CN1086801C - Thermoacoustic refrigerator - Google Patents
Thermoacoustic refrigerator Download PDFInfo
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- CN1086801C CN1086801C CN 95106913 CN95106913A CN1086801C CN 1086801 C CN1086801 C CN 1086801C CN 95106913 CN95106913 CN 95106913 CN 95106913 A CN95106913 A CN 95106913A CN 1086801 C CN1086801 C CN 1086801C
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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
- F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
- F25B9/14—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the cycle used, e.g. Stirling cycle
- F25B9/145—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the cycle used, e.g. Stirling cycle pulse-tube cycle
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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
- F25B2309/00—Gas cycle refrigeration machines
- F25B2309/14—Compression machines, plants or systems characterised by the cycle used
- F25B2309/1404—Pulse-tube cycles with loudspeaker driven acoustic driver
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Abstract
The present invention relates to a novel thermoacoustics refrigerator device. The present invention can consume sound energy and use a sound refrigeration function generated by a semiwave resonance sound field or a similar resonance sound field to transfer the heat quantity of a low temperature heat source to a high temperature heat source. The novel thermoacoustics refrigerator is composed of a speaker 1, sound wave guide tubes 2, 6, 8, heat exchangers 3, 5, a heat regenerator 4, a resonating tube 7, a sound absorber 9 and a sound wave guide tube or guide tube sets 10, 11, wherein the sound wave guide tube is provided with a sound impedance regulator. The length of the thermoacoustics refrigerator is approximately the half wavelength of a sound wave or is quarter wavelength larger than or half wavelength smaller than the sound wave. In the heat regenerator of the thermoacoustics refrigerator, thermoacoustics effects generated by the travelling wave part and the standing wave part of a sound field are both pump thermal effects.
Description
The present invention relates to one type New Refrigerating machine, particularly a kind of thermoacoustic refrigeration machine that utilizes the pump heat effect refrigeration in the thermoacoustic effect.Hot sound refrigerating machine consumes by the next acoustic energy of the meritorious power conversion of other forms such as electric energy or mechanical energy, or directly utilize acoustic energy, by the compressible fluid working media (sound) of vibration and the thermal interaction of solid working media, the heat delivery of lower temperature thermal source is arrived the thermal source of higher temperature, thereby realize freezing.
At present, known hot sound refrigerating machine such as United States Patent (USP) 4,398,398 (Wheailey 8/1983), 4,772,201 (Hofler 2/1988) are described.This is a kind of hot sound refrigerating machine (L ≈ 1/2 λ of half-wavelength, λ is that sound wave is long), the thermoacoustic effect work that it only utilizes the irreversibility of working media and standing-wave sound field to produce, thereby the conversion of the intensity of the thermoacoustic effect of its generation and effective energy and utilization rate are lower.And for example United States Patent (USP) 4,114,380 (Ceperley 9/1978), 4,355,517 (Ceperley 10/1982) are described, the thermoacoustic effect work that they utilize the row ripple to produce, this is the long hot sound refrigerating machine (L ≈ λ) of a kind of all-wave, and the impedance of its sound travel is difficult for coupling and realizes difficulty, does not see the report that practices so far.
The present invention is on the basis of system research thermoacoustic effect, proposes a kind of new method, flow process and design, can overcome or reduce the shortcoming of hot sound refrigerating machine in the past, improves the intensity of thermoacoustic effect and the conversion and the utilization rate of effective energy to greatest extent.
The invention provides the novel refrigerator device that utilizes thermoacoustic effect of a class, its energy uses electric energy, mechanical energy to change next acoustic energy or directly use acoustic energy, its sound field adopts the design of half-wave resonance sound field (L ≈ 1/2 λ) or nearly resonance sound field (1/2 λ＜L＜1/4 λ), comprehensively and reasonably utilize the characteristics of isothermal wall thermoacoustic effect and adiabatic wall thermoacoustic effect, and the pump heat effect of the thermoacoustic effect that partly produces of the standing wave of the thermoacoustic effect that partly produces of the capable ripple that utilizes sound field simultaneously and sound field, heat is transferred to high temperature heat source from low-temperature heat source, realize refrigeration.
