Soundproofing and cooling arrangement with a fiber medium.

专利摘要:
The invention provides an assembly (100) having a fibrous medium (102) having a plurality of substantially corrugated channels (106) therein, the plurality of substantially corrugated channels (106) being permeable to a flow of fluid (104) therethrough; a manifold (110) in contact with the fibrous medium (102) and having an opening (112) therein for passing a liquid coolant through the manifold (110); and at least two acoustic shields (122) coupled to the fibrous medium (102) and located on opposite sides of the manifold (110). With the arrangement (100), the fluid (102) can be cooled in a passage (24). In this case, the arrangement (100) suppress acoustic waves that would otherwise escape through the passage (24) from a machine.
公开号:CH710051A2
申请号:CH01175/15
申请日:2015-08-14
公开日:2016-02-29
发明作者:Hua Zhang；Joshua Shane Sater；Jianmin Zhang；Valery Ivanovich Ponyavin
申请人:Gen Electric；
IPC主号:

专利说明:

BACKGROUND OF THE INVENTION
The disclosure relates generally to noise attenuation and cooling in a working fluid, such as the intake air of a turbomachine. More precisely, the disclosure relates to arrangements with a fiber medium that provide sound absorption and, in addition, cooling in a turbine.
Conventional turbine systems are often used to generate electricity, for example for electric generators. A working fluid, such as hot gas or steam, can be forced across sets of turbine blades that are coupled to a rotor of the turbine system. The force of the working fluid on the blades sets these blades (and the body of the rotor coupled to them) in rotation. In many cases the rotor body is coupled to the drive shaft of a dynamo-electric machine such as an electric generator. In this sense, the initial rotation of the turbine system rotor can also rotate the drive shaft in the electric generator to produce an electric current (associated with a power output).
Variables such as efficiency, power output and the risk of failure of the turbine are at least partially dependent on the internal temperature of certain components and passages such as inlets, outlets, etc. The temperature of a working fluid flowing through the turbine system influences performance such as the torque generated and / or the electricity generated. Designing a turbine system so that it has a certain operating temperature can improve these performances. The process of regulating operating temperatures in order to increase the output of a system can be referred to as “increasing turbine output”. Various cooling systems can be used to manage the temperature of a turbine system.
Another set of variables that can affect the performance and safety of a turbine, particularly in a gas turbine, are dynamic outputs (i.e., noise) generated by the turbine during operation. The noise generated may be due to the different operating characteristics, e.g. the higher peripheral speed of the compressor rotor in a land-based gas turbine must be greater than in other types of turbomachinery. Thus, some materials or components of a turbine can be designed or selected based on their ability to suppress acoustic waves.
BRIEF DESCRIPTION OF THE INVENTION
[0005] Muffling and cooling arrangements are discussed herein that include a fibrous medium. While embodiments of the disclosure are discussed herein with reference to turbine applications by way of example, it should be understood that embodiments of the present disclosure are applicable to other situations, e.g. any machine with an air passage to accommodate temperature cooling and noise cancellation.
A first aspect of the invention provides an assembly that may include: a fibrous medium having a plurality of substantially corrugated channels therein, the plurality of substantially corrugated channels permeable to a flow of fluid therethrough; a manifold in contact with the fibrous medium having an opening therein for admitting a liquid coolant through the manifold; and at least two acoustic shields coupled to the fibrous media and located near opposite sides of the manifold.
In any embodiment of the arrangement, it can be advantageous that the arrangement further comprises a coolant collecting trough in fluid communication with the fiber medium.
In any embodiment of the arrangement, it may be advantageous that the arrangement further comprises a coolant tube coupled to the manifold in which a flush valve is arranged, the flush valve optionally preventing or allowing a flow of the liquid coolant from the arrangement.
In any embodiment of the arrangement, it can be advantageous that the arrangement further comprises a splash guard coupled to the distributor.
In any embodiment of the arrangement, it can be advantageous for the fiber medium to have a density between about 40 kilograms per cubic meter (kg / m 3) and about 450 kg / m 3.
In any embodiment of the arrangement, it can be advantageous that a curvature of one of the plurality of essentially corrugated channels suppresses a transmission of sound through it.
In any embodiment of the arrangement, it can be advantageous for the fiber medium to contain a plurality of fiber boards arranged in a stack.
A second aspect of the invention provides a turbine component comprising: a passage configured to pass air flow from a compressor; a fibrous medium located in the passageway, the fibrous medium having a plurality of substantially corrugated channels therein, each of the plurality of substantially corrugated channels being permeable to the flow of air; a manifold in contact with the fiber medium and having an opening therein for the passage of a liquid coolant through the manifold; and at least two acoustic shields coupled to the fibrous media and located near opposite sides of the manifold.
In any embodiment of the turbine component, it can be advantageous that the turbine component also has a coolant collecting trough in contact with the fiber medium.
In any embodiment of the turbine component, it can be advantageous that a curvature of one of the plurality of essentially corrugated channels suppresses a transmission of sound therethrough.
In any embodiment of the turbine component, it can be advantageous that the turbine component further comprises a splash guard coupled to the distributor.
