US20050194207A1 - Apparatus and method of sound attenuation in a system employing a VSD and a quarter-wave resonator - Google Patents
Apparatus and method of sound attenuation in a system employing a VSD and a quarter-wave resonator Download PDFInfo
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- US20050194207A1 US20050194207A1 US10/793,130 US79313004A US2005194207A1 US 20050194207 A1 US20050194207 A1 US 20050194207A1 US 79313004 A US79313004 A US 79313004A US 2005194207 A1 US2005194207 A1 US 2005194207A1
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- 239000012530 fluid Substances 0.000 claims abstract description 175
- 238000004891 communication Methods 0.000 claims abstract description 10
- 230000003247 decreasing effect Effects 0.000 claims description 9
- 238000006073 displacement reaction Methods 0.000 claims description 7
- 230000004044 response Effects 0.000 claims description 4
- QAMFBRUWYYMMGJ-UHFFFAOYSA-N hexafluoroacetylacetone Chemical compound FC(F)(F)C(=O)CC(=O)C(F)(F)F QAMFBRUWYYMMGJ-UHFFFAOYSA-N 0.000 claims 2
- 239000003507 refrigerant Substances 0.000 description 28
- 239000007789 gas Substances 0.000 description 27
- 230000000694 effects Effects 0.000 description 4
- 230000008901 benefit Effects 0.000 description 3
- 230000008859 change Effects 0.000 description 2
- 230000006835 compression Effects 0.000 description 2
- 238000007906 compression Methods 0.000 description 2
- 238000005057 refrigeration Methods 0.000 description 2
- 230000009471 action Effects 0.000 description 1
- 238000004378 air conditioning Methods 0.000 description 1
- 230000002238 attenuated effect Effects 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 230000006870 function Effects 0.000 description 1
- 238000010438 heat treatment Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000010349 pulsation Effects 0.000 description 1
- 238000005086 pumping Methods 0.000 description 1
- 239000012858 resilient material Substances 0.000 description 1
- 238000009423 ventilation Methods 0.000 description 1
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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
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M35/00—Combustion-air cleaners, air intakes, intake silencers, or induction systems specially adapted for, or arranged on, internal-combustion engines
- F02M35/12—Intake silencers ; Sound modulation, transmission or amplification
- F02M35/1205—Flow throttling or guiding
- F02M35/1222—Flow throttling or guiding by using adjustable or movable elements, e.g. valves, membranes, bellows, expanding or shrinking elements
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M35/00—Combustion-air cleaners, air intakes, intake silencers, or induction systems specially adapted for, or arranged on, internal-combustion engines
- F02M35/12—Intake silencers ; Sound modulation, transmission or amplification
- F02M35/1255—Intake silencers ; Sound modulation, transmission or amplification using resonance
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B49/00—Arrangement or mounting of control or safety devices
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
- F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2500/00—Problems to be solved
- F25B2500/12—Sound
Definitions
- the present invention relates generally to a method of operation and apparatus for noise attenuation of closed fluid systems, and more particularly, to a method of operation and apparatus for adjustable noise attenuation of closed HVAC&R systems having positive displacement compressors with variable speed drives.
- Heating, ventilation, air conditioning or refrigeration (HVAC&R) systems typically maintain temperature control in a structure by circulating a fluid within coiled tubes such that passing another fluid over the tubes effects a transfer of thermal energy between the two fluids.
- a primary component in such a system is a positive displacement compressor, which receives a cool, low pressure gas and by virtue of a compression device, exhausts a hot, high pressure gas.
- One type of positive displacement compressor is a screw compressor, which generally includes two cylindrical rotors mounted on separate shafts inside a hollow, double-barreled casing. The side-walls of the compressor casing typically form two parallel, overlapping cylinders which house the rotors side-by-side.
- Screw compressor rotors typically have helically extending lobes and grooves on their outer surfaces forming a large thread on the circumference of the rotor.
- the threads of the rotors mesh together, with the lobes on one rotor meshing with the corresponding grooves on the other rotor to form a series of gaps between the rotors.
- These gaps form a continuous compression chamber that continuously reduces in volume as the rotors turn to compress the gas and which communicates with the compressor inlet opening, or “port,” at one end of the casing and with a discharge port at the opposite end of the casing.
- each rotor rotates at high rates of speed, and multiple sets of rotors (compressors) may be configured to work together to further increase the amount of gas that can be circulated in the system, thereby increasing the operating capacity of a system. While the rotors provide a continuous pumping action, each set of rotors (compressor) produces pressure pulses as the pressurized fluid is discharged at the discharge port. These discharge pressure pulsations act as significant sources of audible sound within the system. In addition, mechanical noise is generated by the meshing and unmeshing of the rotors which is the result of backlash and movement between the rotors.
- Noise attenuation devices include reflective and absorptive mufflers. Absorptive mufflers are most effective when the frequencies of the sound are greater than 500 Hz. Since the fundament frequencies for a positive displacement compressor, such as a screw compressor, are typically less than 500 Hz, absorptive mufflers are less effective than other types of mufflers.
- the pressure pulse frequency of screw compressors are predictable, that is, the pressure pulse frequency is a function of the number of lobes of the male rotor multiplied by its rotational speed.
- a screw compressor having a 5 lobed male rotor, which rotates at 3,600 RPM generates a frequency of 5 ⁇ 3, 600/60 or 300 Hz. Therefore, for a compressor, such as a screw compressor, operating at a fixed speed, a reflective muffler, such as a side branch resonator, which is also referred to as a quarter wave resonator, may be configured to attenuate noise at a specific frequency.
- the side branch resonator typically comprises a component that forms a tee “T” adjacent a compressor discharge, with the tee being closed at the end opposite the compressor discharge.
- the length of the side branch resonator is configured or “tuned” to be one-fourth of one wavelength of the sound produced by the compressor to achieve the desired noise attenuation.
- acoustic velocity is defined as the velocity that sound travels through the refrigerant gas for a given set of ambient conditions.
- the present invention relates to a resonator arrangement for a closed fluid system including a body having a passageway in fluid communication with a closed fluid system.
- a piston is movable within the passageway wherein a position of the piston within the passageway defines a noise attenuation frequency for the closed fluid system.
- a control arrangement selectively positions the piston within the passageway to generate a noise attenuation frequency corresponding to a noise frequency generated by the closed fluid system.