In order to illustrate thought of the present invention, below thermoacoustic effect is carried out necessary explanation.
Thermoacoustic effect is meant compressible fluid working medium with thermal expansivity, and have between the solid working media of big thermal capacity and thermal conductivity factor, because the sound oscillation of the relative solid of fluid and generation thermal interaction, and the time equal thermodynamic energy graded effect that causes.
Divide by the solid outside wall surface and the thermo-contact mode of outer thermal source, thermoacoustic effect can be divided into isothermal wall thermoacoustic effect, adiabatic wall thermoacoustic effect and general situation thermoacoustic effect.
The outside wall surface that isothermal wall thermoacoustic effect is meant the solid working media is during with outer thermal source ideal thermo-contact, because the solid as a result of desirable thermo-contact and the mean temperature of fluid are constant in arbitrary cross section, and identical with outer heat source temperature, at this moment the time equal energy effect of the horizontal exchange heat between working media and external heat source appears.The characteristics of isothermal wall thermoacoustic effect are: 1. in low acoustical conductivity than (the acoustical conductivity ratio is local fluid density, the velocity of sound, the ratio of three products of velocity perturbation amplitude and pressure oscillation amplitude) zone, the outside thermal source of working media is emitted heat, 2. in the zone of high acoustical conductivity ratio, if the Prandtl number of fluid working medium (ratio of viscosity and thermal conductivity factor) is enough little, working media is by outer thermal source draw heat, 3. in working media and acoustical conductivity regularly than one, the intensity of isothermal wall thermoacoustic effect is relevant with the ratio of the thermal penetration depth of acoustic streaming road width and fluid with efficient, and is better when the thermal penetration depth of acoustic streaming road equivalent yardstick and fluid is suitable.
The outside wall surface that the adiabatic wall thermoacoustic effect is meant the solid working media is during with outer thermal source ideal heat insulation, because desirable heat-insulating result, (gross energy stream is enthalpy stream and thermally conductive heat stream sum to gross energy stream, also equal hot-fluid and sound merit stream sum) will remain unchanged, at this moment the time equal energy effect of the mutual conversion of heat energy and acoustic energy appears.In the adiabatic wall thermoacoustic effect, acoustic energy is consumed and is converted to heat energy during refrigeration, and hot-fluid is pumped into temperature end by low-temperature end simultaneously.
When the outside wall surface of solid working media with outside thermal source the thermoacoustic effect of general situation takes place when being in limited thermo-contact.Isothermal wall thermoacoustic effect and adiabatic wall thermoacoustic effect are two limit situations of general situation thermoacoustic effect.
Arbitrary sound field can be considered the standing wave part and the row ripple part sum of sound field, and in the adiabatic wall thermoacoustic effect during refrigeration, the effect that the standing wave of sound field partly produces has following characteristics: 1. the thermoacoustic effect intensity of Chan Shenging is lower; 2. direction of heat flow is always hanged down the zone of acoustical conductivity ratio by the field flow orientation of high acoustical conductivity ratio; 3. work as low-temperature end in the zone of high acoustical conductivity ratio, temperature end produces refrigeration effect in the zone of low acoustical conductivity ratio when bearing less thermograde.Direction of heat flow flows to temperature end by low-temperature end, and acoustic energy is used to overcome the irreversible dissipation of working media except that part, and a part also is used to pump heat.The direction of sound merit stream can flow to temperature end by low-temperature end, also can flow to low-temperature end by temperature end; 4. in thermograde one regularly, the maximum when intensity of the pump fuel factor that the standing wave of sound field partly produces and efficient are about the thermal penetration depth of fluid when acoustic streaming road equivalent yardstick.At this moment fluid working medium and solid working media have moderate thermo-contact, and thermoacoustic effect relies on the limited thermodynamics irreversibility work of working media.To completely reversibility or complete irreversible working media, the pump fuel factor that the standing wave of sound field part can not produce.
