US20130277142A1 - High pressure muffling devices - Google Patents
High pressure muffling devices Download PDFInfo
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- US20130277142A1 US20130277142A1 US13/453,388 US201213453388A US2013277142A1 US 20130277142 A1 US20130277142 A1 US 20130277142A1 US 201213453388 A US201213453388 A US 201213453388A US 2013277142 A1 US2013277142 A1 US 2013277142A1
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- Prior art keywords
- inner flow
- flow conditioner
- downstream end
- end wall
- exhaust
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
- F02C6/00—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas- turbine plants for special use
- F02C6/04—Gas-turbine plants providing heated or pressurised working fluid for other apparatus, e.g. without mechanical power output
- F02C6/06—Gas-turbine plants providing heated or pressurised working fluid for other apparatus, e.g. without mechanical power output providing compressed gas
- F02C6/08—Gas-turbine plants providing heated or pressurised working fluid for other apparatus, e.g. without mechanical power output providing compressed gas the gas being bled from the gas-turbine compressor
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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
- F01D17/00—Regulating or controlling by varying flow
- F01D17/10—Final actuators
- F01D17/105—Final actuators by passing part of the fluid
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02K—JET-PROPULSION PLANTS
- F02K3/00—Plants including a gas turbine driving a compressor or a ducted fan
- F02K3/02—Plants including a gas turbine driving a compressor or a ducted fan in which part of the working fluid by-passes the turbine and combustion chamber
- F02K3/04—Plants including a gas turbine driving a compressor or a ducted fan in which part of the working fluid by-passes the turbine and combustion chamber the plant including ducted fans, i.e. fans with high volume, low pressure outputs, for augmenting the jet thrust, e.g. of double-flow type
- F02K3/075—Plants including a gas turbine driving a compressor or a ducted fan in which part of the working fluid by-passes the turbine and combustion chamber the plant including ducted fans, i.e. fans with high volume, low pressure outputs, for augmenting the jet thrust, e.g. of double-flow type controlling flow ratio between flows
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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
- F05D2250/00—Geometry
- F05D2250/20—Three-dimensional
- F05D2250/23—Three-dimensional prismatic
- F05D2250/232—Three-dimensional prismatic conical
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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
Definitions
- the subject matter disclosed herein relates generally to muffling systems, and, more specifically, to muffling devices capable of inducing high pressure drops and desirable flow properties.
- air is pressurized in a compression module during operation.
- the air channeled through the compression module is mixed with fuel in a combustor and ignited, generating hot combustion gases which flow through turbine stages that extract energy therefrom for powering the fan and compressor rotors and generate engine thrust to propel an aircraft in flight or to power a load, such as an electrical generator.
- a portion of the high-pressure air such as, for example, bleed air from a compressor, may be extracted or bled from the compressor for various needs.
- these needs include, for example, compressor flow bleeding which may be used in order to improve operability as well as to provide turbine cooling, pressurize bearing sumps, purge air or provide aircraft environment control.
- the air may be bled off from the compressor using bleed slots located over specific portions or stages of the compressor.
- the compressor may pump more air than is required for needs including the combustion process.
- a portion of the excess bleed air from the compressor may be routed through bleed conduits and exhausted into the by-pass flow stream, engine exhaust, or to ambient.
- the pressure and temperature of the air stream bled from the compressor may be very high.
- bleed air pressure may be greater than about 1375 kPa and the bleed air temperature may be greater than about 538 degrees C.
- TBV transient bleed valve system
- Certain conventional designs for bleed exhaust systems use large and/or heavy muffling devices to reduce the generated noise.
- the exhaust area of some conventional bleed systems may be set to lower the flow velocity at the exhaust location to a level below that required to meet the acoustic limits for the application.
- the exhaust area, as well as the relatively gently expansions between the source pressure and exhaust, may contribute to the relatively large size and/or weight of these systems. In some applications (e.g., aircraft), it may be undesirable to use large and/or heavy components.
- some conventional exhaust designs on aircraft may require extensive thermal shielding on other components near the exhaust location, once the exhaust velocities that meet the acoustic limits are achieved. Due to the nature of the high temperature air, once it is over-expanded to achieve lower velocities, the air it mixes with may overwhelm the bleed air, causing it to “lay down” on the surrounding structure around the engine.
- the surrounding structure may be made of lightweight composite material or of other metallic material with lesser temperature capability.
- At least one solution for the above-mentioned problem(s) is provided by the present disclosure to include example embodiments, provided for illustrative teaching and not meant to be limiting.
- An example muffling device may include an inner flow conditioner shaped as a generally conical frustum including an upstream base and a downstream base.
- a diameter of the upstream base may be larger than a diameter of the downstream base.
- the inner flow conditioner may include an inlet approximate the upstream base, a generally circular inner flow conditioner downstream end wall having an inner flow conditioner downstream end wall area, the inner flow conditioner downstream end wall being generally orthogonal to a longitudinal axis of the conical frustum and comprising a plurality of generally longitudinally oriented inner flow conditioner downstream end wall holes, and an inner flow conditioner sidewall shaped generally as a truncated cone, the inner flow conditioner sidewall tapering inwardly from approximate the upstream base to approximate the inner flow conditioner downstream wall, the inner flow conditioner sidewall comprising a plurality of generally laterally oriented inner flow conditioner sidewall holes.
- the muffling device may include an exhaust can disposed substantially around the inner flow conditioner and shaped as a generally circular cylinder.
- the exhaust can may include a generally annular upstream end wall disposed approximate the upstream base of the inner flow conditioner and substantially circumscribing the upstream base of the inner flow conditioner, a generally circular exhaust screen comprising a plurality of exhaust screen holes, and a generally circular exhaust can sidewall extending from approximate the upstream end wall to approximate the exhaust screen.
- the inner flow conditioner and the exhaust can may be configured to conduct a fluid inward through the inlet into the inner flow conditioner, through the inner flow conditioner downstream end wall discharge openings and the inner flow conditioner sidewall discharge openings into the exhaust can, and outward through the exhaust screen discharge openings.
- the exhaust can and the inner flow conditioner downstream end wall may at least partially define a downstream end annular area therebetween. A ratio of the inner flow conditioner downstream end wall area to the downstream end annular area may be about 0.12 to about 0.97.
- An example muffling device may include an inner flow conditioner shaped as a generally conical frustum including an upstream base and a downstream base.
- a diameter of the upstream base may be larger than a diameter of the downstream base.
