distribution of camber and/or thickness may be varied. In another embodiment, the second set ofblades 54 may include a radial or spanwise distribution of the foregoing parameters over different sets of blades. - As has been previously discussed, one of the principal sources of unsteady pressures in turbomachinery is the interaction between the wakes of the first set of
blades 52 and the second set ofblades 54, moving relative to each other. As is well understood, the wakes are defined as the region of reduced momentum behind an airfoil evidenced by the aerodynamic drag of the blade. As illustrated, the first set ofblades 52 shed a wake 82 that is impacted by representative second set ofblades 54. However, if at least a second subset ofblades 60 are non-uniformly spaced circumferentially and axially, the wake interaction will occur at different and non-uniformly distributed instants of time. Further, the first subset ofblades 58 and the second subset ofblades 60 may be optimally spaced such that the acoustic waves resulting from such an interaction destructively interfere to produce less overall noise, as described below. In another embodiment, the first subset ofblades 58 and the second subset ofblades 60 may be optimally spaced to reduce unsteady surface pressure loads on theblades -
FIG. 3 is a schematicgraphical illustration 90 of nullification of an exemplary acoustic wave by non-uniform spacing of the second set of blades 54 (FIG. 2 ). An exemplaryacoustic signal 92 representative of an acoustic wave is generated from the interaction between the first set of blades 52 (FIG. 2 ) and asubset 58 of the second set of blades 54 (FIG. 2 ) prior to variation of geometric parameters. An optimal shift in the circumferential and axial position of thesecond subset 60 of the second set ofblades 54 relative to 58, as described inFIG. 2 , induces acoustic radiation resulting in asignal 94 out of phase with thesignal 92. Thus, thesignals signal 96 devoid of the acoustic energy originally generated, a phenomenon commonly referred to as wave destructive interference. It will be appreciated that the illustrated embodiment is an ideal case. However, non-ideal cases may also result in a significant or desirable reduction in noise. -
FIG. 4 is a flow chart representing steps in amethod 110 for manufacturing a turbomachine. Themethod 110 includes providing a first set of blades instep 112. In one embodiment, a rotating first set of blades is provided. A second set of blades is provided instep 114 that moves relative to the first set of blades. In an exemplary embodiment, a stationary second set of blades is provided. The second set of blades includes a first subset of blades having multiple first geometric parameters and at least a second subset of blades non-uniformly spaced circumferentially and axially relative to the first set of blades such that unsteady pressures generated from the wakes of the first set of blades interacting with the second set of blades is below an acceptable level. Further, the at least second subset of blades has multiple second geometric parameters that are different or identical to the plurality of first geometric parameters. In one embodiment, the second set of blades further includes a third subset of blades non-uniformly spaced circumferentially and axially relative to the first subset of blades and the second subset of blades. In another embodiment, the second set of blades further includes any number of subsets of blades non-uniformly spaced circumferentially and axially relative to the all other subsets of blades, up to and including the point where every blade in the second set of blades is uniquely spaced circumferentially and axially and uniquely defined by the multiple second geometric parameters relative to every other blade in the second set. - The various embodiments of a system and method for reduction of unsteady pressures in turbomachinery described above thus provide a convenient and efficient means to reduce aerodynamic noise and/or aeromechanical loading caused by interaction of wakes between sets of blades moving relative to each other. The technique provides non-uniform spacing between blades in a set of blades resulting in a reduction in unsteady blade loading that also results in reduced noise signals and/or a noise field that superimposes in a way to reduce peak noise signals.
- The technique can also be used to improve fuel bum by redesigning other system or geometric parameters (e.g., reducing the separation distance between adjacent sets of interacting turbomachinery blades, thereby also reducing system weight) in such a way to improve system efficiency, and employing the technique described in this invention to maintaining desirable noise levels.
- It is to be understood that not necessarily all such objects or advantages described above may be achieved in accordance with any particular embodiment. Thus, for example, those skilled in the art will recognize that the systems and techniques described herein may be embodied or carried out in a manner that achieves or optimizes one advantage or group of advantages as taught herein without necessarily achieving other objects or advantages as may be taught or suggested herein.