The effect that the capable ripple of sound field partly produces has following characteristics: 1. the thermoacoustic effect intensity of Chan Shenging higher (to the same pressure and the sound wave of velocity amplitude, the energy-flux density that can reach is about the accessible twice of standing wave); 2. always the direction (direction that the row ripple is propagated) with sound merit stream is opposite for direction of heat flow.And ideally hot-fluid and merit flow equal and opposite in direction when the working media completely reversibility, and hot-fluid is less than flowing with merit when there is the thermodynamics irreversibility in working media; 3. when the zone of low-temperature end at high acoustical conductivity ratio, temperature end is in the zone of low acoustical conductivity ratio, flow to low-temperature end by temperature end and produce refrigeration effect constantly bearing less thermograde harmony merit flow path direction, direction of heat flow flows to temperature end by low-temperature end, and part acoustic energy is consumed and is converted to heat energy; 4. in thermograde one regularly, the intensity of the thermoacoustic effect that the capable ripple of sound field partly produces and efficient maximum when the equivalent yardstick in acoustic streaming road is compared less and don't caused bigger viscous dissipation with thermal penetration depth.At this moment fluid working medium and solid working media have thermo-contact preferably, and thermoacoustic effect relies on the thermodynamics invertibity work of working media.To the working media of completely reversibility, it is most effective that the intensity of the pump fuel factor that the capable ripple of sound field partly produces and power conversion are utilized.
The working media that produces thermoacoustic effect should be that the compressible fluid media (medium) with higher thermal expansion degree, low Prandtl number has the solid dielectric of thermal capacity greatly with comparing with fluid media (medium).Special fluid medium, bigger in the high and low temperature temperature difference, and energy flux density is required lower occasion (as the hot sound refrigerating machine of cryogenic temperature than low and less refrigeration work consumption), can adopt the gas that molecular formula is simple, molecular weight is less (as helium, hydrogen, nitrogen etc.); Less in the high and low temperature temperature difference, and energy flux density required bigger occasion (as requiring to obtain the hot sound refrigerating machine of not too low cryogenic temperature and bigger refrigeration work consumption), better simply gas of the molecular formula of available higher operating pressure (as gases such as helium, nitrogen, carbon dioxide) or employing critical-temperature (can be adopted carbon dioxide near the near critical fluids of the simple molecules formula the environment temperature near as room temperature, propylene etc., but operating pressure should be near critical pressure).
The present invention adopts following several basic acoustics and hot part spare to realize.These parts respectively have different functions, and the functions such as providing, change, transport of acoustic energy, heat energy is provided in hot sound refrigerating machine.These basic elements of character are:
1. sonic transducer.Sonic transducer is parts of realizing the mutual conversion of meritorious energy such as electric energy, mechanical energy, pressure energy and acoustic energy.Can realize the conversion of meritorious energy and acoustic energy as electromagnetic type, piston type, air-flowing type loudspeaker etc., for hot sound refrigerating machine provides the energy; The electromagnetic viscosimeter formula, reciprocating-piston microphone or generator can be realized the conversion of acoustic energy and electric energy, reciprocating piston can be realized the conversion of acoustic energy and mechanical energy, compressor valve plate group, magnetic valve group or rotary valve group etc. can realize acoustic energy in pressure can mutual conversion etc., they can be exported the acoustic energy in the hot sound refrigerating machine.To realize that below other meritorious power conversion is that acoustic transducer is referred to as loudspeaker, is referred to as microphone and acoustic energy is converted to other meritorious energy transducer.
2. hot sound heat exchanger.Heat sound heat exchanger is to utilize isothermal wall thermoacoustic effect to realize the parts of the exchange heat of hot sound refrigerating machine and outer thermal source.Heat the heat exchanger that is positioned over high acoustical conductivity ratio zone in the hot sound refrigerating machine sound field is absorbed heat by outer thermal source, claims hot sound heat dump, is positioned over the outside thermal source heat release of hot sound heat exchanger in low acoustical conductivity ratio zone in the hot sound refrigerating machine sound field, claims hot sound radiator.The structure of heat sound heat exchanger can be to adopt the laminated construction of the good solid plate (as metallic plate) of thermal conductivity, forms the acoustic streaming road between plate and the plate; Also can adopt the structure of processing the passage of speaking in solid circular tube group or the monoblock solid, the solid porous material that can also adopt piling up of woven wire to form porous acoustic streaming road or use other type.In the heat sound heat exchanger, the shape in acoustic streaming road can be varied, and as rectangle, circle or ellipticalness, triangle, rhombus, hexagon etc., but acoustic streaming road equivalent yardstick should be suitable with the thermal penetration depth of fluid.The solid dielectric of heat sound heat exchanger should have good thermal conductivity, and the outer wall of solid dielectric should have good thermo-contact with outer thermal source, so that the temperature of whole heat exchanger such as is at temperature state as far as possible.The length of heat exchanger should be less with sound wave appearance ratio, runs off the zone of high acoustical conductivity than zone or low acoustical conductivity ratio to avoid same heat exchanger, makes the neither endothermic nor exothermic effect be cut down or offset.