- the present invention further relates to a variable noise attenuation device for use with an HVAC&R fluid system
- a variable noise attenuation device for use with an HVAC&R fluid system
- a body having a passageway in fluid communication with an HVAC&R fluid system.
- a piston is movable within the passageway wherein a position of the piston within the passageway defines a noise attenuation frequency for the HVAC&R fluid system.
- a proportional valve selectively provides a pressurized fluid from the HVAC&R fluid system to the piston to selectively position the piston within the passageway to generate a noise attenuation frequency corresponding to a noise frequency generated by the HVAC&R fluid system.
- the present invention yet further relates to a method for attenuating noise in a closed fluid system having the steps of providing a body having a passageway in fluid communication with a closed fluid system; providing a piston movable within the passageway wherein a position of the piston within the passageway defines a noise attenuation frequency for the closed fluid system; providing a control arrangement for providing a pressurized fluid to the piston; and positioning selectively the piston within the passageway to generate a noise attenuation frequency corresponding to a noise frequency generated by the closed fluid system.
- An advantage of the present invention is that it attenuates noise of variable frequency.
- a further advantage of the present invention is that it is inexpensive to manufacture.
- FIG. 1 is a schematic of a variable speed HVAC&R system having a variable frequency resonator of the present invention.
- FIG. 2 is an enlarged partial schematic of the HVAC&R system including an enlarged elevation view of the variable frequency resonator of the present invention.
- FIG. 3 is an enlarged partial schematic of the HVAC&R system including an enlarged elevation view of an embodiment of the variable frequency resonator of the present invention.
- FIG. 1 illustrates generally a HVAC&R system 10 incorporating the present invention.
- An AC power source 12 supplies AC power to a variable speed drive (VSD) 14 , which in turn, supplies AC power to a motor 18 for driving a compressor 20 .
- VSD variable speed drive
- a control panel 16 controls both the output frequency and the voltage from VSD 14 that is supplied to motor 18 , which selectively varies both the torque and speed of motor 18 , and likewise varies the speed of compressor 20 .
- Control panel 16 includes an analog to digital (A/D) converter, a microprocessor, a non-volatile memory, and an interface board to control operation of the refrigeration system 10 .
- the control panel 16 can also be used to control the operation of the VSD 14 , the monitor 18 and the compressor 20 .
- Compressor 20 receives refrigerant gas at its inlet and discharges compressed refrigerant gas from its outlet through discharge line 30 .
- other compressors may operate in parallel with compressor 20 to increase the capacity of the system 10 .
- These compressors are typically positive displacement compressors, such as screw, reciprocating or scroll, having a wide range of cooling capacity, but may also include other compressor constructions.
- variable resonator 26 such as a quarter wave resonator.
- Variable resonator 26 is continuously tuned, as will be described in further detail below, to attenuate both the pressure pulses and the mechanical noise generated by the meshing and unmeshing of the rotors that is the result of backlash and movement between the rotors.
- the variable resonator 26 can attenuate both the pressure pulses and the mechanical rotor noise, since each occurs at substantially the same frequency.
- the conventional HVAC&R system 10 includes many other features that are not shown in FIG. 1 . These features have been purposely omitted to simplify the drawing for ease of illustration.
- variable resonator 26 includes a body 38 , such as a tube or cylinder, which defines a passageway 39 .
- a stop 48 having an aperture 49 is secured to one end of body 38
- a cap 40 is secured to the opposite end of body 38 .
- the end of body 38 having the stop 48 is connected to discharge line 30 so that passageway 39 of body 38 is in fluid communication with the refrigerant gas flowing through discharge line 30 .
- a piston 42 is inserted inside of passageway 39 that is slidable or movable within passageway 39 , the piston 42 further includes a seal 44 , such as an O-ring, to provide a substantially fluid tight seal between piston 42 and an inside surface 41 of body 38 as piston 42 slides along passageway 39 .
- a resilient device 46 such as a spring, is interposed between piston 42 and cap 40 to urge piston 42 into movement along passageway 39 in a direction away from cap 40 , the travel of the piston 42 in this direction being limited by stop 48 .
- stop 48 the travel of the piston 42 along passageway 39 is limited by the stop 48 , in one direction, and by the cap 40 , minus the thickness of the compressed resilient device 46 , in the other direction.
- variable resonator length 50 is defined by the distance between the lower surface of piston 42 and the lower surface of stop 48 .
- variable resonator length 50 preferably corresponds to one quarter of a wavelength, such as the wavelengths generated during the operation of the compressor 20 , which can be attenuated by the resonator 26 . While the single position of a fixed length resonator may effectively attenuate noise of a specific wavelength corresponding to a compressor operating at a fixed speed and a specific set of ambient conditions, such unchanging operating conditions are unrealistic.
- changing ambient conditions such as temperature
- changes the density of the refrigerant which changes the sonic speed C of the refrigerant, which changes the resonator length required to attenuate the noise generated by the compressor as discussed in equation [1].
- a fixed length resonator cannot accommodate these changing conditions.
- the compressor of the present invention operates at variable speeds, which, in turn, results in variable frequencies.
- selective control of the position of the piston 42 within the passageway 39 of the resonator 26 is required for consistent, noise attenuation.
- a valve 28 such as a proportional valve, is controlled by the control panel 16 to selectively provide pressurized refrigerant gas from a pressure line 36 through cap 40 .
- the control panel 16 actuates the valve 28 to bleed pressurized refrigerant gas from a high pressure line 34 , which is in fluid communication with the compressor discharge 30 , to provide to the pressure line 36 .
- the control panel 16 actuates the valve 28 to bleed pressurized refrigerant gas from the pressure line 36 to provide to the low pressure line 32 , which may be connected to a port in the compressor 20 , or to the suction line at the inlet of the compressor 20 .
- the low pressure line 32 may be connected to a separate container (not shown) that is maintained at an even lower pressure than the suction line at the compressor inlet to provide an even wider range of pressure differential, if desired.
- the amount of pressure in the pressure line 36 can range anywhere from the discharge pressure of the high pressure line 34 to the lower pressure contained in the low pressure line 32 to effect movement of the piston 42 along the passageway 39 of the resonator body 38 .
- the net force that is applied to the surface of the piston 42 , which is facing the cap 40 must be sufficiently different from the net force that is applied to the opposite surface of the piston 42 which faces the aperture 49 . There must be a sufficient difference in forces acting on the opposed surfaces of the piston 42 to overcome any combination of frictional forces between the seal 44 and the inside surface of body 38 , the weight of the piston 42 (if the piston moves vertically) and inertia of the piston 42 .