- the inner flow conditioner may include an inlet approximate the upstream base, a generally circular inner flow conditioner downstream end wall having an inner flow conditioner downstream end wall area, the inner flow conditioner downstream end wall being generally orthogonal to a longitudinal axis of the conical frustum and comprising a plurality of generally longitudinally oriented inner flow conditioner downstream end wall holes, and an inner flow conditioner sidewall shaped generally as a truncated cone, the inner flow conditioner sidewall tapering inwardly from approximate the upstream base to approximate the inner flow conditioner downstream wall, the inner flow conditioner sidewall comprising a plurality of generally laterally oriented inner flow conditioner sidewall holes.
- the muffling device may include an exhaust can disposed substantially around the inner flow conditioner and shaped as a generally circular cylinder.
- the exhaust can may include a generally annular upstream end wall disposed approximate the upstream base of the inner flow conditioner and substantially circumscribing the upstream base of the inner flow conditioner, a generally circular exhaust screen comprising a plurality of exhaust screen holes, and a generally circular exhaust can sidewall extending from approximate the upstream end wall to approximate the exhaust screen.
- the inner flow conditioner and the exhaust can may be configured to conduct a fluid inward through the inlet into the inner flow conditioner, through the inner flow conditioner downstream end wall discharge openings and the inner flow conditioner sidewall discharge openings into the exhaust can, and outward through the exhaust screen discharge openings.
- the exhaust can and the inner flow conditioner downstream end wall may at least partially define a downstream end annular area therebetween.
- a ratio of the downstream end annular area to the downstream end wall area may be proportional, by a factor of about 0.8 to about 1.9, to a ratio of an effective area of the inner flow conditioner sidewall holes to an effective area of the inner flow conditioner downstream end wall holes.
- An example muffling device may include an inner flow conditioner shaped as a generally conical frustum including an upstream base and a downstream base.
- a diameter of the upstream base may be larger than a diameter of the downstream base.
- the inner flow conditioner may include an inlet approximate the upstream base, a generally circular inner flow conditioner downstream end wall having an inner flow conditioner downstream end wall area, the inner flow conditioner downstream end wall being generally orthogonal to a longitudinal axis of the conical frustum and comprising a plurality of generally longitudinally oriented inner flow conditioner downstream end wall holes, and an inner flow conditioner sidewall shaped generally as a truncated cone, the inner flow conditioner sidewall tapering inwardly from approximate the upstream base to approximate the inner flow conditioner downstream wall, the inner flow conditioner sidewall comprising a plurality of generally laterally oriented inner flow conditioner sidewall holes.
- the muffling device may include an exhaust can disposed substantially around the inner flow conditioner and shaped as a generally circular cylinder.
- the exhaust can may include a generally annular upstream end wall disposed approximate the upstream base of the inner flow conditioner and substantially circumscribing the upstream base of the inner flow conditioner, a generally circular exhaust screen comprising a plurality of exhaust screen holes, and a generally circular exhaust can sidewall extending from approximate the upstream end wall to approximate the exhaust screen.
- the inner flow conditioner and the exhaust can may be configured to conduct a fluid inward through the inlet into the inner flow conditioner, through the inner flow conditioner downstream end wall discharge openings and the inner flow conditioner sidewall discharge openings into the exhaust can, and outward through the exhaust screen discharge openings.
- the exhaust can and the inner flow conditioner downstream end wall may at least partially define a downstream end annular area therebetween.
- the inner flow conditioner downstream end wall holes may have an inner flow conditioner downstream end wall hole diameter.
- the inner flow conditioner downstream end wall may be spaced from the exhaust screen by a dissipation distance.
- a ratio of the dissipation distance to the inner flow conditioner downstream end wall hole diameter may be greater than about 10.
- FIG. 1 is a schematic cross-sectional view of an example gas turbine engine assembly including an example bleed system including an example muffling device;
- FIG. 2 is a perspective view of an example bleed system including an example muffling device
- FIG. 3 is a cross-sectional view of an example muffling device
- FIG. 4 is a partial-cutaway, perspective view of an example muffling device, all in accordance with at least some aspects of the present disclosure.
- the present disclosure includes, inter alia, muffling systems, and more specifically muffling devices capable of inducing high pressure drops and desirable flow properties.
- turbofan engines may use high-pressure/high-temperature bleed from the aft compressor stages to improve operability and performance.
- This bleed air may be directed into the fan duct or other locations, which may generate additional noise during some phases of engine operation.
- Some example embodiments according to the present disclosure provide a compact, lightweight transient/operability bleed exhaust muffling device (which may be referred to generally as a “pepperpot”) that has minimal acoustic impact. Acoustic benefit for the high pressure/temperature compressor discharge bleed may be achieved at a high exhaust velocity into the fan duct and, in some example embodiments, may use only a single flow conditioning element (which may be referred to as an “inner flow conditioner”) within the pepperpot body (which may be referred to as an “exhaust can”). Some such embodiments may be referred to as “single stage” muffling devices. The present disclosure contemplates that some “single stage” muffling devices are described in U.S. Provisional Patent Application No.
- acoustic pepperpots may utilize multiple (e.g., three to five or more) inner flow conditioning elements, which may add weight to the engine.
- the present disclosure contemplates that some other acoustically friendly pepperpots may necessitate extensive shielding on the thrust reverser structure to address thermal concerns.
- Some example embodiments according to the present disclosure may reduce or eliminate the need for such shielding by directing at least a substantial portion of the high-temperature bleed air generally to the middle of the cool fan duct flow, which may allow the hot plume to exit the fan duct without substantially impinging on thrust reverser or other aircraft surfaces.
- FIG. 1 is a schematic cross-sectional view of an example gas turbine engine assembly 10 including an example bleed system 40 including an example muffling device 50 , according to at least some aspects of the present disclosure.
- FIG. 2 is a perspective view of bleed system 40 including muffling device 50 , according to at least some aspects of the present disclosure.
- the gas turbine engine assembly 10 includes a core gas turbine engine 12 that includes a high-pressure compressor 14 , a combustor 16 , and a high-pressure turbine 18 .
- the gas turbine engine assembly 10 also includes a low-pressure turbine 20 coupled axially downstream from core gas turbine engine 12 and a fan assembly 22 coupled axially upstream from core gas turbine engine 12 .
- Fan assembly 22 includes an array of fan blades 24 that extend radially outward from a rotor disk.
- gas turbine engine assembly 10 has an intake side 28 and an exhaust side 29 .
- Core gas turbine engine 12 , fan assembly 22 , and low-pressure turbine 20 are coupled together by a first rotor shaft 31
- high-pressure compressor 14 and high-pressure turbine 18 are coupled together by a second rotor shaft 32 .
- the air discharged from fan assembly 22 is channeled to high-pressure compressor 14 where the airflow is further compressed and channeled to combustor 16 .
- Products of combustion from combustor 16 are utilized to drive high-pressure turbine 18 and low-pressure turbine 20 , and turbine 20 drives fan assembly 22 via shaft 31 .