In any embodiment of the turbine component, it can be advantageous that the fiber medium has a density between about 40 kilograms per cubic meter (kg / m 3) and about 450 kg / m 3.
In any embodiment of the turbine component, it can be advantageous that the flow of compressed air through the fiber medium comes into contact with part of the liquid coolant in the fiber medium, so that it evaporates.
In any embodiment of the turbine component, it can be advantageous for the fiber medium to have several fiber boards arranged in a stack.
A third aspect of the invention provides a combined cycle gas and steam power plant with an arrangement positioned in a fluid flow section of one of a gas turbine, a heat recovery stream generator (HRSG) and a steam turbine, the An assembly comprising: a fibrous medium having a plurality of substantially corrugated channels therein, the substantially corrugated channels permeable to a flow of fluid therethrough, a manifold in contact with the fibrous medium and having an opening therein for passage of a liquid coolant through the manifold; and at least two acoustic shields coupled to the fibrous media and located near opposite sides of the manifold.
In any embodiment of the combined cycle power plant, it can be advantageous for the flow of fluid through the fiber medium to come into contact with part of the liquid coolant in the fiber medium, so that it evaporates.
In any embodiment of the combined cycle power plant, it can be advantageous that a curvature of one of the plurality of essentially corrugated channels suppresses a transmission of sound through them.
In any embodiment of the combined cycle power plant, it can be advantageous for the combined cycle power plant to further comprise a spray protection cover coupled to the distributor.
In any embodiment of the combined cycle power plant, it can be advantageous for the fiber medium to have a density between about 40 kilograms per cubic meter (kg / m 3) and about 450 kg / m 3.
In any embodiment of the combined cycle power plant, it can be advantageous that the fiber medium comprises several fiber boards arranged in a stack.
BRIEF DESCRIPTION OF THE DRAWINGS
These and other features of the present invention will become better understood from the following detailed description of the various aspects of the invention in conjunction with the accompanying drawings which illustrate various aspects of the invention. 1 shows a schematic view of electricity generation according to an embodiment of the present disclosure; 2 shows a perspective view of a sound damping and cooling arrangement according to an embodiment of the present disclosure; 3 shows a perspective view of a coolant supply system according to an embodiment of the present disclosure; 4 shows a perspective partial view of a fiber medium consisting of plates according to an embodiment of the present disclosure; 5 is a cross-sectional view of a fiber medium with channels between plates in accordance with an embodiment of the present disclosure; 6 is a schematic view of parts of a multi-shaft combined cycle power plant according to an embodiment of the present disclosure; 7 shows a schematic view of parts of a multi-shaft combined cycle power plant according to embodiments of the present disclosure; 8 is a schematic diagram of the behavior of acoustic waves in a fiber medium according to an embodiment of the present disclosure; 9 shows a curve of the sound suppression in a fiber medium according to an embodiment of the present disclosure.
It is noted that the drawings of the invention are not necessarily to scale. The drawings are only intended to illustrate typical aspects of the invention and are therefore not to be regarded as limiting the scope of the invention. In the drawings, like numbers refer to like elements in the drawings.
DETAILED DESCRIPTION OF THE INVENTION
The aspects of the invention discussed herein generally relate to the provision of cooling and noise suppression in mechanical plants and equipment. More particularly, the aspects of the invention discussed herein relate to a sound deadening and cooling arrangement having a fibrous medium.
Fig. 1 shows a power generation plant 10 in the form of a turbo machine. The power plant 10 is exemplified as a combustion assisted turbomachine assembly, although embodiments of the present disclosure may be designed for use with other types of turbomachines (steam turbines, wind turbines, water turbines, etc.). In combustion-assisted turbomachines, a combustion chamber 12 connected to a fuel nozzle 14 is typically located between the compressor 16 and the turbine 18 of the power generation plant 10. The compressor 16 and the turbine 18 can be mechanically coupled to one another via a rotatable shaft 20. Air 22 flows successively through the compressor 16, the combustion chamber 12 and finally through the turbine 18. The compression achieved by the compressor 16 can also increase the temperature of the air 22. The fuel nozzle 14 can supply fuel which burns in the presence of air 22 in the combustion chamber 12 in order to generate a hot gas flow. Combustion reactions in the combustion chamber 12 generate acoustic waves as a dynamic output. The hot gas flow can enter the turbine 18 in order to apply mechanical energy to the rotatable shaft 20 in order to thereby lead power back to the compressor 16 and / or to loads (not shown) possibly coupled to the rotatable shaft (20). The power plant may have a passage between the compressor 16 and the combustion chamber 12 through which air compressed in the compressor 16 passes before it burns. The power plant 10 can be one of several individual turbomachines controlled by the same operator and / or can be part of a larger power plant. Larger machinery that may include power plant 10 is discussed in detail elsewhere herein.