- the net force that is applied to the surface of the piston 42 facing the cap 40 is applied in two parts.
- the first part of the net force is the pressure of the refrigerant gas in the pressure line 36 (P LINE ) multiplied by the surface area of the piston 42 (A SURFACE ) facing the cap 40 .
- the second part of the net force is the force applied by the resilient device 46 , which is the product of the spring constant (k) of the spring multiplied by the distance (d) the spring is compressed.
- the net force that is applied to the surface of the piston 42 facing the stop 48 is applied in a single part.
- This single net force part is the pressure of the refrigerant gas in the discharge line 36 (P DISCHARGE ) multiplied by the surface area of the piston 42 (A SURFACE ) facing the stop 48 .
- the P DISCHARGE may or may not vary.
- P DISCHARGE may or may not vary.
- the P DISCHARGE may fluctuates, the fluctuation being either variable or substantially constant, depending upon the operating conditions.
- the magnitude of P DISCHARGE will vary no more than about one percent of the variable resonator length 50 .
- the effect of P DISCHARGE fluctuation can typically be disregarded, while it is the sonic speed of the refrigerant that must be monitored.
- the piston 42 when there is a sufficient difference between the F CAP and the F STOP forces, the piston 42 is urged to move along the passageway 39 in a direction away from the larger force. In other words, the piston 42 will continue to move in this direction until the forces are substantially equal, or the piston 42 has reached the end of its possible travel, that is, abutting the stop 48 or abutting the cap 40 , minus the thickness of the compressed resilient device 46 .
- the variable resonator length 50 is at its shortest length and corresponds to the shortest one-quarter wavelength position, and therefore, the shortest wavelength, or highest frequency, that the resonator 26 can attenuate.
- variable resonator length 50 is at its maximum length, and corresponds to the longest one-quarter wavelength position, and therefore, the longest wavelength, or lowest frequency, that the resonator 26 can attenuate. It is appreciated by those skilled in the art that there exists a reciprocal relationship between frequency and wavelength.
- the position of the piston 42 is controlled by the control panel 16 using a control algorithm. Based upon application of equations [1]-[3], the control algorithm determines the desired resonator length 50 , that is, the desired position of the piston 42 within the passageway 39 , by reading the VSD frequency output that is supplied to the compressor motor 18 , and comparing the desired position of the piston 42 to the position of the piston 42 in the passageway 39 .
- the control algorithm may employ a look-up table that accounts for changes in ambient conditions, such as temperature and pressure, which likewise can change the acoustic velocity of the gas, and the desired position of the piston 42 within the passageway 39 .
- control algorithm may further employ the look-up table or calculate the relationship between the spring length (d in equation [2]) and the piston 42 position without needing to measure the piston 42 position.
- the position of the piston 42 in the passageway 39 may be determined by a sensor, a rheostat, or any other suitable mechanical or electrical device that provides such positional information to the control panel 16 .
- the control panel 16 sends a control signal(s) to the valve 28 .
- the control signal from the control panel 16 causes the valve 28 to actuate to bleed pressurized refrigerant from the high pressure line 34 to the pressure line 36 , thereby increasing the pressure in the pressure line 36 .
- the combined forces, generated from the pressure in the pressure line 36 and the compressed resilient device 46 are applied to the piston 42 , which collectively define force F CAP as previously discussed in equation [2].
- the opposing force that is applied to the piston 42 defines force F STOP as previously discussed in equation [3].
- the control signal from the control panel 16 causes the valve 28 to actuate to bleed pressurized refrigerant from the pressure line 36 to the low pressure line 32 , thereby decreasing the pressure in the pressure line 36 .
- the combined forces generated from the pressure in the adjustable pressure line 36 and the compressed resilient device 46 are applied to the piston 42 , which collectively define force F CAP as previously discussed in equation [2].
- the opposing force that is applied to the piston 42 defines force F STOP as previously discussed in equation [3].
- F STOP force sufficiently exceeds the F CAP force, the piston 42 slides toward the cap 40 , thereby increasing the variable resonator length 50 .
- valve 28 controlling the position of the piston 42 by selectively providing pressurized refrigerant gas between lines 32 , 34 and 36 using the refrigerant gas from the HVAC&R system 10
- pressurized refrigerant from a source that is independent from the HVAC&R system 10 may also be used.
- other pressurized fluids each from independent sources of pressurized fluid such as air or other compressible gas, or even incompressible fluids may also be used with the valve 28 to selectively move the piston 42 along the passageway 39 .
- the use of such gases or fluids if incompatible with the efficient operations HVAC&R system 10 , may need to remain separate from the refrigerant in the HVAC&R system 10 .
- piston 42 may also be magnetically or electrically displaced within the passageway 39 .
- pressurized fluids are selectively provided to or bled from the pressure line 36 of a resonator 126 by the valve 28 from an independent pressurized fluid source 154 and an independent fluid receptacle 152 .
- the fluid receptacle 152 receives pressurized fluid that is bled from the pressure line 36 when the control panel 16 determines that the variable resonator length 50 needs to be increased to likewise urge the piston 42 to move along the passageway 39 of the resonator body 38 toward the cap 40 .
- the pressurized fluid source 154 provides pressurized fluid to the pressure line 36 when the control panel 16 determines that the variable resonator length 50 needs to be decreased to likewise urge the piston 42 to move along the passageway 39 of the resonator body 38 toward the stop 48 .
- the pressurized fluid source 154 is pressurized to a higher level than the receptacle 152 , and may be pressurized to a much higher pressure than the discharge pressure from the discharge line 30 , if desired.
- By providing highly pressurized fluid in pressurized fluid source 154 it may be possible to eliminate the need for the resilient device spring 46 , and decrease the response time for movement of the piston 42 along the passageway 39 of the resonator body 38 .
- a second valve 129 that is also controlled by the control panel 16 is provided to selectively provide pressurized fluid from a high pressure line 158 to a variable pressure line 156 .
- pressurized fluid may be bled to the receptacle 152 through a low pressure line 160 .
- the pressurized fluid from the second valve 129 is received in an expandable/contractable toroidal container 162 .
- the container 162 is disposed between the stop 48 and the piston 42 and is composed of a resilient material that permits the container 162 to expand or contract in response to sufficient differences between forces F CAP and F STOP which result in movement of the piston 42 with respect to the container 162 .