3. thermal acoustic regenerator.Thermal acoustic regenerator is to utilize the adiabatic wall thermoacoustic effect to realize the pump heat effect of hot sound refrigerating machine and the critical component of acoustic energy and heat energy conversion.It is positioned over appropriate location in the hot sound refrigerating machine sound field, and consumption sound merit is transported to temperature end with heat by low-temperature end, realizes refrigeration.The acoustical conductivity that the design of thermal acoustic regenerator should make its two ends is than suitably so that power conversion and pump heat are smooth, and with heat sound heat exchanger can co-ordination.The structure of thermal acoustic regenerator can be the laminated construction of solid thin plate (as metallic plate), forms the acoustic streaming road between plate and the plate; Also can adopt the solid porous material (as granular materials) that forms porous acoustic streaming road or other type that piles up of woven wire.In the thermal acoustic regenerator, the shape in acoustic streaming road can be to adopt the combination of multiple shape in the varied or same regenerator.But the equivalent yardstick in acoustic streaming road should be about the thermal penetration depth (accounting for the zone of major part at standing-wave sound field) of local fluid, or much smaller than the thermal penetration depth (the wave sound field of being expert at accounts for the zone of major part) of fluid, or be an appropriate value less than the fluid thermal penetration depth (all accounting for the zone of suitable share in standing wave and row wave sound field).Thermal acoustic regenerator can be a straight tube, also can adopt the varying cross-section duct that shrinks to low-temperature end from temperature end, and as tubaeform continuous contraction, or trapezoidal staged is shunk.The solid dielectric of thermal acoustic regenerator should have preferably laterally (perpendicular to the acoustic propagation direction) thermal conductivity and relatively poor vertical (along the acoustic propagation direction) thermal conductivity (laminated construction of this available vertical layout is realized), so that whole regenerator is identical as far as possible in the temperature in same cross section, and don't can be because the heat conduction causes bigger being lost by the longitudinal heat flux of regenerator temperature end to low-temperature end.The thermal capacitance of regenerator solid dielectric on same cross section should be much larger than the thermal capacitance of fluid media (medium), and the thermocontact area of solid dielectric and fluid media (medium) should make thermoacoustic effect insufficient and cause unnecessary thermodynamics irreversible loss greatly to avoid incomplete thermo-contact.Thermal acoustic regenerator and outer thermal source should have good heat insulation, are lost to the thermotransport of low-temperature end by temperature end to the leakage heat and the thermoacoustic effect generation of environment avoiding.
4. hot acoustic resonance pipe.The solid pipeline that the two ends that hot acoustic resonance pipe is one section outside wall surface thermal insulation link to each other with the high and low temperature end respectively, its two are looked closely situation can be provided with high and low warm sound heat exchanger, to keep the two ends temperature constant.Its main effect is by the coupling of duct length in system, in whole system, produce half-wave resonance or nearly resonance sound field, and connect and to work in any two hot part spares of high temperature section and low-temperature zone, and don't can cause bigger decay of flowing to the hot-fluid loss harmony merit of low-temperature end by temperature end.The two ends acoustical conductivity of hot acoustic resonance pipe is than the zone of preferably crossing over high acoustical conductivity ratio and hanging down the acoustical conductivity ratio.Hot acoustic resonance pipe should adopt the relatively poor pipeline of thermal conductivity, and as thin metallic tubd or non-metallic pipe, or outside wall surface is nonmetallic compound sheet-metal duct for the metal inner surface face.The cross sectional shape of hot acoustic resonance pipe can be varied, but its acoustic streaming road equivalent yardstick should greater than or much larger than the thermal penetration depth of local fluid, to avoid because solid thermal conduction and thermoacoustic effect produce from the hot-fluid of temperature end to low-temperature end loses, but can not be too big so that the empty volume of whole system is too big, energy density is too low.Hot acoustic resonance pipe can adopt straight tube along the longitudinal direction, also can adopt from the varying cross-section duct of low-temperature end to the temperature end expansion, and as tubaeform continuous expansion, or the expansion of trapezoidal staged.Can fill in the pipe of hot acoustic resonance pipe or partially filled or do not fill heat sound regenerative material, distribute with the axial temperature that improves hot acoustic resonance pipe.The outside wall surface of hot acoustic resonance pipe and the outer thermal source heat insulation of should trying one's best is to avoid heat loss.The two ends of hot acoustic resonance pipe can be provided with (also can not being provided with) laminarization element, make flowing in the hot acoustic resonance pipe pipe approach laminar flow as far as possible, reduce or the loss of elimination turbulent mixture.