- Furthermore, the skilled artisan will recognize the interchangeability of various features from different embodiments. For example, a third subset of blades described with respect to one embodiment may include a geometric variation in stagger, camber and thickness relative to a first subset and a second subset of blades described with respect to another. This concept can also be extended to the point where every blade in the set is designed uniquely relative to all other blades in the set. Similarly, the various features described, as well as other known equivalents for each feature, can be mixed and matched by one of ordinary skill in this art to construct additional systems and techniques in accordance with principles of this disclosure.
- While only certain features of the invention have been illustrated and described herein, many modifications and changes will occur to those skilled in the art. It is, therefore, to be understood that the appended claims are intended to cover all such modifications and changes as fall within the true spirit of the invention.
Claims (12)
1. A turbomachinery system, comprising:
a first set of blades; and
a second set of blades moving relative to the first set of blades, the second set of blades comprising:
a first subset of blades comprising a plurality of first geometric parameters; and
at least a second subset of blades non-uniformly spaced circumferentially and axially relative to the first subset of blades such that unsteady pressures generated from the wakes of the first set of blades interacting with the second set of blades is below an acceptable level, the at least second subset of blades comprising a plurality of second geometric parameters that are different or identical to the plurality of first geometric parameters.
2. The system of claim 1 , wherein the first subset of blades is stationary and the second set of blades is rotating.
3. The system of claim 1 , wherein the first set of blades is rotating and the second set of blades is stationary.
4. The system of claim 1 , wherein the first set of blades and the second set of blades are counter-rotating.
5. The system of claim 1 , wherein the second set of blades further comprises a third subset of blades spaced circumferentially and axially relative to the first subset of blades and the second subset of blades.
6. The system of claim 1 , wherein the plurality of first geometric parameters and the plurality of second geometric parameters comprises a camber, a stagger, a chord, a thickness, a chordwise distribution and a spanwise distribution of the camber, the thickness and the stagger respectively.
7. The system of claim 1 , wherein the turbomachinery system comprises an aircraft engine, gas turbine, steam turbine, a wind turbine, a hydro turbine, or a heating-ventillating-airconditioning system.
8. A method for manufacturing a turbomachine comprising:
providing a first set of blades; and
providing a second set of blades moving relative to the first set of blades, the second set of blades comprising:
a first subset of blades comprising a plurality of first geometric parameters; and
at least a second subset of blades non-uniformly spaced circumferentially and axially relative to the first subset of blades such that unsteady pressures generated from the wakes of the first set of blades interacting with the second set of blades is below an acceptable level, the at least second subset of blades comprising a plurality of second geometric parameters that are different or identical to the plurality of first geometric parameters.
9. The method of claim 8 , wherein said providing a first set of blades comprises rotating a first set of blades.
10. The method of claim 8 , wherein said providing a second set of blades comprises rotating the second set of blades.
11. The method of claim 8 , wherein providing a second set of blades further comprises providing a third subset of blades non-uniformly spaced circumferentially and axially relative to the first subset of blades and the second subset of blades.
12. The method of claim 8 , wherein providing a second set of blades further comprises providing a unique spacing circumferentially and axially and unique geometric definition for each blade in the second set.
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
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US12/142,940 US20090317237A1 (en) | 2008-06-20 | 2008-06-20 | System and method for reduction of unsteady pressures in turbomachinery |
US12/416,950 US8333552B2 (en) | 2008-06-20 | 2009-04-02 | Combined acoustic absorber and heat exchanging outlet guide vanes |
US13/247,096 US8540490B2 (en) | 2008-06-20 | 2011-09-28 | Noise reduction in a turbomachine, and a related method thereof |
Applications Claiming Priority (1)
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US12/142,940 US20090317237A1 (en) | 2008-06-20 | 2008-06-20 | System and method for reduction of unsteady pressures in turbomachinery |
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US12/342,466 Continuation-In-Part US9938931B2 (en) | 2008-06-20 | 2008-12-23 | Combined surface cooler and acoustic absorber for turbomachines |
US13/247,096 Continuation-In-Part US8540490B2 (en) | 2008-06-20 | 2011-09-28 | Noise reduction in a turbomachine, and a related method thereof |
Publications (1)
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US20090317237A1 true US20090317237A1 (en) | 2009-12-24 |
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US12/142,940 Abandoned US20090317237A1 (en) | 2008-06-20 | 2008-06-20 | System and method for reduction of unsteady pressures in turbomachinery |
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