- the container 162 remains adjacent to the inside the surface 41 of the resonator body 38 and collapses upon itself as the container 162 is maintained in contact with the piston 42 as it moves along the passageway 39 , possibly by use of baffles.
- a resilient device (not shown) may be provided inside the container 162 .
- the container 162 preferably provides a uniform cross sectional profile within the passageway 39 to further provide predictable noise attenuation behavior as the resonator length 50 is varied as previously described.
- pressurized fluids from pressurized sources or receptacles may be used with the pressurized refrigerant gas from the HVAC&R system, and that these pressurized fluids may or may not need to be separated from each other. It is also appreciated that any number of valves may be used to control the flow of the pressurized fluids as discussed.
Abstract
A resonator in a closed fluid system includes a body having a passageway in communication with a closed fluid system wherein a piston is movable within the passageway. Each position of the piston within the passageway defines a noise attenuation frequency corresponding to a noise frequency generated by the closed fluid system. A device providing a pressurized fluid from the closed fluid system selectively moves the piston within the passageway to vary the noise attenuation frequency.
Description
- The present invention relates generally to a method of operation and apparatus for noise attenuation of closed fluid systems, and more particularly, to a method of operation and apparatus for adjustable noise attenuation of closed HVAC&R systems having positive displacement compressors with variable speed drives.
- Heating, ventilation, air conditioning or refrigeration (HVAC&R) systems typically maintain temperature control in a structure by circulating a fluid within coiled tubes such that passing another fluid over the tubes effects a transfer of thermal energy between the two fluids. A primary component in such a system is a positive displacement compressor, which receives a cool, low pressure gas and by virtue of a compression device, exhausts a hot, high pressure gas. One type of positive displacement compressor is a screw compressor, which generally includes two cylindrical rotors mounted on separate shafts inside a hollow, double-barreled casing. The side-walls of the compressor casing typically form two parallel, overlapping cylinders which house the rotors side-by-side. Screw compressor rotors typically have helically extending lobes and grooves on their outer surfaces forming a large thread on the circumference of the rotor. During operation, the threads of the rotors mesh together, with the lobes on one rotor meshing with the corresponding grooves on the other rotor to form a series of gaps between the rotors. These gaps form a continuous compression chamber that continuously reduces in volume as the rotors turn to compress the gas and which communicates with the compressor inlet opening, or “port,” at one end of the casing and with a discharge port at the opposite end of the casing.
- These rotors rotate at high rates of speed, and multiple sets of rotors (compressors) may be configured to work together to further increase the amount of gas that can be circulated in the system, thereby increasing the operating capacity of a system. While the rotors provide a continuous pumping action, each set of rotors (compressor) produces pressure pulses as the pressurized fluid is discharged at the discharge port. These discharge pressure pulsations act as significant sources of audible sound within the system. In addition, mechanical noise is generated by the meshing and unmeshing of the rotors which is the result of backlash and movement between the rotors.
- To eliminate or minimize the undesirable sound, noise attenuation devices or systems can be used. Noise attenuation devices include reflective and absorptive mufflers. Absorptive mufflers are most effective when the frequencies of the sound are greater than 500 Hz. Since the fundament frequencies for a positive displacement compressor, such as a screw compressor, are typically less than 500 Hz, absorptive mufflers are less effective than other types of mufflers.
- However, the pressure pulse frequency of screw compressors are predictable, that is, the pressure pulse frequency is a function of the number of lobes of the male rotor multiplied by its rotational speed. For example, a screw compressor having a 5 lobed male rotor, which rotates at 3,600 RPM generates a frequency of 5×3, 600/60 or 300 Hz. Therefore, for a compressor, such as a screw compressor, operating at a fixed speed, a reflective muffler, such as a side branch resonator, which is also referred to as a quarter wave resonator, may be configured to attenuate noise at a specific frequency. The side branch resonator typically comprises a component that forms a tee “T” adjacent a compressor discharge, with the tee being closed at the end opposite the compressor discharge. The length of the side branch resonator is configured or “tuned” to be one-fourth of one wavelength of the sound produced by the compressor to achieve the desired noise attenuation.
- Unfortunately, even with the compressor operating at a fixed speed, there are variations in ambient conditions, such as pressure and temperature of the refrigerant gas used in the system. Variations in the ambient conditions can likewise vary the frequency of the noise produced by the system, as such ambient condition variations can likewise change the acoustic velocity of the refrigerant gas. The term acoustic velocity is defined as the velocity that sound travels through the refrigerant gas for a given set of ambient conditions. Thus, it is generally not possible to attenuate the noise generated by a fixed speed compressor with a single side branch or quarter-wave resonator. Further, for reasons of increased compressor efficiency, it is often desirable to employ variable speed drives to power the compressor motors, resulting in compressors running at variable speeds.
- What is needed is a cost-effective, efficient and easily implemented method or apparatus for compressor noise attenuation that may be used with variable speed compressors.
- The present invention relates to a resonator arrangement for a closed fluid system including a body having a passageway in fluid communication with a closed fluid system. A piston is movable within the passageway wherein a position of the piston within the passageway defines a noise attenuation frequency for the closed fluid system. A control arrangement selectively positions the piston within the passageway to generate a noise attenuation frequency corresponding to a noise frequency generated by the closed fluid system.
- The present invention further relates to a variable noise attenuation device for use with an HVAC&R fluid system including a body having a passageway in fluid communication with an HVAC&R fluid system. A piston is movable within the passageway wherein a position of the piston within the passageway defines a noise attenuation frequency for the HVAC&R fluid system. A proportional valve selectively provides a pressurized fluid from the HVAC&R fluid system to the piston to selectively position the piston within the passageway to generate a noise attenuation frequency corresponding to a noise frequency generated by the HVAC&R fluid system.
- The present invention yet further relates to a method for attenuating noise in a closed fluid system having the steps of providing a body having a passageway in fluid communication with a closed fluid system; providing a piston movable within the passageway wherein a position of the piston within the passageway defines a noise attenuation frequency for the closed fluid system; providing a control arrangement for providing a pressurized fluid to the piston; and positioning selectively the piston within the passageway to generate a noise attenuation frequency corresponding to a noise frequency generated by the closed fluid system.
- An advantage of the present invention is that it attenuates noise of variable frequency.
- A further advantage of the present invention is that it is inexpensive to manufacture.