FIG. 2 shows an arrangement 100 according to embodiments of the present disclosure. Embodiments of the arrangement 100 can suppress noise generated by a turbine system and can additionally absorb heat from fluids that pass between components of the power generation system 10 (FIG. 1) (e.g. cooling air entering through the passage (FIG. 1) between the compressor 16 ( Fig. 1) and the combustion chamber 12 (Fig. 1) flows). With respect to the power plant 10 (Fig. 1), the compressor 16 (Fig. 1) may generate acoustic waves of substantial volume (ie, a sound pressure ratio between about thirty and fifty decibels (dB)) from the power plant 10 (Fig. 1) . Embodiments of the arrangement 100 can suppress these acoustic waves and can prevent them from affecting other components, devices, etc. that are located outside the power generation plant 10 (FIG. 1) in order to meet the requirements for the development of noise in power plants. In addition, embodiments of the arrangement 100 can cool pressurized fluids for the compressor 16 (FIG. 1), the temperature of which increases after the compression. The arrangement 100 combines the features of cooling an air flow in the passage 24 with the acoustic suppression of sound waves that also traverse the passage 24.
In operation, the assembly 100 can cool fluids in passage 24 while suppressing acoustic waves that would otherwise exit a machine (e.g., power plant 10) through passage 24. While certain embodiments of the assembly 100 are illustrated in the accompanying drawings and discussed herein by way of example, it should be understood that the assembly 100 may include a number of different structures employing the same or similar concepts. The assembly 100 may include a medium (e.g., multiple sheets, mesh, tile, or other layer) of fibers positioned substantially across a cross section of the passage 24. Space between the fibers of the medium can create multiple channels through the medium of the assembly 100 through which fluids in the passage 24 can pass. These channels can be essentially corrugated, so that acoustic waves in the passage 24 have no direct line of passage and are suppressed or blocked or at least attenuated by the fiber medium of the arrangement 100. Spaces between fibers of the fibrous medium also allow cooling fluids to be distributed through the fibrous medium of the assembly 100, which can absorb thermal energy from fluids in the passage 24.
The assembly 100 may include a delivery system for delivering liquid coolants to the fibrous medium of the assembly 100 including the substantially corrugated channels therein. In operation, liquid coolants can be distributed across the fibrous material in the assembly 100 by flowing through spaces between individual fibers of the material. In a particular embodiment, the liquid coolant can be water or another type of evaporative coolant. Fluids can flow through the essentially corrugated channels of the medium and transfer energy to the coolant, so that part of the distributed coolant evaporates. This transfer of energy from fluid to liquid coolants distributed throughout assembly 100 can lower the temperature of fluids in passageway 24. If necessary, undevaporated liquid coolants can be collected in a trough at the bottom of the arrangement 100 and diverted back to the supply system and / or to other components (e.g. by a pump, siphon, conduit, etc.).
An assembly 100 including a fibrous medium 102 therein may be positioned in a path through which a fluid 104 flows, e.g. a flow of air through passage 24 of power plant 10 (FIG. 1) such as a turbine. The assembly 100 may be attached, coupled, or otherwise attached to the structure of the passageway 24 by any known or later developed coupling mechanism. The fiber medium 102 may be composed of one or more currently known or later developed fiber materials and, as non-limiting examples, may include fiber-based membranes, polymeric films or lamellas, cellulosic materials, glass-based fibers, mineral fibers, composite materials, any of the herein disclosed substances and / or other materials, etc. In an exemplary embodiment, the fiber medium 102 may have a density between about forty kilograms per cubic meter (kg / m 3) and about four hundred fifty kg / m 3 with a fiber diameter between about five Micrometers (µm) and about fifty µm. Fiber media 102 may be selected, modified, manufactured, etc., to have a plurality of substantially corrugated channels 106 therein that can transmit the flow of fluid 104 through fiber media 102.
The arrangement 100 can also have a coolant supply system 108 in addition to the fiber medium 102. The coolant supply system 108 can convey liquid coolants that are pumped from a reservoir 109 to the fiber material 102 in order to absorb thermal energy from fluid 104. In an exemplary embodiment, the coolant supply system 108 of the arrangement 100 can also be located in the passage 24 of the power generation system 10 (FIG. 1).
With reference now briefly to FIG. 3, the coolant delivery system 108 and its components will now be illustrated in greater detail. The coolant delivery system 108 may include a manifold 110 in contact with fibrous medium 102. The manifold 110 may be in the form of any component now known or later developed for transferring fluids, including liquids, from another component, chamber, etc. to another. The distributor 110 is shown in FIGS. 2 and 3 by way of example in the form of a pad, but other configurations can also be provided. For example, the manifold 110 may be in the form of a chamber, multiple perforations, a perforated tube, a partially permeable material or group of materials, and so on. The manifold 110 may have an opening 112 that allows liquid coolant to flow through the manifold 110 to fiber medium 102. More specifically, the opening 112 can establish a fluid connection between fiber medium 102 and a coolant tube 114 coupled to the manifold 110.
A reservoir 109 can store a predetermined amount of liquid coolant that is to be distributed over the fiber medium 102 or diverted to other components. A pump 111 can deliver the liquid coolant in the reservoir 109 to the coolant pipe 114. 2, and discussing the present disclosure, includes coolant tube 114 as a particular example, but it should be understood that coolant tube 114 can, additionally or alternatively, be in the form of any currently known or later developed mechanical device for storing and / or transmitting Fluids can be present. While the opening 112 is visible to a human observer as shown in FIGS. 2 and 3, it should also be understood that one embodiment of the manifold 110 utilizes selectively permeable materials (e.g., filter materials and / or carbon-based substances) with multiple openings 112 may have therein that are invisible to a human observer. As non-limiting examples, coolant tube 114 can transfer liquid coolants such as: an antifreeze, water, an evaporative coolant, an antifreeze water solution, and / or other currently known or later developed materials with similar heat transfer properties. Coolants provided by a coolant supply system 108 can travel laterally through plates of fibrous medium 102 by flowing through gaps and / or portions of fibrous medium 102 that are permeable to liquids. Some coolants supplied to fiber medium 102 may include coolants for evaporative cooling. Evaporative cooling refers to a process that uses a coolant with a high heat of evaporation (e.g. water with a heat of evaporation of 40.68 kilojoules per mole) to cool a flowing fluid such as air. With evaporative cooling, a fluid can transfer energy to the coolant, so that the coolant evaporates, thereby lowering the temperature of the fluid.