- a portion of the compressed air may be routed through the bleed system 40 , thereby becoming bleed air 2 .
- Bleed air 2 from high-pressure compressor 14 may enter a bleed flow conduit 44 .
- Bleed air 2 may pass through the bleed flow conduit 44 and enter muffling device 50 that directs bleed air 2 into a flow path, such as the bypass flow path 4 and mixes that air with another flow, such as a fan flow stream 1 .
- Flow through bleed flow conduit 44 may be controlled by a bleed air valve 45 .
- Bleed flow conduit 44 may be made from a variety of materials, such as a metal, which may be selected to be capable of withstanding a bleed air 2 flow that is relatively hot and at high pressure.
- Muffling device 50 may be in flow communication with bleed flow conduit 44 such that the bleed air 2 is discharged as exit flow stream 5 into by-pass flow path 4 , facilitating a reduction of the noise generated by the mixing of the exit flow stream 5 and fan flow stream 1 .
- bleed flow conduit 44 may convey bleed air 2 from bleed air valve 45 to muffling device 50 .
- some or all of the acoustic improvements provided by this device occur within muffling device 50 , which may allow the use of relatively small diameter and lightweight ducting to direct the flow to a location very close to the exhaust can.
- FIG. 3 is a cross-sectional view of an example muffling device 50 , according to at least some aspects of the present disclosure.
- FIG. 4 is a partial-cutaway, perspective view of an example muffling device 50 , according to at least some aspects of the present disclosure.
- Muffling device 50 may comprise an exhaust can 102 , which may include an exhaust screen 104 (which may be generally circular) at a downstream end, an upstream end wall 126 (which may be generally annular), and a sidewall 128 (which may be generally circular).
- Exhaust can 102 may be generally in the form of a hollow circular cylinder arranged about a central axis 124 with a diameter 130 .
- Exhaust screen 104 may include a plurality of holes 106 through which air may be discharged from an interior 108 of exhaust can 102 . In some example embodiments, exhaust screen 104 may be outwardly curved.
- an inner flow conditioner 110 may be disposed within exhaust can 102 .
- Inner flow conditioner 110 may be generally in the form of a hollow, conical frustum arranged coaxially with exhaust can 102 about central axis 124 .
- Inner flow conditioner 110 may include an inwardly tapering sidewall 112 and a downstream end wall 114 , which may be generally circular.
- Sidewall 112 may be shaped generally as a truncated cone.
- Downstream end wall 114 may be generally orthogonal to central axis 124 .
- Inner flow conditioner 110 may taper inwardly from an upstream base 136 (which may be substantially circumscribed by upstream end wall 126 ) to a downstream base 138 (which may be proximate downstream end wall 114 ). Sidewall 112 and downstream end wall 114 may at least partially define an interior 116 of inner flow conditioner 110 . Sidewall 112 may include a plurality of generally laterally oriented holes 120 and/or downstream end wall 114 may include a plurality of generally axially oriented holes 122 through which pressurized air may be discharged into interior 108 of exhaust can 102 . Inner flow conditioner 110 may be arranged to receive pressurized air from bleed flow conduit 44 through an inlet 118 (which may be proximate upstream base 136 ).
- Inner flow conditioner 110 may have an upstream base diameter 132 proximate inlet 118 and/or downstream base diameter 134 proximate downstream end wall 114 .
- Upstream base diameter 132 may be larger than downstream base diameter 134 .
- Inner flow conditioner 110 may be attached inside exhaust can 102 such that inlet 118 is disposed within upstream end wall 126 of exhaust can 102 .
- Downstream base 138 may at least partially define a downstream end wall area 133 , which may be the generally axially downstream facing area of downstream end wall 114 .
- Downstream base 138 and exhaust can 102 may at least partially define a downstream end annular area 135 , which may be the generally axially downstream facing area between downstream end wall 114 and sidewall 128 of exhaust can 102 .
- a ratio of downstream end wall area 133 to downstream end annular area 135 may be about 0.12 to about 0.97.
- a ratio of downstream end wall area 133 to downstream end annular area 135 may be about 0.16 to about 0.28.
- a ratio of downstream end wall area 133 to downstream end annular area 135 may be about 0.17 to about 0.20.
- inner flow conditioner 110 and exhaust screen 102 may be configured to conduct pressurized air inward through inlet 118 into interior 116 of inner flow conditioner 110 , through holes 120 and/or holes 122 of inner flow conditioner 110 into interior 108 of exhaust can 102 , and outward through holes 106 of exhaust screen 104 .
- interior 108 of exhaust can 102 may be substantially devoid of flow obstructions between holes 120 and holes 122 of inner flow conditioner and holes 106 of exhaust screen 104 .
- An example muffling device 50 may include holes 106 , 120 , 122 having individual hole sizes (e.g., diameters and/or slot length/width) and areas.
- An individual hole may have an effective area for fluid flow that differs from its measurable physical area.
- a hole's effective area for fluid flow may be determined by known methods, and may depend on the size and shape of the hole.
- a plurality of holes, e.g., holes 106 of exhaust screen 104 may have an effective area for fluid flow that may be calculated using known methods.
- holes 120 of sidewall 112 of inner flow conditioner 110 may have an effective flow area and/or holes 122 of downstream end wall 114 of inner flow conditioner 110 may have an effective flow area.
- a ratio of downstream end annular area 135 to downstream end wall area 133 may be proportional, by a factor of about 0.8 to about 1.9, to a ratio of the effective area of holes 120 of sidewall 112 of inner flow conditioner 110 to the effective flow area of holes 122 of downstream end wall 114 of inner flow conditioner 110 .
- downstream ⁇ ⁇ end ⁇ ⁇ annular ⁇ ⁇ area ⁇ ⁇ 135 downstream ⁇ ⁇ end ⁇ ⁇ wall ⁇ ⁇ area ⁇ ⁇ 133 F * effective ⁇ ⁇ flow ⁇ ⁇ area ⁇ ⁇ of ⁇ ⁇ holes ⁇ ⁇ 120 effective ⁇ ⁇ flow ⁇ ⁇ area ⁇ ⁇ of ⁇ ⁇ holes ⁇ ⁇ 122
- F in some example embodiments, may be about 0.8 to about 1.9. In some example embodiments, F may be about 0.88 to about 1.58. In some example embodiments, F may be about 0.97 to about 1.26.
- a ratio of an effective flow area of the holes (e.g., holes 120 and holes 122 ) of an inner flow conditioner (e.g., inner flow conditioner 110 ) to an effective flow area of an inlet (e.g., inlet 118 ) may be about 0.7 to about 1.2. In some example embodiments according to at least some aspects of the present disclosure, a ratio of an effective flow area of the holes of the inner flow conditioner to an effective flow area of the inlet may be about 0.76 to about 0.91.