- Other features and advantages of the present invention will be apparent from the following more detailed description of the preferred embodiment, taken in conjunction with the accompanying drawings which illustrate, by way of example, the principles of the invention.
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FIG. 1 is a schematic of a variable speed HVAC&R system having a variable frequency resonator of the present invention. -
FIG. 2 is an enlarged partial schematic of the HVAC&R system including an enlarged elevation view of the variable frequency resonator of the present invention. -
FIG. 3 is an enlarged partial schematic of the HVAC&R system including an enlarged elevation view of an embodiment of the variable frequency resonator of the present invention. - Wherever possible, the same reference numbers will be used throughout the drawings to refer to the same or like parts.
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FIG. 1 illustrates generally aHVAC&R system 10 incorporating the present invention. AnAC power source 12 supplies AC power to a variable speed drive (VSD) 14, which in turn, supplies AC power to amotor 18 for driving acompressor 20. Acontrol panel 16 controls both the output frequency and the voltage fromVSD 14 that is supplied tomotor 18, which selectively varies both the torque and speed ofmotor 18, and likewise varies the speed ofcompressor 20.Control panel 16 includes an analog to digital (A/D) converter, a microprocessor, a non-volatile memory, and an interface board to control operation of therefrigeration system 10. Thecontrol panel 16 can also be used to control the operation of theVSD 14, themonitor 18 and thecompressor 20.Compressor 20 receives refrigerant gas at its inlet and discharges compressed refrigerant gas from its outlet throughdischarge line 30. Optionally, other compressors may operate in parallel withcompressor 20 to increase the capacity of thesystem 10. These compressors are typically positive displacement compressors, such as screw, reciprocating or scroll, having a wide range of cooling capacity, but may also include other compressor constructions. - After refrigerant gas is discharged by
compressor 20 throughdischarge line 30 towardcondenser 22, the refrigerant gas is directed past avariable resonator 26, such as a quarter wave resonator.Variable resonator 26 is continuously tuned, as will be described in further detail below, to attenuate both the pressure pulses and the mechanical noise generated by the meshing and unmeshing of the rotors that is the result of backlash and movement between the rotors. Thevariable resonator 26 can attenuate both the pressure pulses and the mechanical rotor noise, since each occurs at substantially the same frequency. Once the refrigerant gas passesvariable resonator 26, it is serially directed to condenser 22 and then toevaporator 24 where the refrigerant gas is placed in a non-mixing heat exchange relationship with fluids outside thesystem 10 to maintain temperature control in a structure before returning the refrigerant gas to thecompressor 20 to repeat the cycle. Theconventional HVAC&R system 10 includes many other features that are not shown inFIG. 1 . These features have been purposely omitted to simplify the drawing for ease of illustration. - Referring to
FIG. 2 ,variable resonator 26 includes abody 38, such as a tube or cylinder, which defines apassageway 39. Astop 48 having anaperture 49 is secured to one end ofbody 38, and acap 40 is secured to the opposite end ofbody 38. The end ofbody 38 having thestop 48 is connected todischarge line 30 so thatpassageway 39 ofbody 38 is in fluid communication with the refrigerant gas flowing throughdischarge line 30. Apiston 42 is inserted inside ofpassageway 39 that is slidable or movable withinpassageway 39, thepiston 42 further includes aseal 44, such as an O-ring, to provide a substantially fluid tight seal betweenpiston 42 and aninside surface 41 ofbody 38 aspiston 42 slides alongpassageway 39. Aresilient device 46, such as a spring, is interposed betweenpiston 42 andcap 40 to urgepiston 42 into movement alongpassageway 39 in a direction away fromcap 40, the travel of thepiston 42 in this direction being limited bystop 48. Thus, the travel of thepiston 42 alongpassageway 39 is limited by thestop 48, in one direction, and by thecap 40, minus the thickness of the compressedresilient device 46, in the other direction. - It is desirable to control the position of the
piston 42 within thepassageway 39, in which avariable resonator length 50 is defined by the distance between the lower surface ofpiston 42 and the lower surface ofstop 48. Thevariable resonator length 50 ofresonator 26, which is a side branch resonator, operates in accordance with the following equation stated symbolically as
F=C/(4×1) [1] - Wherein F is the resonant frequency of the
resonator 26; C is the sonic speed or acoustic velocity of the fluid traveling through theresonator 26; and 1 is theresonator length 50. Thus, thevariable resonator length 50 preferably corresponds to one quarter of a wavelength, such as the wavelengths generated during the operation of thecompressor 20, which can be attenuated by theresonator 26. While the single position of a fixed length resonator may effectively attenuate noise of a specific wavelength corresponding to a compressor operating at a fixed speed and a specific set of ambient conditions, such unchanging operating conditions are unrealistic. In other words, changing ambient conditions, such as temperature, also changes the density of the refrigerant, which changes the sonic speed C of the refrigerant, which changes the resonator length required to attenuate the noise generated by the compressor as discussed in equation [1]. A fixed length resonator cannot accommodate these changing conditions. Additionally, the compressor of the present invention operates at variable speeds, which, in turn, results in variable frequencies. Thus, selective control of the position of thepiston 42 within thepassageway 39 of theresonator 26 is required for consistent, noise attenuation. - To achieve positional control of the
piston 42 within thepassageway 39, avalve 28, such as a proportional valve, is controlled by thecontrol panel 16 to selectively provide pressurized refrigerant gas from apressure line 36 throughcap 40. To increase the amount of pressure in thepressure line 36, thecontrol panel 16 actuates thevalve 28 to bleed pressurized refrigerant gas from ahigh pressure line 34, which is in fluid communication with thecompressor discharge 30, to provide to thepressure line 36. Conversely, to decrease the amount of pressure in thepressure line 36, thecontrol panel 16 actuates thevalve 28 to bleed pressurized refrigerant gas from thepressure line 36 to provide to thelow pressure line 32, which may be connected to a port in thecompressor 20, or to the suction line at the inlet of thecompressor 20. Alternately, thelow pressure line 32 may be connected to a separate container (not shown) that is maintained at an even lower pressure than the suction line at the compressor inlet to provide an even wider range of pressure differential, if desired. In other words, the amount of pressure in thepressure line 36 can range anywhere from the discharge pressure of thehigh pressure line 34 to the lower pressure contained in thelow pressure line 32 to effect movement of thepiston 42 along thepassageway 39 of theresonator body 38. - To effect movement of the