5. sound absorption device (or claim silencer).The sound absorption device be a kind of in sound field absorption sound merit and it is dissipated be the parts of heat energy.The effect of sound absorption device in hot sound refrigerating machine is to be used for substituting in some occasions acoustic energy is converted to the microphone of the meritorious energy of other form to form bigger traveling-wave component in hot machine appropriate location.Some occasions here are meant utilizes microphone that these less being unworthy of resulting energy in acoustic energy conversion back are utilized, or utilize this part energy too complicated, uneconomical, or the occasions such as mechanical part that need reduce motion for the simplicity that improves system and reliability.The form of sound absorption device can be varied, as aperture sound absorption device, Helmholtz acoustic resonator, porous material sound absorption device etc.The acoustic resistance part of sound absorption device can be made the form of can regulating, and realizes the adjusting of acoustic resistance as adopting needle-valve.
6. acoustic waveguide tube.Acoustic waveguide tube is one section or one group of solid pipeline that works in identical or close temperature.Its effect mainly is to be used for connecting the hot machine of heat sound to be in the feedback regulation loop of the two ends of same warm area with the formation sound wave, or is used for the intrinsic frequency of regulating system.
7. acoustic impedance adjuster.The acoustic impedance adjuster is to regulate and the parts of coupling acoustic impedance, with it can be in the hot machine of heat sound the appropriate location regulate and the size and the phase place of the sound oscillation (speed and pressure oscillation) of coupling locality.Three kinds of impedance types are arranged in sound travel, and acoustic resistance, acoustic capacitance and phonoreception are so the acoustic impedance adjuster also has three kinds of fundamental types.Acoustic resistance adjuster (or acoustic damping adjuster) can be a bit of pore pipe or a bit of porous media or an aperture control valve or its combination.The acoustic compliance adjuster is to connect a bigger cavity on the sound passage.And the acoustic(al) inertance adjuster generally is to connect one section elongated pipeline on the passage.These three kinds of basic adjusters can be used in combination separately or by modes such as parallel connection, series connection during actual the use, obtain required sound oscillation, regulate the amplitude and the phase place of certain position sound field with ad-hoc location in sound travel.
The hot sound refrigerating machine of indication of the present invention is to be made of above several basic acoustics and hot part spare.Selection that these several parts are different and combination, the hot sound refrigerating machine of formation different structure characteristics.The different selections and the combination of indication here all needs to satisfy such condition, and promptly a hot sound refrigerating machine comprises above several basic element of character at least; In low-temperature end, heat sound heat exchanger is from the low-temperature heat source heat absorption in the external world; In thermal acoustic regenerator, the capable ripple part of sound field and the thermoacoustic effect that standing wave partly produces all are to produce the pump heat effect, are about to heat and are transported to temperature end by low-temperature end; In temperature end, heat sound heat exchanger is to the high temperature heat source heat release in the external world; Sound field in the whole hot sound refrigerating machine is half-wave resonance sound field or nearly resonance sound field, and the resonance of sound field mates by hot acoustic resonance pipe and acoustic waveguide tube; The generation of the traveling-wave component of sound field is converted to the energy of other form by microphone or sound absorption device with acoustic energy, realizes by the audio feedback circuit that has the acoustic impedance adjuster simultaneously.