A suction line 116 can transfer coolant pumped from the reservoir 109 with the pump 111 into the coolant pipe 114 of the coolant supply system 108. The suction line 116 is exemplified in the form of a single conduit, but any number of conduits are possible and the suction line 116 can also be in the form of other structures for transferring a coolant. Coolants that do not enter the fibrous medium 102 through the manifold 110 can be selectively flushed from the coolant supply system 108 through one or more flush lines 118 in fluid communication with the coolant tube 114. Purge lines 118 may be coupled to coolant tube 114 to regulate the flow of liquid coolants from coolant tube 114 into manifold 110 during operation. For example, while FIG. 2 shows two flush lines 118, any number of flush lines 118 can be used. Furthermore, flushing lines 118 may be in the form of a different structure or supply system for transferring coolants. In order to prevent liquid coolant from splashing out of the coolant pipe 114 and / or from spilling into other regions of the arrangement 100 as it passes through the manifold 100, a splash guard 120 can be coupled to the manifold 110. The splash guard 120 may be configured to receive the coolant tube 114 therein. The splash guard 120 may be made of a material such as glass, a metal, a plastic, and / or any other type of material that blocks the flow of fluids therethrough.
Referring to FIG. 2, the arrangement 100 can also include two or more acoustic shields 122 that are coupled to the fiber medium 102 and are located in the vicinity of the manifold 110. Acoustic shields 122 can suppress acoustic waves that otherwise bypass assembly 100 and travel from a noise generating component (e.g., a compressor 16 (FIG. 1) of power plant 10 (FIG. 1)) or other components and systems outside of power generation system 10. Acoustic shields 122 can have a shape and material composition that suppress acoustic waves and are sized e.g. decrease between about ten and about twenty decibels (dB). Acoustic shields 122 with solid surfaces can also suppress acoustic waves, e.g. by reflection, suppression, etc., without the acoustic waves reaching the coolant supply system 108 or components that are beyond the position of the arrangement 100. Some materials from which acoustic shields 122 may be constructed include, by way of non-limiting example, foam materials, plastics, acrylic fibers, combinations of these materials, and / or other acoustic cancellation materials either now known or later developed. Acoustic shields 122 can include a coolant tube and manifold 110 and can be devoid of passages therein. The solid surface structure of acoustic shields 122 may also reflect or block the flow of fluid 104.
The assembly 100 may also include a partition 124 for dividing fiber material 102 into multiple sections. The partition 124 may be made of any material that blocks the flow of fluid 104 and, in a particular configuration, may be made of the same material as the acoustic shields 122 or a different type of acoustic shielding material. Although FIGS. 2 and 3 show only a single coolant supply system 108 for purposes of illustration, it is to be understood that a single arrangement 100 can include a plurality of coolant supply systems 108 if necessary. Additionally or alternatively, the arrangement 100 can also have several distributors 110 and / or coolant tubes 114. Each manifold 110 and / or each coolant tube 114 can distribute liquid coolant to different sections of fiber medium 102 divided by partitions 124. In some cases, multiple coolant delivery systems 108 can provide coolant to the same assembly 100. In this case, sections of fiber medium 102 (e.g. divided by partitions 124) can be coupled to a corresponding coolant supply system 108 and / or, if necessary, a section of a larger coolant supply system 108. Several coolant supply systems can be used, e.g. for regulating the amount of liquid coolant supplied to different sections of fiber medium 102 to achieve different levels of cooling.
A drip pan 126 may be positioned below the fibrous medium 102 to collect liquid coolants, including undevaporated coolants, that can be reused for the assembly 100 and / or other components. The collecting trough 126 can be in fluid connection with the fiber medium 102 and can, in a particular embodiment, collect a predetermined amount of liquid coolant. While coolants are distributed through the fiber material 102 from the distributor 110, coolants can sink through the fiber medium 102 due to gravity. Undevaporated liquid coolants can settle in the coolant pan 126. In alternative embodiments, the drip pan 126 can e.g. a selectively activated vacuum to provide suction to collect liquid coolants from the fibrous medium 102. To couple the drip pan 126 to the coolant delivery system 108 and / or other components, the drip pan 126 may include tubing components such as drainage, pipes, pumps, etc. (not shown) coupled therewith to convey the coolant to other components, if necessary. In an exemplary embodiment, a pump and conduit can transfer coolant from the catch pan 126 to the suction line 116. In another exemplary embodiment, purge lines 118 may lead to drip pan 126 to mix unused coolant with unevaporated liquid coolants, which can then be routed back to coolant tube 114 or other location.