piston 42 within thepassageway 39, the net force that is applied to the surface of thepiston 42, which is facing thecap 40 must be sufficiently different from the net force that is applied to the opposite surface of thepiston 42 which faces theaperture 49. There must be a sufficient difference in forces acting on the opposed surfaces of thepiston 42 to overcome any combination of frictional forces between theseal 44 and the inside surface ofbody 38, the weight of the piston 42 (if the piston moves vertically) and inertia of thepiston 42. The net force that is applied to the surface of thepiston 42 facing thecap 40 is applied in two parts. The first part of the net force is the pressure of the refrigerant gas in the pressure line 36 (PLINE) multiplied by the surface area of the piston 42 (ASURFACE) facing thecap 40. The second part of the net force is the force applied by theresilient device 46, which is the product of the spring constant (k) of the spring multiplied by the distance (d) the spring is compressed. The sum of the forces applied to the surface ofpiston 42 facing cap 40 (FCAP) is stated symbolically as
F CAP=(P LINE ×A SURFACE)+(k×d) [2] - The net force that is applied to the surface of the
piston 42 facing thestop 48 is applied in a single part. This single net force part is the pressure of the refrigerant gas in the discharge line 36 (PDISCHARGE) multiplied by the surface area of the piston 42 (ASURFACE) facing thestop 48. The force applied to the surface of thepiston 42 facing the stop 48 (FSTOP) is stated symbolically as
F STOP =P DISCHARGE ×A SURFACE [3] - Depending upon the configuration of the HVAC&R system, the PDISCHARGE may or may not vary. For example, if the system uses a water-cooled condenser, PDISCHARGE is considered substantially constant over the range of operating speeds of the compressor. In contrast, if an air-cooled condenser is used, the PDISCHARGE fluctuates, the fluctuation being either variable or substantially constant, depending upon the operating conditions. However, over an extreme range of operating conditions using the air-cooled condenser, it has been determined that the magnitude of PDISCHARGE will vary no more than about one percent of the
variable resonator length 50. Thus, the effect of PDISCHARGE fluctuation can typically be disregarded, while it is the sonic speed of the refrigerant that must be monitored. - Therefore, when there is a sufficient difference between the FCAP and the FSTOP forces, the
piston 42 is urged to move along thepassageway 39 in a direction away from the larger force. In other words, thepiston 42 will continue to move in this direction until the forces are substantially equal, or thepiston 42 has reached the end of its possible travel, that is, abutting thestop 48 or abutting thecap 40, minus the thickness of the compressedresilient device 46. When thepiston 42 abuts stop 48, thevariable resonator length 50 is at its shortest length and corresponds to the shortest one-quarter wavelength position, and therefore, the shortest wavelength, or highest frequency, that theresonator 26 can attenuate. Conversely, when thepiston 42 abuts thecap 40, minus the thickness of the compressedresilient device 46, thevariable resonator length 50 is at its maximum length, and corresponds to the longest one-quarter wavelength position, and therefore, the longest wavelength, or lowest frequency, that theresonator 26 can attenuate. It is appreciated by those skilled in the art that there exists a reciprocal relationship between frequency and wavelength. - The position of the
piston 42 is controlled by thecontrol panel 16 using a control algorithm. Based upon application of equations [1]-[3], the control algorithm determines the desiredresonator length 50, that is, the desired position of thepiston 42 within thepassageway 39, by reading the VSD frequency output that is supplied to thecompressor motor 18, and comparing the desired position of thepiston 42 to the position of thepiston 42 in thepassageway 39. The control algorithm may employ a look-up table that accounts for changes in ambient conditions, such as temperature and pressure, which likewise can change the acoustic velocity of the gas, and the desired position of thepiston 42 within thepassageway 39. Further, the control algorithm may further employ the look-up table or calculate the relationship between the spring length (d in equation [2]) and thepiston 42 position without needing to measure thepiston 42 position. Alternatively, the position of thepiston 42 in thepassageway 39 may be determined by a sensor, a rheostat, or any other suitable mechanical or electrical device that provides such positional information to thecontrol panel 16. In response to comparing the desired position of thepiston 42 to its actual position within thepassageway 39, thecontrol panel 16 sends a control signal(s) to thevalve 28. If the control algorithm determines that thevariable resonator length 50 should be decreased, the control signal from thecontrol panel 16 causes thevalve 28 to actuate to bleed pressurized refrigerant from thehigh pressure line 34 to thepressure line 36, thereby increasing the pressure in thepressure line 36. The combined forces, generated from the pressure in thepressure line 36 and the compressedresilient device 46, are applied to thepiston 42, which collectively define force FCAP as previously discussed in equation [2]. The opposing force that is applied to thepiston 42 defines force FSTOP as previously discussed in equation [3]. When the FCAP force sufficiently exceeds the FSTOP force, thepiston 42 slides toward thestop 48, thereby decreasing thevariable resonator length 50. - Conversely, if the algorithm determines that the
resonator length 50 should be increased, the control signal from thecontrol panel 16 causes thevalve 28 to actuate to bleed pressurized refrigerant from thepressure line 36 to thelow pressure line 32, thereby decreasing the pressure in thepressure line 36. The combined forces generated from the pressure in theadjustable pressure line 36 and the compressedresilient device 46 are applied to thepiston 42, which collectively define force FCAP as previously discussed in equation [2]. The opposing force that is applied to thepiston 42 defines force FSTOP as previously discussed in equation [3]. When the FSTOP force sufficiently exceeds the FCAP force, thepiston 42 slides toward thecap 40, thereby increasing thevariable resonator length 50. - Although a preferred embodiment of the
resonator 26 discloses thevalve 28 controlling the position of thepiston 42 by selectively providing pressurized refrigerant gas betweenlines HVAC&R system 10, it is appreciated that pressurized refrigerant from a source that is independent from theHVAC&R system 10 may also be used. Additionally, other pressurized fluids each from independent sources of pressurized fluid such as air or other compressible gas, or even incompressible fluids may also be used with thevalve 28 to selectively move thepiston 42 along thepassageway 39. However, the use of such gases or fluids, if incompatible with the efficientoperations HVAC&R system 10, may need to remain separate from the refrigerant in theHVAC&R system 10. Alternately,piston 42 may also be magnetically or electrically displaced within thepassageway 39. - For example, referring to
