CN100593678C - Tandem type thermoacoustic system - Google Patents
Tandem type thermoacoustic system Download PDFInfo
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- CN100593678C CN100593678C CN200610171654A CN200610171654A CN100593678C CN 100593678 C CN100593678 C CN 100593678C CN 200610171654 A CN200610171654 A CN 200610171654A CN 200610171654 A CN200610171654 A CN 200610171654A CN 100593678 C CN100593678 C CN 100593678C
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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
- F25B2309/1405—Pulse-tube cycles with travelling waves
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Abstract
The invention provides a tandem thermoacoustic system, which comprises at least two stages of thermoacoustic devices which are mutually connected in series; the first stage thermoacoustic device comprises: one or at least two lambda/2 acoustic resonators connected in parallel with each other; λ is the acoustic wavelength; and a standing wave type thermoacoustic engine installed in the standing wave region in the resonant pipe of each lambda/2 acoustic resonator; the traveling-mode thermoacoustic engine is arranged in a high-impedance traveling wave region in each lambda/2 acoustic resonator resonance tube, and the temperature gradient of the traveling-mode thermoacoustic engine is the same as that of the standing-mode thermoacoustic engine; the last-stage thermoacoustic device includes: one or at least two lambda/2 acoustic resonators connected in parallel with each other; λ is the acoustic wavelength; and a traveling-wave type thermoacoustic refrigerator or an acoustoelectric transducer which is arranged in the traveling-wave region in the resonance tube of each lambda/2 acoustic resonator, wherein the temperature gradient of the traveling-wave type thermoacoustic refrigerator is opposite to that of the standing-wave type thermoacoustic engine of the first-stage thermoacoustic device.
Description
Invention field
The present invention relates generally to a kind of thermoacoustic system, particularly a kind of tandem type thermoacoustic system that drives energy converters such as hot sound refrigerating machine or the generating of heat sound with thermoacoustic engine.
Background technology
The hot machine of heat sound (comprising thermoacoustic engine and hot sound refrigerating machine and heat sound heat pump) has fundamentally been eliminated moving component, environment for use close friend's natural medium, and can effectively utilize low grade heat energy, thereby demonstrate important application prospects at aspects such as space technology, natural gas liquefaction and environmental protection and Refrigeration Engineerings.But the raising of heat sound conversion efficiency is restriction heat hot machine through engineering approaches of sound and business-like core technology problem always, is to solve efficiency, the hot machine of heat sound from initial standing wave type, travelling-wave type develop into have with the efficiency of internal combustion engine compare favourably compound.The hot machine of standing wave type heat sound is because depend on can not the work of backheating sound transfer process, and the raising of its efficient is restricted.The standing wave hot sound refrigerating machine only is 0.6 in the Energy Efficiency Ratio (COP) of family expenses refrigerator warm area; The thermal efficiency of standing wave thermoacoustic engine also is no more than 20% usually.The simple annular ring travelling-wave type heat hot machine of sound causes serious viscosity loss and the heat loss of shuttling back and forth because the loop acoustic impedance is low, and actual efficiency is also very low.Though moving standing wave composite type heat acoustic Stirling engine can reach 30% the thermal efficiency,, need take the means of extra effective inhibition acoustic streaming because there is the loss of lucky (Gedeon) sound direct current in loop.In the patent No. is 6,658, (G.W.Swift.Cascaded thermoacoustic devices.U.S.Patent No.6 in 862 the United States Patent (USP), 658,862,2003.), put down in writing the hot machine of a kind of moving standing wave cascade connection type heat sound, its structure only limits to arrange standing wave thermoacoustic engine and travelling-wave type thermoacoustic engine in single half-wavelength acoustic resonator, but its high impedance Hang Bo district is too narrow usually, cascade progression is very limited, and the progression under high frequency (greater than 300Hz) vibration situation is no more than secondary usually.
Summary of the invention
The objective of the invention is to overcome the defective of above-mentioned prior art, promptly can avoid circulating loss, can realize the conversion of efficient heat sound again, be beneficial to the integrated tandem type thermoacoustic system of thermoacoustic system thereby provide a kind of.