- inner flow conditioner 110 may be disposed within an exhaust can 102 such that airflow through holes 122 of downstream end wall 114 substantially dissipates before it reaches exhaust screen 104 of exhaust can 102 .
- downstream end wall 114 may be spaced from exhaust screen 104 by a dissipation distance 140 .
- One or more holes 122 through downstream end wall 114 may have a hole diameter 142 .
- a ratio of dissipation distance 140 to hole diameter 142 may be greater than 10.
- the ratio of dissipation distance 140 to hole diameter 142 may be greater than 15.
- the ratio of dissipation distance 140 to hole diameter 142 may be greater than 20.
- Some example embodiments according to at least some aspects of the present disclosure may be arranged such that air flow 144 approaching exhaust screen 104 may be substantially uniform across diameter 130 of exhaust can 102 .
- some example embodiments have been described in connection with discharging exit flow stream 5 into by-pass flow path 4 , it is within the scope of the disclosure to direct exit flow stream 5 elsewhere.
- some muffling devices according to the present disclosure may be mounted at the engine pylon, the turbine rear frame, and/or core nozzle/center bleed tube.
- Some example embodiments may be arranged to direct exit flow stream 5 generally behind gas turbine engine assembly 10 .
Abstract
Some example muffling devices may include an inner flow conditioner shaped as a generally conical frustrum and a generally cylindrical an exhaust can around the inner flow conditioner. A ratio of a downstream end wall area of the inner flow conditioner to a downstream end annular area between the downstream end wall and the exhaust can may be about 0.12 to about 0.97. A ratio of the downstream end annular area to the downstream end wall area may be proportional, by a factor of about 0.8 to about 1.9, to a ratio of an effective area of the inner flow conditioner sidewall holes to an effective area of the inner flow conditioner downstream end wall holes. A ratio of a dissipation distance between the inner flow conditioner downstream end wall and the exhaust screen to the inner flow conditioner downstream end wall hole diameter may be greater than about 10.
Description
- The subject matter disclosed herein relates generally to muffling systems, and, more specifically, to muffling devices capable of inducing high pressure drops and desirable flow properties.
- In a gas turbine engine, air is pressurized in a compression module during operation. The air channeled through the compression module is mixed with fuel in a combustor and ignited, generating hot combustion gases which flow through turbine stages that extract energy therefrom for powering the fan and compressor rotors and generate engine thrust to propel an aircraft in flight or to power a load, such as an electrical generator.
- In some gas turbine engines, a portion of the high-pressure air, such as, for example, bleed air from a compressor, may be extracted or bled from the compressor for various needs. These needs include, for example, compressor flow bleeding which may be used in order to improve operability as well as to provide turbine cooling, pressurize bearing sumps, purge air or provide aircraft environment control. The air may be bled off from the compressor using bleed slots located over specific portions or stages of the compressor.
- The problem: In least some gas turbine engines, during engine operation occurring in some operating conditions, the compressor may pump more air than is required for needs including the combustion process. In order to manage operability of the engine and combustion performance, a portion of the excess bleed air from the compressor may be routed through bleed conduits and exhausted into the by-pass flow stream, engine exhaust, or to ambient. The pressure and temperature of the air stream bled from the compressor may be very high. For example, bleed air pressure may be greater than about 1375 kPa and the bleed air temperature may be greater than about 538 degrees C. A transient bleed valve system (TBV) system is sometimes used for bleeding and exhausting the air removed from the compressor. Certain conventional designs for bleed exhaust systems use large and/or heavy muffling devices to reduce the generated noise. For example, the exhaust area of some conventional bleed systems may be set to lower the flow velocity at the exhaust location to a level below that required to meet the acoustic limits for the application. The exhaust area, as well as the relatively gently expansions between the source pressure and exhaust, may contribute to the relatively large size and/or weight of these systems. In some applications (e.g., aircraft), it may be undesirable to use large and/or heavy components.
- In addition, some conventional exhaust designs on aircraft may require extensive thermal shielding on other components near the exhaust location, once the exhaust velocities that meet the acoustic limits are achieved. Due to the nature of the high temperature air, once it is over-expanded to achieve lower velocities, the air it mixes with may overwhelm the bleed air, causing it to “lay down” on the surrounding structure around the engine. In some aircraft the surrounding structure may be made of lightweight composite material or of other metallic material with lesser temperature capability.
- At least one solution for the above-mentioned problem(s) is provided by the present disclosure to include example embodiments, provided for illustrative teaching and not meant to be limiting.
- An example muffling device according to at least some aspects of the present disclosure may include an inner flow conditioner shaped as a generally conical frustum including an upstream base and a downstream base. A diameter of the upstream base may be larger than a diameter of the downstream base. The inner flow conditioner may include an inlet approximate the upstream base, a generally circular inner flow conditioner downstream end wall having an inner flow conditioner downstream end wall area, the inner flow conditioner downstream end wall being generally orthogonal to a longitudinal axis of the conical frustum and comprising a plurality of generally longitudinally oriented inner flow conditioner downstream end wall holes, and an inner flow conditioner sidewall shaped generally as a truncated cone, the inner flow conditioner sidewall tapering inwardly from approximate the upstream base to approximate the inner flow conditioner downstream wall, the inner flow conditioner sidewall comprising a plurality of generally laterally oriented inner flow conditioner sidewall holes. The muffling device may include an exhaust can disposed substantially around the inner flow conditioner and shaped as a generally circular cylinder. The exhaust can may include a generally annular upstream end wall disposed approximate the upstream base of the inner flow conditioner and substantially circumscribing the upstream base of the inner flow conditioner, a generally circular exhaust screen comprising a plurality of exhaust screen holes, and a generally circular exhaust can sidewall extending from approximate the upstream end wall to approximate the exhaust screen. The inner flow conditioner and the exhaust can may be configured to conduct a fluid inward through the inlet into the inner flow conditioner, through the inner flow conditioner downstream end wall discharge openings and the inner flow conditioner sidewall discharge openings into the exhaust can, and outward through the exhaust screen discharge openings. The exhaust can and the inner flow conditioner downstream end wall may at least partially define a downstream end annular area therebetween. A ratio of the inner flow conditioner downstream end wall area to the downstream end annular area may be about 0.12 to about 0.97.