FIG. 3 , which is otherwise the same asFIG. 2 except as shown, pressurized fluids are selectively provided to or bled from thepressure line 36 of aresonator 126 by thevalve 28 from an independent pressurizedfluid source 154 and an independentfluid receptacle 152. Thefluid receptacle 152 receives pressurized fluid that is bled from thepressure line 36 when thecontrol panel 16 determines that thevariable resonator length 50 needs to be increased to likewise urge thepiston 42 to move along thepassageway 39 of theresonator body 38 toward thecap 40. Conversely, the pressurizedfluid source 154 provides pressurized fluid to thepressure line 36 when thecontrol panel 16 determines that thevariable resonator length 50 needs to be decreased to likewise urge thepiston 42 to move along thepassageway 39 of theresonator body 38 toward thestop 48. The pressurizedfluid source 154 is pressurized to a higher level than thereceptacle 152, and may be pressurized to a much higher pressure than the discharge pressure from thedischarge line 30, if desired. By providing highly pressurized fluid in pressurizedfluid source 154, it may be possible to eliminate the need for theresilient device spring 46, and decrease the response time for movement of thepiston 42 along thepassageway 39 of theresonator body 38. - Optionally, a
second valve 129 that is also controlled by thecontrol panel 16 is provided to selectively provide pressurized fluid from ahigh pressure line 158 to a variable pressure line 156. To decrease the amount of pressure in the variable pressure line 156, pressurized fluid may be bled to thereceptacle 152 through alow pressure line 160. To ensure the pressurized fluid that is provided to theresonator body 38 from thesecond valve 129 remains separate from the refrigerant fluid of theHVAC&R system 10, i.e., the refrigerant gas flowing in thedischarge line 30, the pressurized fluid from thesecond valve 129 is received in an expandable/contractable toroidal container 162. The container 162 is disposed between thestop 48 and thepiston 42 and is composed of a resilient material that permits the container 162 to expand or contract in response to sufficient differences between forces FCAP and FSTOP which result in movement of thepiston 42 with respect to the container 162. Preferably, the container 162 remains adjacent to the inside thesurface 41 of theresonator body 38 and collapses upon itself as the container 162 is maintained in contact with thepiston 42 as it moves along thepassageway 39, possibly by use of baffles. Optionally, a resilient device (not shown) may be provided inside the container 162. Additionally, the container 162 preferably provides a uniform cross sectional profile within thepassageway 39 to further provide predictable noise attenuation behavior as theresonator length 50 is varied as previously described. - It is appreciated that any number of combinations of independently provided pressurized fluids from pressurized sources or receptacles may be used with the pressurized refrigerant gas from the HVAC&R system, and that these pressurized fluids may or may not need to be separated from each other. It is also appreciated that any number of valves may be used to control the flow of the pressurized fluids as discussed.
- While the invention has been described with reference to a preferred embodiment, it will be understood by those skilled in the art that various changes may be made and equivalents may be substituted for elements thereof without departing from the scope of the invention. In addition, many modifications may be made to adapt a particular situation or material to the teachings of the invention without departing from the essential scope thereof. Therefore, it is intended that the invention not be limited to the particular embodiment disclosed as the best mode contemplated for carrying out this invention, but that the invention will include all embodiments falling within the scope of the appended claims.
Claims (39)
1. A resonator arrangement for a closed fluid system comprising:
a body having a passageway in fluid communication with a closed fluid system;
a piston movable within the passageway wherein a position of the piston within the passageway defines a noise attenuation frequency for the closed fluid system;
a control arrangement to selectively position the piston within the passageway to generate a noise attenuation frequency corresponding to a noise frequency generated by the closed fluid system.
2. The resonator of claim 1 wherein the control arrangement includes a pressurized fluid to selectively position the piston.
3. The resonator of claim 2 wherein the pressurized fluid to selectively position the piston is taken from a pressurized fluid source that is independent of the closed fluid system.
4. The resonator of claim 3 wherein the pressurized fluid to selectively position the piston is separated from the fluid in the closed fluid system.
5. The resonator of claim 3 wherein the pressurized fluid to selectively position the piston is the same as the fluid in the closed fluid system.
6. The resonator of claim 2 wherein the pressurized fluid to selectively position the piston is taken from the closed fluid system.
7. The resonator of claim 3 wherein the pressurized fluid provided to selectively position the piston within the passageway in a direction to generate a decreased noise attenuation frequency corresponding to the noise frequency generated by the closed fluid system is taken from a pressurized fluid source that is independent of the closed fluid system; and
wherein the pressurized fluid provided to selectively position the piston within the passageway in a direction to generate an increased noise attenuation frequency corresponding to the noise frequency generated by the closed fluid system is taken from the closed fluid system.
8. The resonator of claim 7 wherein the pressurized fluid taken from the pressurized fluid source that is independent of the closed fluid system is separated from the fluid in the closed fluid system.
9. The resonator of claim 3 wherein the pressurized fluid provided to selectively move the piston within the passageway in a direction to generate an increased noise attenuation frequency corresponding to the noise frequency generated by the closed fluid system is taken from a pressurized fluid source that is independent of the closed fluid system; and
wherein the pressurized fluid provided to selectively move the piston within the passageway in a direction to generate a decreased noise attenuation frequency corresponding to the noise frequency generated by the closed fluid system is taken from the closed fluid system.
10. The resonator of claim 9 wherein the pressurized fluid taken from the pressurized fluid source that is independent of the closed fluid system is separated from the fluid in the closed fluid system.
11. The resonator of claim 1 wherein the closed fluid system is an HVAC&R system.
12. The resonator of claim 11 wherein the HVAC&R system includes a variable speed drive.
13. The resonator of claim 1 wherein the control arrangement includes a valve.
14. The resonator of claim 1 wherein the control arrangement includes a proportional valve.
15. The resonator of claim 1 further comprising a resilient device within the passageway to urge the piston to move in a direction within the passageway.
16. The resonator of claim 15 wherein the resilient device is a spring.
17. The resonator of claim 15 further comprising a resilient device within the passageway to urge the piston to move in a direction within the passageway toward the closed fluid system.
18. The resonator of claim 15 further comprising a resilient device within the passageway to urge the piston to move in a direction within the passageway away from the closed fluid system.