Adopt above-mentioned design, can improve the refrigerating capacity of hot sound refrigerating machine significantly, reduce the loss of various hot-fluid losses and available energy, improve the efficient of hot sound refrigerating machine.More owing to adopted design flexible, according to situation we can select the parts of multi-form different characteristics such as transducer combination (as want cube little, in light weight, when efficient is high, select electromagnetic piston or diaphragm type transducer for use, adopt higher operating frequency; And require that cryogenic temperature is lower, when refrigerating capacity is big, select the air-flowing type transducer for use), can satisfy the needs of different occasions like this.
Below in conjunction with accompanying drawing to the layout of the thermoacoustic refrigeration machine of indication of the present invention and the course of work more detailed explanation.
Fig. 1 is the structure chart that adopts the thermoacoustic refrigerator of single speaker drive.The arrow indication is the direction of merit stream (down together) among the figure.
Fig. 2 is the structure chart that adopts (two driving) hot sound refrigerating machine of sound absorption device in microphone alternate figures 1 structure.
In the hot sound refrigerating machine of Fig. 1, loudspeaker 1 (it can be piston type or diaphragm type, air-flowing type etc.) becomes acoustic energy to produce sound oscillation in system the power conversion of other form, and provides thermoacoustic effect to produce the required acoustic energy of pump heat effect to go waveshape.The high temperature acoustic waveguide tube 2 that works in environment temperature is used to transmit the terminal acoustic impedance of sound oscillation and speaker-matched 1, makes mechanical energy etc. be converted to acoustic energy smoothly, and makes elevated temperature heat sound radiator 3 work in the zone of low acoustical conductivity ratio.Utilizing the thermal acoustic regenerator 4 of the pump heat effect work in the capable ripple part of sound field and the thermoacoustic effect that the standing wave part is produced to consume part is simultaneously flowed by the part sound merit of loudspeaker 1, the heat that makes heat that low-temperature thermoacoustic heat dump 5 is absorbed by outside low-temperature heat source and the sound merit that is consumed be converted is pumped into temperature end together, and is emitted to environment by elevated temperature heat sound radiator 3.Work in the acoustic waveguide tube 6 realization low-temperature thermoacoustic heat dumps 5 of low-temperature end and being connected of hot acoustic resonance pipe 7 low-temperature end, hot acoustic resonance pipe 7 is used for wow flutter is propagated into temperature end by low-temperature end.The length of this interior heat acoustic resonance pipe should make its temperature end and acoustic impedance low-temperature end obtain coupling, makes it work in the zone of high acoustical conductivity ratio in low-temperature end, works in the zone of low acoustical conductivity ratio in temperature end.Acoustic waveguide tube 8 is used for the connection of hot acoustic resonance pipe 7 harmony absorbers 9, and be used for the impedance of compatible termini acoustic impedance harmony absorber 9, make the temperature end of hot acoustic resonance pipe 7 work in the zone of hanging down the acoustical conductivity ratio, so that acoustic energy is changed the operate as normal of harmony absorber smoothly.It is heat energy that sound absorption device 9 is used in system acoustic energy being dissipated, and produces a traveling-wave component that runs through thermal acoustic regenerator 4 in system.The acoustic waveguide tube 10 that has the acoustic impedance adjuster is used to form the primary feedback regulating loop of sound wave, makes each hot part spare be operated in kilter so that regulate capable ripple and the standing wave component (regulating the phase difference of pressure oscillation and velocity perturbation) in the thermal acoustic regenerator and mate acoustic impedance.The acoustic waveguide tube of band acoustic impedance adjuster or conduit group 11 are used for being connected of thermal acoustic regenerator 4 and hot acoustic resonance pipe 7 centre positions, form the inferior feedback regulation loop of one or more sound wave, so that the operating efficiency of thermal acoustic regenerator 4 obtains the performance of the best.Whole hot sound refrigerating machine from speaker sound to the length of sound absorption device should approximate the half-wavelength of sound wave or greater than the quarter-wave of sound wave with less than the half-wavelength of sound wave, thereby realize half-wave resonance or nearly resonance sound field, total effect is to make in the thermal acoustic regenerator phase place of pressure oscillation be ahead of the phase place of velocity perturbation, guarantee in thermal acoustic regenerator, the capable ripple part of sound field and the thermoacoustic effect that standing wave partly produces all are to produce the pump heat effect, are about to heat and are transported to temperature end by low-temperature end.