- An example muffling device according to at least some aspects of the present disclosure may include an inner flow conditioner shaped as a generally conical frustum including an upstream base and a downstream base. A diameter of the upstream base may be larger than a diameter of the downstream base. The inner flow conditioner may include an inlet approximate the upstream base, a generally circular inner flow conditioner downstream end wall having an inner flow conditioner downstream end wall area, the inner flow conditioner downstream end wall being generally orthogonal to a longitudinal axis of the conical frustum and comprising a plurality of generally longitudinally oriented inner flow conditioner downstream end wall holes, and an inner flow conditioner sidewall shaped generally as a truncated cone, the inner flow conditioner sidewall tapering inwardly from approximate the upstream base to approximate the inner flow conditioner downstream wall, the inner flow conditioner sidewall comprising a plurality of generally laterally oriented inner flow conditioner sidewall holes. The muffling device may include an exhaust can disposed substantially around the inner flow conditioner and shaped as a generally circular cylinder. The exhaust can may include a generally annular upstream end wall disposed approximate the upstream base of the inner flow conditioner and substantially circumscribing the upstream base of the inner flow conditioner, a generally circular exhaust screen comprising a plurality of exhaust screen holes, and a generally circular exhaust can sidewall extending from approximate the upstream end wall to approximate the exhaust screen. The inner flow conditioner and the exhaust can may be configured to conduct a fluid inward through the inlet into the inner flow conditioner, through the inner flow conditioner downstream end wall discharge openings and the inner flow conditioner sidewall discharge openings into the exhaust can, and outward through the exhaust screen discharge openings. The exhaust can and the inner flow conditioner downstream end wall may at least partially define a downstream end annular area therebetween. A ratio of the downstream end annular area to the downstream end wall area may be proportional, by a factor of about 0.8 to about 1.9, to a ratio of an effective area of the inner flow conditioner sidewall holes to an effective area of the inner flow conditioner downstream end wall holes.
- An example muffling device according to at least some aspects of the present disclosure may include an inner flow conditioner shaped as a generally conical frustum including an upstream base and a downstream base. A diameter of the upstream base may be larger than a diameter of the downstream base. The inner flow conditioner may include an inlet approximate the upstream base, a generally circular inner flow conditioner downstream end wall having an inner flow conditioner downstream end wall area, the inner flow conditioner downstream end wall being generally orthogonal to a longitudinal axis of the conical frustum and comprising a plurality of generally longitudinally oriented inner flow conditioner downstream end wall holes, and an inner flow conditioner sidewall shaped generally as a truncated cone, the inner flow conditioner sidewall tapering inwardly from approximate the upstream base to approximate the inner flow conditioner downstream wall, the inner flow conditioner sidewall comprising a plurality of generally laterally oriented inner flow conditioner sidewall holes. The muffling device may include an exhaust can disposed substantially around the inner flow conditioner and shaped as a generally circular cylinder. The exhaust can may include a generally annular upstream end wall disposed approximate the upstream base of the inner flow conditioner and substantially circumscribing the upstream base of the inner flow conditioner, a generally circular exhaust screen comprising a plurality of exhaust screen holes, and a generally circular exhaust can sidewall extending from approximate the upstream end wall to approximate the exhaust screen. The inner flow conditioner and the exhaust can may be configured to conduct a fluid inward through the inlet into the inner flow conditioner, through the inner flow conditioner downstream end wall discharge openings and the inner flow conditioner sidewall discharge openings into the exhaust can, and outward through the exhaust screen discharge openings. The exhaust can and the inner flow conditioner downstream end wall may at least partially define a downstream end annular area therebetween. The inner flow conditioner downstream end wall holes may have an inner flow conditioner downstream end wall hole diameter. The inner flow conditioner downstream end wall may be spaced from the exhaust screen by a dissipation distance. A ratio of the dissipation distance to the inner flow conditioner downstream end wall hole diameter may be greater than about 10.
- The subject matter for which patent claim coverage is sought is particularly pointed out and claimed herein. The subject matter and embodiments thereof, however, may be best understood by reference to the following description taken in conjunction with the accompanying drawing figures in which:
-
FIG. 1 is a schematic cross-sectional view of an example gas turbine engine assembly including an example bleed system including an example muffling device; -
FIG. 2 is a perspective view of an example bleed system including an example muffling device; -
FIG. 3 is a cross-sectional view of an example muffling device; and -
FIG. 4 is a partial-cutaway, perspective view of an example muffling device, all in accordance with at least some aspects of the present disclosure. - In the following detailed description, reference is made to the accompanying drawings, which form a part hereof. In the drawings, similar symbols typically identify similar components, unless context dictates otherwise. The illustrative embodiments described in the detailed description, drawings, and claims are not meant to be limiting. Other embodiments may be utilized, and other changes may be made, without departing from the spirit or scope of the subject matter presented here. It will be readily understood that the aspects of the present disclosure, as generally described herein, and illustrated in the figures, can be arranged, substituted, combined, and designed in a wide variety of different configurations, all of which are explicitly contemplated and make part of this disclosure.
- The present disclosure includes, inter alia, muffling systems, and more specifically muffling devices capable of inducing high pressure drops and desirable flow properties.
- The present disclosure contemplates that modern, highly efficient turbofan engines may use high-pressure/high-temperature bleed from the aft compressor stages to improve operability and performance. This bleed air may be directed into the fan duct or other locations, which may generate additional noise during some phases of engine operation.
- Some example embodiments according to the present disclosure provide a compact, lightweight transient/operability bleed exhaust muffling device (which may be referred to generally as a “pepperpot”) that has minimal acoustic impact. Acoustic benefit for the high pressure/temperature compressor discharge bleed may be achieved at a high exhaust velocity into the fan duct and, in some example embodiments, may use only a single flow conditioning element (which may be referred to as an “inner flow conditioner”) within the pepperpot body (which may be referred to as an “exhaust can”). Some such embodiments may be referred to as “single stage” muffling devices. The present disclosure contemplates that some “single stage” muffling devices are described in U.S. Provisional Patent Application No. 61/580,675, titled COMPACT HIGH-PRESSURE EXHAUST MUFFLING DEVICES, filed Dec. 28, 2011, and U.S. patent application Ser. No. 13/347,728, titled COMPACT HIGH-PRESSURE EXHAUST MUFFLING DEVICES, filed Jan. 11, 2012, which are incorporated herein by reference. The present disclosure contemplates that some other acoustic pepperpots may utilize multiple (e.g., three to five or more) inner flow conditioning elements, which may add weight to the engine.
- In addition, the present disclosure contemplates that some other acoustically friendly pepperpots may necessitate extensive shielding on the thrust reverser structure to address thermal concerns. Some example embodiments according to the present disclosure may reduce or eliminate the need for such shielding by directing at least a substantial portion of the high-temperature bleed air generally to the middle of the cool fan duct flow, which may allow the hot plume to exit the fan duct without substantially impinging on thrust reverser or other aircraft surfaces.