Tandem type thermoacoustic system provided by the present invention, this system comprises the acoustic device of two levels of thermal at least of mutual polyphone;
Described first order thermoacoustic devices comprises:
One or at least two λ parallel with one another/2 acoustic resonator; λ is a wave length of sound; With
Be loaded on a standing wave type thermoacoustic engine in each λ/2 acoustic resonator resonatron standing internal wave districts; Be loaded on the travelling-wave type thermoacoustic engine in high impedance Hang Bo district in each λ/2 acoustic resonator resonatrons, described travelling-wave type thermoacoustic engine thermograde is identical with the thermograde of described standing wave type thermoacoustic engine;
Described afterbody thermoacoustic devices comprises:
One or at least two λ parallel with one another/2 acoustic resonator; λ is a wave length of sound; With
Be loaded on the travelling-wave type hot sound refrigerating machine or the acoustic-electrical transducer in the expert ripple of each λ/2 acoustic resonator resonatrons district, the thermograde of described travelling-wave type hot sound refrigerating machine is opposite with the thermograde of the standing wave type thermoacoustic engine of described first order thermoacoustic devices.
Tandem type thermoacoustic system provided by the present invention, the intergrade thermoacoustic devices that also can further comprise between first order thermoacoustic devices and afterbody thermoacoustic devices and contact with it;
Described intergrade thermoacoustic devices comprises:
One or at least two λ parallel with one another/2 acoustic resonator; λ is a wave length of sound; With
Be loaded on the travelling-wave type thermoacoustic engine in each λ/2 acoustic resonator resonatron high impedance Hang Bo districts, described travelling-wave type thermoacoustic engine thermograde is identical with the thermograde of the standing wave type thermoacoustic engine of described first order thermoacoustic devices.
The resonatron of described λ/2 acoustic resonator is provided with and is attached thereto logical hollow and annular pipe; The plane at described hollow and annular pipe place is perpendicular to the resonatron of described λ/2 acoustic resonator; The connection intersection point that described hollow and annular pipe is connected with the resonatron of described λ/2 acoustic resonator and the best of described λ/2 acoustic resonator listen between the point of articulation distance to be less than or equal to 1/8 λ, and satisfy formula p
J/ U
J=ρ a/Acot (2 π L/ λ), wherein p
JFor described hollow and annular pipe is communicated with the acoustic pressure of intersection point, U with the resonatron of described λ/2 acoustic resonator
JFor being communicated with the volume flow speed of intersection point place work medium in the resonatron of described λ/2 acoustic resonator, ρ is the averag density of the interior work of the resonatron medium of described λ/2 acoustic resonator, a is the velocity of sound of the interior work of the resonatron medium of described λ/2 acoustic resonator, A is the cross-sectional area of hollow and annular pipe, and L is the length of hollow and annular pipe; The best point of articulation of listening is meant that acoustic pressure is zero point with the hunting speed phase difference in the resonatron.
Described hollow and annular pipe be shaped as circle, ellipse or rectangle closed-loop path loop pipe.
The resonatron of described λ/2 acoustic resonator is 2-4 with the caliber of described hollow and annular pipe ratio, and described hollow and annular length of tube is 8-20 with the ratio of described hollow and annular caliber;
The end of the resonatron of the initiating terminal of the resonatron of the λ of described first order thermoacoustic devices/2 acoustic resonator or the λ of afterbody thermoacoustic devices/2 acoustic resonator is the opening shape, and resonator or mobile piston perhaps are installed.
The resonatron two ends of the λ of described intergrade thermoacoustic devices/2 acoustic resonator are connected with resonator respectively, promptly have the dumbbell type structure.
Described resonator is hollow ball shape or cylindrical cavity.
Industry technical staff knows, the travelling-wave type thermoacoustic engine generally by cooler, heater and be located at described cooler and heater in the middle of regenerator form.The travelling-wave type hot sound refrigerating machine generally is made up of cryogenic heat exchanger, room temperature heat exchanger and the regenerator between two heat exchangers.