4 shows an embodiment of fiber medium 102 comprised of multiple plates 202. Each plate 202 may be comprised of one or more of the exemplary fibrous substances discussed herein to dampen acoustic waves traveling through substantially corrugated fiber medium 102. Substantially corrugated channels 106 can be positioned between two or more plates 202 and fluid 104 can flow through substantially corrugated channels 106. In an exemplary embodiment, a plurality of plates 202 can be stacked with essentially corrugated channels 106 as gaps between the various plates to form fibrous medium 102. Arranging multiple plates 202 in a stack to form fibrous media 102 enables a user and / or manufacturer of assembly 100 to add or remove plates of fibrous media 102 as needed to achieve the level of suppression and / or cooling provided in assembly 100 to change.
Substantially corrugated channels 106 between plates 202 of fibrous medium 102 are shown in greater detail in FIG. Each plate 202 of fibrous medium 102 may have a surface with a profiled shape (e.g., curved, sinusoidal, irregular, etc.). The surfaces of plates 202 may contact one another at specific locations to create substantially corrugated channels 106 between two contacting plates 202. Fluid 104 can flow into the substantially corrugated channel 106 (e.g., in the plane of FIG. 5) between plates 202 to pass through fibrous medium 102. The substantially corrugated shape of substantially corrugated channels 106 may produce multiple reflections of sound waves to increase the absorption of acoustic energy or otherwise block the transmission of acoustic waves (i.e., sound) through fiber medium 102 and assembly 100. In one embodiment, the substantially corrugated channel 106 can be devoid of complete "lines of sight" through which acoustic waves can pass. Plates 202 can be synthesized from other materials (e.g., by fiber fractionation or chemical processes) or made to have a surface with a certain curvature such that each substantially corrugated channel 106 has a predetermined amount of acoustic suppression (e.g., a certain acoustic transmission loss in decibels) for each plate 202. In a mathematical example discussed elsewhere herein, acoustic suppression properties of fiber medium 102 are discussed.
The curvature of substantially corrugated channels 106 may also reduce the resistance to fluid 104 flowing through the assembly 100 compared to conventional evaporative media. For example, the size and configuration of substantially corrugated channels 106 may have a minimal effect on fluid velocity and / or fluid flow through them, while creating multiple surfaces to reflect and thereby reduce the amplitude of acoustic waves. Increasing the curvature of panels 202 may increase the amount of acoustic attenuation, but that increase may come at the expense of increasing resistance to fluid 104 within substantially corrugated channels 106. The appropriate level of noise attenuation and / or frictional resistance to fluids 104 passing therethrough may be specific to a particular machine and / or application. However, embodiments of the present invention with substantially corrugated channels 106 may provide at least significant acoustic suppression regardless of material, shape, etc., as illustrated in a mathematical model of the assembly 100 herein.
6 shows a schematic view of a multi-shaft combined cycle power plant 300. The combined cycle power plant 300 can for example comprise a gas turbine system 500 with a gas turbine 580, which is operatively connected to a generator 570. The generator 570 and the gas turbine 580 can be mechanically coupled by a shaft 515 that can transfer energy between a drive shaft (not shown) of the gas turbine 580 and the generator 570. As FIG. 6 also shows, a heat exchanger 586 can be operatively coupled to the gas turbine 580 and a steam turbine system 590. The heat exchanger 586 can be fluidically connected via conventional conduits (numbering omitted) both to the gas turbine 580 and to a steam turbine 592 of the steam turbine system 590. The heat exchanger 586 may be a conventional heat recovery steam generator (HRSG) such as that used in conventional combined cycle power plants. As is known in the power generation art, HRSG 586 can use hot exhaust gases from gas turbine 580 in combination with a water supply to generate steam that is fed to steam turbine 592. The steam turbine 592 can optionally be coupled to another generator system 570 (via another shaft 515). It should be understood that generators 570 and shafts 515 can be of any size or type known in the art and vary depending on their application or the equipment to which they are associated. The common numbering of the generators and shafts is only intended for clarity and does not necessarily suggest that these generators or shafts are identical. Each generator set 570 and each shaft 515 may operate on substantially similar principles and / or may have substantially the same behavior. One or more plants and / or elements of a combined cycle power plant 300 can be designed to have an arrangement 100 for suppressing acoustic waves and / or for cooling fluids therein. In one embodiment of the present invention (shown in phantom) a gas turbine system 500 and / or a steam turbine system 590 can be provided with an arrangement 100, e.g. in passage 24, can be retrofitted. In another embodiment shown in FIG. 7, a single-shaft combined cycle power plant 600 can have a single generator 570 that is coupled to both the gas turbine 580 and the steam turbine 592 via a single shaft 515. The single shaft combined cycle power plant 600 and / or elements therein can be retrofitted so that an embodiment of the arrangement 100, e.g. in passage 24.
As discussed herein, embodiments of the assembly 100 can provide cooling and acoustic suppression for the power plant 10 (FIG. 1), the combined cycle power plant 300 (FIGS. 6, 7), and / or other machines or components that require soundproofing and cooling are desired. The acoustic cancellation features of the assembly 100 will be discussed in more detail with reference to a mathematical example.
The performance of the arrangement 100 with fiber medium 102 according to embodiments of the present disclosure can be checked with mathematical models. The ability of a particular material to suppress acoustic waves can be expressed in terms of "specific flow resistance" (R1), which can depend in part on the diameter of fibers in a fiber material in addition to the density of the material. In the following example it is assumed that the fiber medium 102 has a fiber diameter of about fifteen µm and a bulk density of about two hundred kg / m 3. The specific flow resistance of a material to acoustic waves can be defined by one of the following formulas:
where «D» represents the fiber diameter of the fiber medium 102 in micrometers, bulk represents the bulk density of the fiber medium 102 in kg / m <3>, «SpGr» is an abbreviation for the unitless specific gravity of a certain material and R1 the specific flow resistance in MKS Rayls pro Meter ("MKS Rayl / m"). In the example discussed herein, the specific flow resistance of fiber medium 102 is determined to be 50,840 MKS Rayl / m.
Other mathematical descriptors of an effect of a material on an acoustic wave depend in part on the frequency of the transmitted sound. In the present example, two acoustic suppression characteristics, the "propagation constant" of acoustic waves through fiber medium 102 and the "acoustic impedance" of fiber medium 102, illustrate the amount of wave propagation and acoustic suppression that fiber medium 102 provides for a given wave. These readings can be derived from the calculated specific flow resistance discussed above and from the frequency of a propagated acoustic wave. The propagation constant measures the amplitude of an acoustic wave as the wave propagates through a particular material. Acoustic impedance generally measures the suppression response of fiber medium 102 to sound waves therein at a certain frequency and can be expressed as MKS Rayls per square meter ("MKS Rayl / m <2>"). These constants contain a quantity and a frequency and can be expressed for a group of «n» materials by equations in the complex domain:
where «E» (also known as sound energy density) is defined as ((f) (ρ0) / R1), «f» represents the sound frequency in Hertz («Hz») (1 / second), «j» an imaginary number ( ie represents the square root of -1), «k0» is defined as (ω / c0), «ω» represents the angular sound frequency in radians per second (rad / sec) and «ρ0» and «c0» the density and the Represent the speed of sound in air. The remaining constants α ́, α ́ ́, β ́ and β ́ ́ are predetermined regression coefficients and can be determined for illustrative known materials with reference to the following tables:
For the fiber medium 102, the propagation constant and acoustic impedance can alternatively be calculated using the following equations using several of the same variables, but without relying on regression coefficients:
where «R1» represents the calculated specific flow resistance of fiber medium 102, «ρ0» represents the density of air, «f» represents the sound frequency in Hertz and «j» represents an imaginary number. Applying the frequency of a sound wave and the properties of a material (e.g. fiber diameter and density) to these equations gives the propagation constant and acoustic impedance for the modeled acoustic wave. By referring to the properties of the fiber medium 102 discussed above and the frequency of a particular sound wave, the propagation constant and acoustic impedance of the fiber medium 102 are mathematically defined. As discussed herein, these quantities can be used to derive the transmission loss of an acoustic wave through fiber medium 102.
The pressure field of acoustic waves in fiber medium 102 can be used with the propagation constant and acoustic impedance of fiber medium 102 to determine a total transmission loss of acoustic waves through fiber material 102. Acoustic pressure «ρ» is dependent on the position and transit time of a wave through fiber medium 102, measured in Pascal (Pa) or Newton per square meter (N / m <2>), and generally describes the strength of the acoustic wave at a specific position and at some point.
8, these equations can be applied to fiber material 102 of the two-sided arrangement 100 in order to determine the amount of acoustic suppression in fiber material 102 relative to external substances. Acoustic waves can enter fiber material 102 from one direction and can propagate further through fiber material 102 essentially along that direction. Some acoustic waves may propagate through fibrous material 102 and exit on an opposite side, while others may be reflected from the opposite side of fibrous material 102 where acoustic waves would exit. Where the speed of the acoustic wave is defined as the acoustic pressure field across the characteristic impedance of the medium through which an acoustic wave passes, the total acoustic resistance "R" of fiber medium 102 can be defined as:
where “ZC” represents the characteristic impedance of fiber medium 102 where derived elsewhere herein and “Z0” represents the characteristic impedance of the medium outside of fiber medium 102, which in embodiments of the present disclosure may be air. As also discussed herein, the characteristic impedance of the fiber medium 102 and the external material is dependent on the frequency of the traveling acoustic waves. Converting the characteristic impedance of fiber medium 102 and the adjacent medium (e.g., the passage in Figure 8) to a complex form (i.e., ZC = Z0 (a-jb)) by the relationships discussed above yields the following relationship:
where «a» represents the size of a real component and «b» the size of an imaginary component. The generalized expression of "R" in complex form is provided by adding the real and imaginary parts of ZC and Z0 in the numerator and subtracting the real and imaginary parts of Z0 from ZC in the denominator. As discussed elsewhere herein, the resulting acoustic resistance R measures the total acoustic resistance of the fibrous medium 102 in complex form relative to the external material (e.g., air) to acoustic waves traveling through it. The acoustic resistance R may be combined with the resistance of fiber medium 102 to reflected waves as discussed herein to determine the transmission loss of fiber medium 102.
For acoustic waves that are reflected from the exit interface between fiber medium 102 and external medium (e.g. passage in Fig. 8), the total acoustic resistance for reflected acoustic waves (R ') can also be expressed in complex form (where «a »Is the size of a real component and« b »is the size of an imaginary component) as:
which is the same as the resistance of unreflected acoustic waves, but with a phase difference of 180 °. This phase difference between the two terms is a result of the acoustic waves being reflected before traveling through fiber medium 102 against an acoustic resistance of R '.