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FIG. 1 is a schematic cross-sectional view of an example gasturbine engine assembly 10 including anexample bleed system 40 including anexample muffling device 50, according to at least some aspects of the present disclosure.FIG. 2 is a perspective view ofbleed system 40 including mufflingdevice 50, according to at least some aspects of the present disclosure. The gasturbine engine assembly 10 includes a coregas turbine engine 12 that includes a high-pressure compressor 14, acombustor 16, and a high-pressure turbine 18. In the example embodiment shown inFIG. 1 , the gasturbine engine assembly 10 also includes a low-pressure turbine 20 coupled axially downstream from coregas turbine engine 12 and afan assembly 22 coupled axially upstream from coregas turbine engine 12.Fan assembly 22 includes an array offan blades 24 that extend radially outward from a rotor disk. In the exemplary embodiment shown inFIG. 1 , gasturbine engine assembly 10 has anintake side 28 and anexhaust side 29. Coregas turbine engine 12,fan assembly 22, and low-pressure turbine 20 are coupled together by afirst rotor shaft 31, and high-pressure compressor 14 and high-pressure turbine 18 are coupled together by asecond rotor shaft 32. - In operation, air flows through
fan blades 24 and is supplied to high-pressure compressor 14. The air discharged fromfan assembly 22 is channeled to high-pressure compressor 14 where the airflow is further compressed and channeled tocombustor 16. Products of combustion fromcombustor 16 are utilized to drive high-pressure turbine 18 and low-pressure turbine 20, andturbine 20 drivesfan assembly 22 viashaft 31. - In an example gas
turbine engine assembly 10, at certain operating conditions, a portion of the compressed air may be routed through thebleed system 40, thereby becomingbleed air 2. Bleedair 2 from high-pressure compressor 14 may enter ableed flow conduit 44. Bleedair 2 may pass through thebleed flow conduit 44 and enter mufflingdevice 50 that directs bleedair 2 into a flow path, such as thebypass flow path 4 and mixes that air with another flow, such as afan flow stream 1. Flow throughbleed flow conduit 44 may be controlled by ableed air valve 45. Bleedflow conduit 44 may be made from a variety of materials, such as a metal, which may be selected to be capable of withstanding ableed air 2 flow that is relatively hot and at high pressure. - Muffling
device 50, described in more detail herein below, may be in flow communication withbleed flow conduit 44 such that thebleed air 2 is discharged asexit flow stream 5 into by-pass flow path 4, facilitating a reduction of the noise generated by the mixing of theexit flow stream 5 andfan flow stream 1. - As shown in
FIG. 2 , bleedflow conduit 44 may convey bleedair 2 frombleed air valve 45 to mufflingdevice 50. In some example embodiments according to at least some aspects of the present disclosure, some or all of the acoustic improvements provided by this device occur within mufflingdevice 50, which may allow the use of relatively small diameter and lightweight ducting to direct the flow to a location very close to the exhaust can. -
FIG. 3 is a cross-sectional view of anexample muffling device 50, according to at least some aspects of the present disclosure.FIG. 4 is a partial-cutaway, perspective view of anexample muffling device 50, according to at least some aspects of the present disclosure. Mufflingdevice 50 may comprise an exhaust can 102, which may include an exhaust screen 104 (which may be generally circular) at a downstream end, an upstream end wall 126 (which may be generally annular), and a sidewall 128 (which may be generally circular). Exhaust can 102 may be generally in the form of a hollow circular cylinder arranged about acentral axis 124 with adiameter 130.Exhaust screen 104 may include a plurality ofholes 106 through which air may be discharged from an interior 108 of exhaust can 102. In some example embodiments,exhaust screen 104 may be outwardly curved. - In some example embodiments according to at least some aspects of the present disclosure, an
inner flow conditioner 110 may be disposed within exhaust can 102.Inner flow conditioner 110 may be generally in the form of a hollow, conical frustum arranged coaxially with exhaust can 102 aboutcentral axis 124.Inner flow conditioner 110 may include an inwardly taperingsidewall 112 and adownstream end wall 114, which may be generally circular.Sidewall 112 may be shaped generally as a truncated cone.Downstream end wall 114 may be generally orthogonal tocentral axis 124.Inner flow conditioner 110 may taper inwardly from an upstream base 136 (which may be substantially circumscribed by upstream end wall 126) to a downstream base 138 (which may be proximate downstream end wall 114).Sidewall 112 anddownstream end wall 114 may at least partially define an interior 116 ofinner flow conditioner 110.Sidewall 112 may include a plurality of generally laterally orientedholes 120 and/ordownstream end wall 114 may include a plurality of generally axially orientedholes 122 through which pressurized air may be discharged intointerior 108 of exhaust can 102.Inner flow conditioner 110 may be arranged to receive pressurized air frombleed flow conduit 44 through an inlet 118 (which may be proximate upstream base 136).Inner flow conditioner 110 may have anupstream base diameter 132proximate inlet 118 and/ordownstream base diameter 134 proximatedownstream end wall 114.Upstream base diameter 132 may be larger thandownstream base diameter 134.Inner flow conditioner 110 may be attached inside exhaust can 102 such thatinlet 118 is disposed withinupstream end wall 126 of exhaust can 102. -
Downstream base 138 may at least partially define a downstreamend wall area 133, which may be the generally axially downstream facing area ofdownstream end wall 114.Downstream base 138 and exhaust can 102 may at least partially define a downstream endannular area 135, which may be the generally axially downstream facing area betweendownstream end wall 114 andsidewall 128 of exhaust can 102. In some example embodiments, a ratio of downstreamend wall area 133 to downstream endannular area 135 may be about 0.12 to about 0.97. In some example embodiments, a ratio of downstreamend wall area 133 to downstream endannular area 135 may be about 0.16 to about 0.28. In some example embodiments, a ratio of downstreamend wall area 133 to downstream endannular area 135 may be about 0.17 to about 0.20. - In operation,
inner flow conditioner 110 andexhaust screen 102 may be configured to conduct pressurized air inward throughinlet 118 intointerior 116 ofinner flow conditioner 110, throughholes 120 and/orholes 122 ofinner flow conditioner 110 intointerior 108 of exhaust can 102, and outward throughholes 106 ofexhaust screen 104. In some example embodiments,interior 108 of exhaust can 102 may be substantially devoid of flow obstructions betweenholes 120 andholes 122 of inner flow conditioner and holes 106 ofexhaust screen 104. - An
example muffling device 50 may includeholes exhaust screen 104, may have an effective area for fluid flow that may be calculated using known methods. For example, holes 120 ofsidewall 112 ofinner flow conditioner 110 may have an effective flow area and/orholes 122 ofdownstream end wall 114 ofinner flow conditioner 110 may have an effective flow area. - In some example embodiments according to at least some aspects of the present disclosure, a ratio of downstream end
annular area 135 to downstreamend wall area 133 may be proportional, by a factor of about 0.8 to about 1.9, to a ratio of the effective area ofholes 120 ofsidewall 112 ofinner flow conditioner 110 to the effective flow area ofholes 122 ofdownstream end wall 114 ofinner flow conditioner 110. Expressed mathematically, -
- where F, in some example embodiments, may be about 0.8 to about 1.9. In some example embodiments, F may be about 0.88 to about 1.58. In some example embodiments, F may be about 0.97 to about 1.26.