Among the present invention, the center of the regenerator in the described travelling-wave type thermoacoustic engine and the λ of this travelling-wave type thermoacoustic engine/2 acoustic resonator are best listens the distance between the point of articulation to be less than or equal to 1/8 λ.
Among the present invention, the center of the regenerator in the described travelling-wave type hot sound refrigerating machine and the λ of this travelling-wave type hot sound refrigerating machine/2 acoustic resonator are best listens the distance between the point of articulation to be less than or equal to 1/8 λ.
The regenerator of described travelling-wave type thermoacoustic engine and described travelling-wave type hot sound refrigerating machine is a porous road structure, and the hydraulic radius in each duct is 0.1-0.5 a times of medium vibration heat leak layer.
Described standing wave type thermoacoustic engine comprises cooler, heater and is positioned at described cooler and the thermoacoustic system of heater centre that it is 0.025 λ-0.3 λ that the best of the center of described thermoacoustic system and λ/2 acoustic resonator is listened the distance between the point of articulation.
Described thermoacoustic system is that plate stack structure or woven wire are formed, and the 1-2 that its microchannel hydraulic radius is the heat leak layer doubly.
The work medium of described λ/2 acoustic resonator is nitrogen, helium, carbon dioxide, argon gas, hydrogen or is the mist of above-mentioned two or more gas compositions.
The resonatron cross section of described λ/2 acoustic resonator is circular or square; Its tube wall is made with closely knit and firm material, the smooth interior surfaces of tube wall and do not have fine slit; The ratio of resonatron length and circular section internal diameter or the square section length of side is in 10～50 scopes, and the length of resonatron is 1～1.25 times of scope of half-wavelength.
Described tandem type thermoacoustic system, the sound merit produces at the thermoacoustic engine of standing wave mechanism works at first, go through travelling-wave type thermoacoustic engines at different levels and amplification step by step successively after propagate, consume until transducing unit such as afterbody travelling-wave type hot sound refrigerating machine or acoustic-electrical transducers.
Described tandem type thermoacoustic system, its structure belongs to linear pattern and arranges, avoided the appearance of Gedeon sound direct current like this, thereby can make full use of the near traveling wave phase region of a plurality of high impedances, more sound merit is carried out the conversion of heat energy and acoustic energy with the form that circulates near Stirling (Stirling) in the regenerator of follow-up tandem, thereby has the heat sound conversion efficiency that can reach the highest in theory.
Described high impedance Hang Bo district is meant the zone in the acoustic pressure and the positive and negative 45 degree scopes of hunting speed phase difference in the resonatron.
The implication of collaborative work before and after having between the described travelling-wave type heat sound machine at different levels, listen the point of articulation because only there is a best in the half-wavelength acoustic resonator, near the best Hang Bo district of the point of articulation of listening only accounts for 2.5% of wavelength usually, for satisfying the heat insulation of starting between level and the refrigeration-grade for hot, the hot buffer distance that needs about 1% wavelength, so tandem type thermoacoustic system is at least the long resonator system of all-wave, this in theory thermoacoustic system can the infinite stages tandem;
The loop structure of described prolongation high resistance regions, shown in Fig. 7 a, the resonatron of loop and λ/2 acoustic resonator is arranged vertically, such structure can not cause the sound circulation in the resonatron, the connection intersection point that described hollow and annular pipe is connected with the resonatron of described λ/2 acoustic resonator and the best of described λ/2 acoustic resonator listen between the point of articulation distance to be less than or equal to 1/8 λ, require the cross-sectional area A of hollow and annular pipe and hollow and annular length of tube L must satisfy following acoustic impedance relation (concrete reason is referring to the elaboration partly of following operation principle) simultaneously:
p
J/U
J＝ρa/Acot(2πL/λ) (1)
P in the formula
JFor described hollow and annular pipe is communicated with the acoustic pressure of intersection point, U with the resonatron of described λ/2 acoustic resonator
JFor being communicated with the volume flow speed of intersection point place work medium in the resonatron of described λ/2 acoustic resonator;
The present invention is according to the understanding to actual enclosure space sound field characteristic and modulation mechanism thereof, the rule of binding member acoustic impedance condition coupling, viewpoint from fluctuation, create the acoustical area that is beneficial to the conversion of high-efficiency thermal sound, and pass through plural serial stage, the sound merit is amplified in communication process layer by layer, thereby is implemented in the bigger sound merit of output on the high efficiency level.