The total acoustic resistance of the fiber medium 102 can mathematically indicate the sound pressure of acoustic waves entering and exiting the fiber material 102. Based on this relationship between acoustic waves propagating through fiber medium 102 and reflected acoustic waves, the magnitude of the acoustic pressure (e.g. the magnitude of acoustic pressure for waves entering the fiber medium 102 (P1) increases over the magnitude of acoustic pressure for waves in air before the fiber medium 102 (P0) is reached, can be expressed as «absorption coefficient» α:
As shown in Fig. 8, P3 represents the acoustic pressure of waves after exiting the fiber medium 102 and P2 represents the acoustic pressure of waves reaching the opposite side of the fiber medium 102. With the help of the absorption coefficient, the total transmission loss achieved by the fiber medium 102 can be mathematically derived with the help of the propagation constant, derived elsewhere herein, where the subscript "re" denotes a real component of a variable and the subscript "im" denotes an imaginary component of the propagation constant (which in turn is dependent on the frequency of an acoustic wave as discussed herein). The variable «d» denotes the fiber diameter of fiber medium 102 and «α» represents the absorption coefficient defined here:
where "TL" represents the transmission loss of an acoustic wave through fiber medium 102 in decibels. While the models for transmission loss discussed herein do not include variables representing multiple reflections of an acoustic wave in fiber medium 102, the effect of these variables on the resulting transmission loss through fiber medium 102 can be negligible.
In the present example, the fiber medium 102 can have a depth of approximately 46 centimeters (cm) and for analysis purposes it can be assumed that it has an “effective depth” (ie a distance over which acoustic waves are suppressed) of approximately 3 .0 centimeters. For frequencies between about zero kHz and about eight kHz, the transmission loss is shown in the curve of FIG. 9 to be between about ten decibels (dB) and about eighteen dB. Configurations of the assembly 100 in the passageway 24 can provide acoustic suppression to the extent indicated by the mathematical examples discussed herein. For example, two-sided fiber medium 102 can resist the flow of acoustic waves through it, and some of the acoustic waves can be reflected before they exit the fiber medium 102. However, fluids in passageway 24 can pass through substantially corrugated channels 106 without experiencing increased drag force, despite the fact that the shape of the substantially corrugated channel 106 is designed to suppress acoustic waves. In general, each passage 24 between a mechanical plant and / or a mechanical component, such as the power generation plant 10 (FIG. 1), the combined cycle power plant 300 (FIGS. 6, 7), an embodiment of the arrangement 100 with a fiber medium 102 therein to suppress acoustic waves and cool fluids passing through a particular passage. Additionally, acoustic shields (e.g., acoustic shields 124 (Figs. 2, 3)) can be added to provide additional blocking of acoustic waves where flow of fluids 104 through assembly 100 is not desired. All of these acoustic cancellation features can be associated with the cooling provided by the assembly 100 as discussed herein. Thus, technical effects of the arrangement 100 can include a single component that dampens acoustic waves from a power generation plant and thereby cools fluids that are produced by the same power generation plant.
The apparatus and method of the present disclosure are not limited to any particular gas turbine, steam turbine, power generation plant, or other plant, and may be used with other power generation plants and / or plants (e.g., combined cycle, single cycle, nuclear reactor, etc.). Additionally, the apparatus of the present invention can be used with other systems not described herein that can benefit from the increased operating range, efficiency, durability, and reliability of the apparatus described herein.
[0054] The terminology used herein is intended to describe specific embodiments only and is not intended to limit the disclosure. As used herein, the singular forms such as "an" and "der / die / das" are intended to include the plural forms as well, unless the context clearly indicates otherwise. It is also to be understood that the term “comprises” and / or “comprising” when used in this specification indicates the presence of specified features, integers, steps, operations, elements and / or components, but the presence or do not exclude the addition of one or more other features, whole numbers, steps, operations, elements, components and / or groups thereof.
This written description uses examples to disclose the invention, including the best mode, and to enable any person skilled in the art to practice the invention, including making and using devices or systems, or performing integrated processes. The patentable scope of the invention is defined by the claims, and may include other examples that will 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 language of the claims.
Embodiments of the present invention provide an assembly 100 having a fibrous medium 102 having a plurality of substantially corrugated channels 106 therein, the plurality of substantially corrugated channels 106 permeable to flow of fluid 104 therethrough; a manifold 110 in contact with the fibrous medium 102 and having an opening 112 therein for the passage of liquid coolant through the manifold 110; and at least two acoustic shields 122 coupled to fiber media 102 and located on opposite sides of manifold 110.
PARTS LIST
10 power generation plant 12 combustion chamber 14 fuel nozzle 16 compressor 18 turbine 20 rotatable shaft 22 air 24 passage 100 arrangement 102 fiber medium 104 fluid 106 corrugated channels 108 coolant supply system 109 reservoir 110 manifold 111 pump 112 opening 114 coolant pipe 116 suction line 118 flushing lines 120 splash guard 122 acoustic shields 126 Drip pan 202 Plates 300 Combined cycle power plant 500 Gas turbine system 515 Shaft 570 Generator 580 Gas turbine 586 Heat exchanger 592 Steam turbine