Fig. 2 is the structure with the main feedback loop 10 of sound absorption device 9 and sound wave in microphone 12 alternate figures 1.(it also can be piston type or diaphragm type to microphone 12, air-flowing type etc.) acoustic energy is converted to other form energy output for utilizing, or feed back to loudspeaker 1 and utilize again, and in sound field, produce a traveling-wave component, make in system, produce one run through thermal acoustic regenerator 4 from the traveling-wave component of temperature end to low-temperature end.Here microphone 12 and loudspeaker 1 are answered co-ordination (phase place of wow flutter that can be by control loudspeaker 1 and microphone 12 realizes), the direction that flows with assurance sound merit be by loudspeaker to microphone, and guarantee that in the thermal acoustic regenerator phase place of pressure oscillation is ahead of the phase place of velocity perturbation.The effect of other parts is identical with the effect of corresponding component in Fig. 1 structure among the figure.
Thermal acoustic regenerator and hot acoustic resonance pipe in same warm area work in the hot sound refrigerating machine of above indication can be made into coaxial configuration, to increase the compactedness of device.
Claims (11)
1. hot sound refrigerating machine, comprise the acoustic waveguide tube (10) of loudspeaker (1), room temperature acoustic waveguide tube (2), room temperature heat sound radiator (3), thermal acoustic regenerator (4), low-temperature thermoacoustic heat dump (5), low temperature acoustic waveguide tube (6), hot acoustic resonance pipe (7), room temperature acoustic waveguide tube (8), sound absorption device (9), band acoustic impedance adjuster or sound wave primary feedback regulating loop and time feedback regulation loop (11) that the conduit group is formed by order of placement, it is characterized in that: this hot sound refrigerating machine length is between quarter-wave and half-wavelength; The primary feedback regulating loop of sound wave is connected between acoustic waveguide tube (2) the harmony absorber import acoustic waveguide tube (9) of loudspeaker outlet, and the inferior feedback regulation loop (11) of sound wave is connected between thermal acoustic regenerator (4) and the hot acoustic resonance pipe (7).
2. by the described hot sound refrigerating machine of claim 1, it is characterized in that described loudspeaker is piston or the diaphragm type or the air-flowing type loudspeaker of motor-driven, Electromagnetic Drive.
3. by the described hot sound refrigerating machine of claim 1, it is characterized in that, described room temperature acoustic waveguide tube (2), thermal acoustic regenerator (4) and hot acoustic resonance pipe (7) are by metal tube or non-metallic pipe, the layout of its axis is shaped as linear, U-shaped, crooked shape or the crooked shape of part, the coaxial or non-coaxial setting of thermal acoustic regenerator (4) and hot acoustic resonance pipe (7).
4. by the described hot sound refrigerating machine of claim 1, it is characterized in that, the inner structure of described thermal acoustic regenerator (4) is the laminated construction of solid thin plate, stacked structure or the solid porous structure of other type or their combination of woven wire, and the profile of thermal acoustic regenerator (4) is a straight tube shape, the trapezoidal variable cross-section of the tubaeform or staged contraction of contraction is tubular continuously.
5. by the described hot sound refrigerating machine of claim 1, it is characterized in that, described hot acoustic resonance pipe (7) is the solid pipeline that there is well insulated in a section and the external world, be axial thermal conductivity relatively poor thin metallic tubd or non-metallic pipe, or for outside wall surface be the compound light-wall pipe of non-metallic material for the metal material internal face, hot acoustic resonance pipe (7) is shaped as straight tube, expands trapezoidal varying cross-section duct tubaeform or the staged expansion continuously, and the two ends of hot acoustic resonance pipe (7) are provided with the laminarization element.