- In some example embodiments according to at least some aspects of the present disclosure, a ratio of an effective flow area of the holes (e.g., holes 120 and holes 122) of an inner flow conditioner (e.g., inner flow conditioner 110) to an effective flow area of an inlet (e.g., inlet 118) may be about 0.7 to about 1.2. In some example embodiments according to at least some aspects of the present disclosure, a ratio of an effective flow area of the holes of the inner flow conditioner to an effective flow area of the inlet may be about 0.76 to about 0.91.
- In some example embodiments according to at least some aspects of the present disclosure,
inner flow conditioner 110 may be disposed within an exhaust can 102 such that airflow throughholes 122 ofdownstream end wall 114 substantially dissipates before it reachesexhaust screen 104 of exhaust can 102. For example,downstream end wall 114 may be spaced fromexhaust screen 104 by adissipation distance 140. One ormore holes 122 throughdownstream end wall 114 may have ahole diameter 142. In some example embodiments, a ratio ofdissipation distance 140 to holediameter 142 may be greater than 10. In some example embodiments, the ratio ofdissipation distance 140 to holediameter 142 may be greater than 15. In some example embodiments, the ratio ofdissipation distance 140 to holediameter 142 may be greater than 20. - Some example embodiments according to at least some aspects of the present disclosure may be arranged such that
air flow 144 approachingexhaust screen 104 may be substantially uniform acrossdiameter 130 of exhaust can 102. - Although some example embodiments have been described in connection with discharging
exit flow stream 5 into by-pass flow path 4, it is within the scope of the disclosure to directexit flow stream 5 elsewhere. For example, some muffling devices according to the present disclosure may be mounted at the engine pylon, the turbine rear frame, and/or core nozzle/center bleed tube. Some example embodiments may be arranged to directexit flow stream 5 generally behind gasturbine engine assembly 10. - This written description uses examples to disclose the invention, including the best mode, and also to enable any person skilled in the art to practice the invention, including making and using any devices or systems and performing any incorporated methods. The patentable scope of the invention is defined by the claims, and may include other examples that occur to those skilled in the art. Such other examples are intended to be within the scope of the claims if they have structural elements that do not differ from the literal language of the claims, or if they include equivalent structural elements with insubstantial differences from the literal languages of the claims.
Claims (20)
1. A muffling device, comprising:
an inner flow conditioner shaped as a generally conical frustum comprising an upstream base and a downstream base, a diameter of the upstream base being larger than a diameter of the downstream base, the inner flow conditioner comprising
an inlet approximate the upstream base,
a generally circular inner flow conditioner downstream end wall having an inner flow conditioner downstream end wall area, the inner flow conditioner downstream end wall being generally orthogonal to a longitudinal axis of the conical frustum and comprising a plurality of generally longitudinally oriented inner flow conditioner downstream end wall holes, and
an inner flow conditioner sidewall shaped generally as a truncated cone, the inner flow conditioner sidewall tapering inwardly from approximate the upstream base to approximate the inner flow conditioner downstream wall, the inner flow conditioner sidewall comprising a plurality of generally laterally oriented inner flow conditioner sidewall holes; and
an exhaust can disposed substantially around the inner flow conditioner and shaped as a generally circular cylinder, the exhaust can comprising
a generally annular upstream end wall disposed approximate the upstream base of the inner flow conditioner and substantially circumscribing the upstream base of the inner flow conditioner,
a generally circular exhaust screen comprising a plurality of exhaust screen holes, and
a generally circular exhaust can sidewall extending from approximate the upstream end wall to approximate the exhaust screen;
wherein the inner flow conditioner and the exhaust can are configured to conduct a fluid inward through the inlet into the inner flow conditioner, through the inner flow conditioner downstream end wall discharge openings and the inner flow conditioner sidewall discharge openings into the exhaust can, and outward through the exhaust screen discharge openings;
wherein the exhaust can and the inner flow conditioner downstream end wall at least partially define a downstream end annular area therebetween; and
wherein a ratio of the inner flow conditioner downstream end wall area to the downstream end annular area is about 0.12 to about 0.97.
2. The muffling device of claim 1 , wherein the ratio of the inner flow conditioner downstream end wall area to the downstream end annular area is about 0.16 to about 0.28.
3. The muffling device of claim 1 , wherein the ratio of the inner flow conditioner downstream end wall area to the downstream end annular area is about 0.17 to about 0.20.
4. The muffling device of claim 1 , wherein a ratio of the downstream end annular area to the downstream end wall area is proportional, by a factor of about 0.8 to about 1.9, to a ratio of an effective area of the inner flow conditioner sidewall holes to an effective area of the inner flow conditioner downstream end wall holes.
5. The muffling device of claim 1 , wherein a ratio of the downstream end annular area to the downstream end wall area is proportional, by a factor of about 0.97 to about 1.26, to a ratio of an effective area of the inner flow conditioner sidewall holes to an effective area of the inner flow conditioner downstream end wall holes.
6. The muffling device of claim 1 ,
wherein the inner flow conditioner downstream end wall holes have an inner flow conditioner downstream end wall hole diameter;
wherein the inner flow conditioner downstream end wall is spaced from the exhaust screen by a dissipation distance; and
wherein a ratio of the dissipation distance to the inner flow conditioner downstream end wall hole diameter is greater than about 10.
7. The muffling device of claim 1 ,
wherein the inner flow conditioner downstream end wall holes have an inner flow conditioner downstream end wall hole diameter;
wherein the inner flow conditioner downstream end wall is spaced from the exhaust screen by a dissipation distance; and
wherein a ratio of the dissipation distance to the inner flow conditioner downstream end wall hole diameter is greater than about 20.