19. A variable noise attenuation device for use with an HVAC&R fluid system comprising:
a body having a passageway in fluid communication with an HVAC&R fluid system;
a piston movable within the passageway wherein a position of the piston within the passageway defining a noise attenuation frequency for the HFAC&R fluid system;
a proportional valve selectively providing a pressurized fluid from the HVAC&R fluid system to the piston to selectively position the piston within the passageway to generate a noise attenuation frequency corresponding to a noise frequency generated by the HFAC&R fluid system.
20. The variable noise attenuation device of claim 19 wherein the proportional valve is in fluid communication with a positive displacement compressor.
21. The variable noise attenuation device of claim 20 wherein the positive displacement compressor is a screw compressor or a reciprocating compressor.
22. The variable noise attenuation device of claim 19 wherein the HVAC&R fluid system is a closed HVAC&R fluid system.
23. The variable noise attenuation device of claim 19 wherein the HVAC&R fluid system includes a variable speed drive.
24. A method for attenuating noise in a closed fluid system, the steps comprising:
providing a body having a passageway in fluid communication with a closed fluid system;
providing a piston movable within the passageway wherein a position of the piston within the passageway defines a noise attenuation frequency for the closed fluid system;
providing a control arrangement for providing a pressurized fluid to the piston; and
positioning selectively the piston within the passageway to generate a noise attenuation frequency corresponding to a noise frequency generated by the closed fluid system.
25. The method of claim 24 wherein the step of providing the control arrangement for providing the pressurized fluid to the piston includes providing the pressurized fluid from a pressurized fluid source that is independent of the closed fluid system.
26. The method of claim 25 wherein the step of providing the control arrangement for providing the pressurized fluid from the pressurized fluid source that is independent of the closed fluid system further includes the step of separating the pressurized fluid from the pressurized fluid source that is independent of the closed fluid system from the fluid in the closed fluid system.
27. The method of claim 25 wherein the pressurized fluid from the pressurized fluid source that is independent of the closed fluid system is the same as the fluid in the closed fluid system.
28. The method of claim 24 wherein the step of providing the control arrangement for providing the pressurized fluid to the piston includes providing the pressurized fluid taken from the closed fluid system.
29. The method of claim 25 wherein the step of providing the control arrangement for providing the pressurized fluid from the pressurized fluid source that is independent of the closed fluid system to the piston includes providing the pressurized fluid from the pressurized fluid source that is independent of the closed fluid system to selectively position the piston within the passageway in a direction to generate a decreased noise attenuation frequency corresponding to the noise frequency generated by the closed fluid system; and
providing the control arrangement for providing the pressurized fluid from the closed fluid system to selectively position the piston within the passageway in a direction to generate an increased noise attenuation frequency corresponding to the noise frequency generated by the closed fluid system.
30. The method of claim 29 wherein the pressurized fluid from the pressurized fluid source that is independent of the closed fluid system to selectively position the piston within the passageway in a direction to generate the decreased noise attenuation frequency corresponding to the noise frequency generated by the closed fluid system is separated from the fluid in the closed fluid system.
31. The method of claim 25 wherein the step of providing the control arrangement for providing the pressurized fluid from the pressurized fluid source that is independent of the closed fluid system to the piston includes providing the pressurized fluid from the pressurized fluid source that is independent of the closed fluid system to selectively position the piston within the passageway in a direction to generate an increased noise attenuation frequency corresponding to the noise frequency generated by the closed fluid system; and
providing the pressurized fluid from the closed fluid system to selectively position the piston within the passageway in a direction to generate a decreased noise attenuation frequency corresponding to the noise frequency generated by the closed fluid system.
32. The method of claim 31 wherein the pressurized fluid from the pressurized fluid source that is independent of the closed fluid system to selectively position the piston within the passageway in a direction to generate an increased noise attenuation frequency corresponding to the noise frequency generated by the closed fluid system is separated from the fluid in the closed fluid system.
33. The method of claim 24 wherein the closed fluid system is an HVAC&R system.
34. The method of claim 33 wherein the HVAC&R system includes a variable speed drive.
35. The method of claim 24 wherein the step of providing the control arrangement includes a step of providing a valve.
36. The method of claim 24 wherein the step of providing the control arrangement includes providing a proportional valve.
37. The method of claim 24 further including an additional step, before the step of providing a control arrangement for providing a pressurized fluid from the closed fluid system to the piston, of providing an algorithm, the step of providing an algorithm further including the steps of
reading a variable speed drive frequency output; and
comparing the variable speed drive frequency output to the position of the piston in the passageway; and
wherein the step of positioning selectively the piston within the passageway to generate the noise attenuation frequency corresponding to the noise frequency generated by the closed fluid system includes positioning selectively the piston within the passageway to generate the noise attenuation frequency corresponding to the noise frequency generated by the closed fluid system in response to the algorithm.
38. The method of claim 24 further including an additional step, before the step of providing a control arrangement for providing pressurized fluid, of providing a resilient device within the passageway to urge the piston into movement within the passageway toward the closed fluid system.
39. The method of claim 38 wherein the resilient device is a spring.
Priority Applications (3)
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US10/793,130 US20050194207A1 (en) | 2004-03-04 | 2004-03-04 | Apparatus and method of sound attenuation in a system employing a VSD and a quarter-wave resonator |
TW094105781A TW200537029A (en) | 2004-03-04 | 2005-02-25 | Apparatus and method of sound attenuation in a system employing a VSD and a quarter-wave resonator |
PCT/US2005/006511 WO2005093246A1 (en) | 2004-03-04 | 2005-03-02 | Apparatus and method of sound attenuation in a system employing a quarter-wave resonator |
Applications Claiming Priority (1)
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US10/793,130 US20050194207A1 (en) | 2004-03-04 | 2004-03-04 | Apparatus and method of sound attenuation in a system employing a VSD and a quarter-wave resonator |
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US10/793,130 Abandoned US20050194207A1 (en) | 2004-03-04 | 2004-03-04 | Apparatus and method of sound attenuation in a system employing a VSD and a quarter-wave resonator |
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US9476533B2 (en) * | 2015-01-13 | 2016-10-25 | Embraer S.A. | Enhanced fluid attenuators and methods, especially useful for aircraft hydraulic systems |
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US20180221207A1 (en) * | 2017-02-08 | 2018-08-09 | Andrew L. Cobabe | Devices for filtering sound and related methods |
US10821027B2 (en) * | 2017-02-08 | 2020-11-03 | Intermountain Intellectual Asset Management, Llc | Devices for filtering sound and related methods |
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Also Published As
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WO2005093246A1 (en) | 2005-10-06 |
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