权利要求:
Claims (10)
[1]
1. Arrangement (100), comprising:a fibrous medium (102) having a plurality of substantially corrugated channels (106) therein, the plurality of substantially corrugated channels (106) being permeable to a passing stream of fluid (104);a manifold (110) in contact with the fibrous medium (102) and having an opening (112) therein for passing a liquid coolant through the manifold (110); andat least two acoustic shields (122) coupled to the fiber medium (102) and located on opposite sides of the manifold (110).
[2]
The assembly (100) of claim 1, further comprising a coolant sump (126) in fluid communication (104) with the fibrous medium (102).
[3]
The assembly (100) of claim 1 or 2, further comprising a coolant tube (114) coupled to the manifold (110) and having a purge valve (118) therein, the purge valve (118) receiving a flow of liquid coolant from the assembly (100) selectively prevents and permits.
[4]
4. Arrangement (100) according to one of the preceding claims, which also has a with the manifold (110) coupled splash guard (120).
[5]
The assembly (100) of any one of the preceding claims, wherein the fibrous medium (102) has a density between about 40 kilograms per cubic meter (kg / m 3) and about 450 kg / m 3.
[6]
6. Arrangement (100) according to one of the preceding claims, whereina curvature from one of the plurality of substantially corrugated channels (106) attenuates transmission of sound therethrough.
[7]
7. Arrangement (100) according to one of the preceding claims, wherein the fiber medium (102) comprises a plurality of arranged to a stack of fiberboard (202).
[8]
8. Turbine component, comprising:a passage (24) adapted to pass an airflow from a compressor (16);a fibrous medium (102) positioned in the passage (24), the fibrous medium (102) having a plurality of substantially corrugated channels (106) therein, each of the plurality of substantially corrugated channels (106) being permeable to the flow of air ;a manifold (110) in contact with the fibrous medium (102) and having an opening (112) therein for passing a liquid coolant through the manifold (110); andat least two acoustic shields (122) coupled to the fiber medium (102) and located on opposite sides of the manifold (110).
[9]
A turbine component according to claim 8, wherein the flow of compressed air through the fibrous medium (102) contacts and evaporates a portion of the liquid coolant in the fibrous medium (102).
[10]
10. Gas and steam combined cycle power plant, comprising:an assembly (100) positioned in a fluid flow section (104) of one of a gas turbine, a heat recovery steam generator (HRSG), and a steam turbine, the assembly (100) comprising:a fibrous medium (102) having a plurality of substantially corrugated channels (106) therein, the substantially corrugated channels (106) being permeable to a passing stream of fluid (104),a manifold (110) in contact with the fibrous medium (102) and having an opening (112) therein for passing a liquid coolant through the manifold (110); andat least two acoustic shields (122) coupled to the fiber medium (102) and located on opposite sides of the manifold (110).

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同族专利:

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公开号 | 公开日

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US9359914B2|2016-06-07|

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US20160053637A1|2016-02-25|

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DE102015113008A1|2016-02-25|

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JP6599168B2|2019-10-30|

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JP2016044676A|2016-04-04|

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法律状态:
2017-03-15| NV| New agent|Representative=s name: GENERAL ELECTRIC TECHNOLOGY GMBH GLOBAL PATENT, CH |

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2019-05-31| AZW| Rejection (application)|

优先权:

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申请号 | 申请日 | 专利标题

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US14/462,845|US9359914B2|2014-08-19|2014-08-19|Silencing and cooling assembly with fibrous medium|

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