8. A muffling device, comprising:
an inner flow conditioner shaped as a generally conical frustum comprising an upstream base and a downstream base, a diameter of the upstream base being larger than a diameter of the downstream base, the inner flow conditioner comprising
an inlet approximate the upstream base,
a generally circular inner flow conditioner downstream end wall having an inner flow conditioner downstream end wall area, the inner flow conditioner downstream end wall being generally orthogonal to a longitudinal axis of the conical frustum and comprising a plurality of generally longitudinally oriented inner flow conditioner downstream end wall holes, and
an inner flow conditioner sidewall shaped generally as a truncated cone, the inner flow conditioner sidewall tapering inwardly from approximate the upstream base to approximate the inner flow conditioner downstream wall, the inner flow conditioner sidewall comprising a plurality of generally laterally oriented inner flow conditioner sidewall holes; and
an exhaust can disposed substantially around the inner flow conditioner and shaped as a generally circular cylinder, the exhaust can comprising
a generally annular upstream end wall disposed approximate the upstream base of the inner flow conditioner and substantially circumscribing the upstream base of the inner flow conditioner,
a generally circular exhaust screen comprising a plurality of exhaust screen holes, and
a generally circular exhaust can sidewall extending from approximate the upstream end wall to approximate the exhaust screen;
wherein the inner flow conditioner and the exhaust can are configured to conduct a fluid inward through the inlet into the inner flow conditioner, through the inner flow conditioner downstream end wall discharge openings and the inner flow conditioner sidewall discharge openings into the exhaust can, and outward through the exhaust screen discharge openings;
wherein the exhaust can and the inner flow conditioner downstream end wall at least partially define a downstream end annular area therebetween; and
wherein a ratio of the downstream end annular area to the downstream end wall area is proportional, by a factor of about 0.8 to about 1.9, to a ratio of an effective area of the inner flow conditioner sidewall holes to an effective area of the inner flow conditioner downstream end wall holes.
9. The muffling device of claim 8 , wherein the ratio of the downstream end annular area to the downstream end wall area is proportional, by a factor of about 0.88 to about 1.58, to the ratio of the effective area of the inner flow conditioner sidewall holes to the effective area of the inner flow conditioner downstream end wall holes.
10. The muffling device of claim 8 , wherein the ratio of the downstream end annular area to the downstream end wall area is proportional, by a factor of about 0.97 to about 1.26, to the ratio of the effective area of the inner flow conditioner sidewall holes to the effective area of the inner flow conditioner downstream end wall holes.
11. The muffling device of claim 8 , wherein a ratio of the inner flow conditioner downstream end wall area to the downstream end annular area is about 0.17 to about 0.20.
12. The muffling device of claim 8 ,
wherein the inner flow conditioner downstream end wall holes have an inner flow conditioner downstream end wall hole diameter;
wherein the inner flow conditioner downstream end wall is spaced from the exhaust screen by a dissipation distance; and
wherein a ratio of the dissipation distance to the inner flow conditioner downstream end wall hole diameter is greater than about 10.
13. The muffling device of claim 8 ,
wherein the inner flow conditioner downstream end wall holes have an inner flow conditioner downstream end wall hole diameter;
wherein the inner flow conditioner downstream end wall is spaced from the exhaust screen by a dissipation distance; and
wherein a ratio of the dissipation distance to the inner flow conditioner downstream end wall hole diameter is greater than about 20.
14. A muffling device, comprising:
an inner flow conditioner shaped as a generally conical frustum comprising an upstream base and a downstream base, a diameter of the upstream base being larger than a diameter of the downstream base, the inner flow conditioner comprising
an inlet approximate the upstream base,
a generally circular inner flow conditioner downstream end wall having an inner flow conditioner downstream end wall area, the inner flow conditioner downstream end wall being generally orthogonal to a longitudinal axis of the conical frustum and comprising a plurality of generally longitudinally oriented inner flow conditioner downstream end wall holes, and
an inner flow conditioner sidewall shaped generally as a truncated cone, the inner flow conditioner sidewall tapering inwardly from approximate the upstream base to approximate the inner flow conditioner downstream wall, the inner flow conditioner sidewall comprising a plurality of generally laterally oriented inner flow conditioner sidewall holes; and
an exhaust can disposed substantially around the inner flow conditioner and shaped as a generally circular cylinder, the exhaust can comprising
a generally annular upstream end wall disposed approximate the upstream base of the inner flow conditioner and substantially circumscribing the upstream base of the inner flow conditioner,
a generally circular exhaust screen comprising a plurality of exhaust screen holes, and
a generally circular exhaust can sidewall extending from approximate the upstream end wall to approximate the exhaust screen;
wherein the inner flow conditioner and the exhaust can are configured to conduct a fluid inward through the inlet into the inner flow conditioner, through the inner flow conditioner downstream end wall discharge openings and the inner flow conditioner sidewall discharge openings into the exhaust can, and outward through the exhaust screen discharge openings;
wherein the exhaust can and the inner flow conditioner downstream end wall at least partially define a downstream end annular area therebetween;
wherein the inner flow conditioner downstream end wall holes have an inner flow conditioner downstream end wall hole diameter;
wherein the inner flow conditioner downstream end wall is spaced from the exhaust screen by a dissipation distance; and
wherein a ratio of the dissipation distance to the inner flow conditioner downstream end wall hole diameter is greater than about 10.
15. The muffling device of claim 14 , wherein a ratio of the dissipation distance to the inner flow conditioner downstream end wall hole diameter is greater than about 15.
16. The muffling device of claim 14 , wherein a ratio of the dissipation distance to the inner flow conditioner downstream end wall hole diameter is greater than about 20.
17. The muffling device of claim 14 , wherein a ratio of the inner flow conditioner downstream end wall area to the downstream end annular area is about 0.16 to about 0.28.
18. The muffling device of claim 14 , wherein a ratio of the inner flow conditioner downstream end wall area to the downstream end annular area is about 0.17 to about 0.20.
19. The muffling device of claim 14 , wherein a ratio of the downstream end annular area to the downstream end wall area is proportional, by a factor of about 0.88 to about 1.58, to a ratio of an effective area of the inner flow conditioner sidewall holes to an effective area of the inner flow conditioner downstream end wall holes.
20. The muffling device of claim 14 , wherein a ratio of the downstream end annular area to the downstream end wall area is proportional, by a factor of about 0.97 to about 1.26, to a ratio of an effective area of the inner flow conditioner sidewall holes to an effective area of the inner flow conditioner downstream end wall holes.
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Also Published As
Publication number | Publication date |
---|---|
WO2014018126A3 (en) | 2014-04-03 |
CN104334835B (en) | 2016-12-07 |
JP2015521244A (en) | 2015-07-27 |
JP6018293B2 (en) | 2016-11-02 |
WO2014018126A2 (en) | 2014-01-30 |
US8550208B1 (en) | 2013-10-08 |
CA2870604C (en) | 2017-02-14 |
EP2841714A2 (en) | 2015-03-04 |
CN104334835A (en) | 2015-02-04 |
CA2870604A1 (en) | 2014-01-30 |
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