6. by the described hot sound refrigerating machine of claim 1, it is characterized in that, the solid plate formula laminated construction of internal structure for making of described room temperature heat sound radiator (3) and low-temperature thermoacoustic heat dump (5) by the thermal conductivity good material, perhaps by the monoblock solid structure of processing the passage of speaking in the monoblock solid, perhaps pile up the formation cellular structure for woven wire, in the heat sound heat exchanger, the acoustic streaming road be shaped as rectangle, circle, ellipse, triangle, rhombus or hexagon.
7. by the described hot sound refrigerating machine of claim 1, it is characterized in that described sound absorption device (9) is aperture sound absorption device, Helmholtz acoustic resonator or porous material sound absorption device, the acoustic resistance of sound absorption device (9) partly adopts adjustable needle-valve.
8. by the described hot sound refrigerating machine of claim 1, it is characterized in that described band acoustic impedance adjuster is acoustic resistance adjuster, acoustic capacitance adjuster or phonoreception adjuster; The acoustic resistance adjuster is a bit of pore pipe or a bit of porous media or an aperture control valve or their combination; The acoustic compliance adjuster is to connect a bigger cavity on the sound passage; Connect one section elongated pipeline on the sound passage of acoustic(al) inertance adjuster; In parallel or the series connection use of acoustic resistance adjuster, acoustic capacitance adjuster and phonoreception adjuster.
9. by the described hot sound refrigerating machine of claim 1, it is characterized in that, described sound wave primary feedback regulating loop is connected between acoustic waveguide tube (2) harmony absorber (9) the import acoustic waveguide tube of loudspeaker outlet, sound wave time feedback regulation loop is connected between thermal acoustic regenerator (4) and the hot acoustic resonance pipe (7), and the inferior feedback regulation loop of sound wave is one the tunnel, two-way or multichannel.
10. by the described hot sound refrigerating machine of claim 3, it is characterized in that, described thermal acoustic regenerator (4) and the coaxial placement of hot acoustic resonance pipe (7), the sound wave feedback regulation loop of bypass is opened one, two or more aperture on the common wall of thermal acoustic regenerator (4) and hot acoustic resonance pipe (7), or its common wall is adopted or be made into porous wall.
11. by the described hot sound refrigerating machine of claim 1, it is characterized in that, sound absorption device (9) and sound wave main feedback loop are substituted by a microphone, and described microphone is electromagnetic viscosimeter formula microphone, reciprocating-piston microphone, compressor valve plate group, magnetic valve group or rotary valve group.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 95106913 CN1086801C (en) | 1995-06-06 | 1995-06-06 | Thermoacoustic refrigerator |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 95106913 CN1086801C (en) | 1995-06-06 | 1995-06-06 | Thermoacoustic refrigerator |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1137631A CN1137631A (en) | 1996-12-11 |
| CN1086801C true CN1086801C (en) | 2002-06-26 |
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ID=5076115
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 95106913 Expired - Fee Related CN1086801C (en) | 1995-06-06 | 1995-06-06 | Thermoacoustic refrigerator |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN1086801C (en) |
Families Citing this family (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6792764B2 (en) * | 2002-04-10 | 2004-09-21 | The Penn State Research Foundation | Compliant enclosure for thermoacoustic device |
| CN100340825C (en) * | 2004-09-03 | 2007-10-03 | 中国科学院理化技术研究所 | High pressure ratio thermoacoustic drive refrigerating system using elastic diaphragm |
| CN100344920C (en) * | 2004-11-24 | 2007-10-24 | 中国科学院理化技术研究所 | Pressurizer of refrigerator driven by thermoacoustic engine |
| CN1818512B (en) * | 2006-03-14 | 2010-04-14 | 中国科学院理化技术研究所 | Device for eliminating straight flow of two-way air inlet pulsing pipe refrigerator |
| CN102042846B (en) * | 2009-10-12 | 2012-07-25 | 中国科学院理化技术研究所 | Thermo-acoustic process testing system and testing method |
| GB2514830B (en) * | 2013-06-06 | 2016-04-06 | Isis Innovation | Pulse tube cooler |
| CN107394306A (en) * | 2017-06-29 | 2017-11-24 | 深圳市沃特玛电池有限公司 | A kind of electrokinetic cell packs cooling system |
-
1995
- 1995-06-06 CN CN 95106913 patent/CN1086801C/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| CN1137631A (en) | 1996-12-11 |
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