Compared with prior art, tandem type thermoacoustic system provided by the present invention, key is to utilize the propagation law of sound wave to modulate high impedance traveling-wave phase district, and guarantees the realization of expection sound field from the acoustic construction design.The loop structure of local prolongation high resistance regions is more compact, succinct than the LC method, flexible.
For further specifying the reasonability of structural design of the present invention, also further specify the principle that when carrying out this structural design, will follow simultaneously, below make an explanation from operation principle.
Usually the self-oscillation of heat sound is with fundamental frequency starting of oscillation (system energy loss minimum this moment), for under fundamental vibration, realizing the sound field condition of tandem thermoacoustic system, to adopt the long acoustic resonator of all all-waves as shown in Figure 1 is example, form by two sections elongated acoustic resonance pipes and three resonators, two end resonators also can adopt the mode of opening or mobile piston, and middle resonator can guarantee that system is by the fundamental frequency exciting.According to the interference theory that sound wave is propagated, the sound field characteristic of this resonator is as follows:
p
1＝[p
sa?cos?k′x-ip
ta?sin?k′x]e
iωt
p
sa＝p
ia+p
ra p
ta＝p
ia-p
ra
Wherein: k '=k-i α k=ω/c
0K ' wave vector, Acoustic Boundary Conditions decision wave vector; The α attenuation coefficient.
As seen actual sealing sound field is to be composited p in the formula by standing wave and two kinds of components of row ripple
SaAnd p
TaThe complex amplitude of representing standing wave composition and row wave component respectively.Fig. 2 is that the waveform space of base frequency oscillation distributes in the long tandem acoustic resonator of a kind of all-wave of right of this patent institute demand, near as can be seen from the figure best two the local high impedance areas of the existence of the point of articulation of listening, and fluctuation acoustic pressure vector that should the zone and the phase difference between the velocity of wave motion vector connect near traveling wave, the suitable regenerator unit of arranging the conversion of efficient heat sound, the gas micelle experiences similar Stirling microcirculation in regenerator, therefore have very high conversion efficiency.
The high frequency heat sound system can reduce the size of whole thermoacoustic devices because wavelength is short, shortens but often local high impedance areas is also corresponding, does not have enough locus to arrange hot sound component section.The present invention proposes a kind of high impedance at existing λ/2 acoustic resonator resonatrons and is provided with the method for logical hollow and annular pipe as the acoustics loop that be attached thereto, design the purpose that reaches prolongation λ/2 acoustic resonator resonatron high resistance regions by rational hollow and annular pipe acoustic impedance, shown in Fig. 7 a.Described hollow and annular pipe is communicated with the acoustic pressure note of intersection point and is p with the resonatron of described λ/2 acoustic resonator
J, the volume flow speed note that is communicated with work medium in intersection point place in the resonatron of described λ/2 acoustic resonator is U
J, suppose that the volume flow speed of the interior work of the resonatron medium of described λ/2 acoustic resonator is-U originally
J, how the rational acoustic construction of bypass makes it to become+U through behind the by-pass port
J, high resistance regions can effectively be prolonged like that.Be the way that adopts LC (phonoreception-acoustic capacitance) acoustic construction at present, but the LC proportion is bigger usually, so not only influences the compactedness of system but also can increase the difficulty of whole thermoacoustic system starting of oscillation.This patent proposes the structure that a kind of new loop bypass is regulated for this reason.By analysis to sound field in the hollow and annular pipe, shown in Fig. 7 b, the actual acoustic resonance pipe that is equivalent to a both ends open of whole hollow and annular pipe, two ends have reciprocal velocity perturbation all the time, if in one bifurcations volume flow speed be+U
J, along the loop circumferentially deploying, another bifurcations must be-U
J, but because this bifurcations also is communicated with the main line, for the main line, be still+U
JSo main line volume flow speed has become+U through the fork in the road
JThis inevitable requirement loop satisfies certain acoustic impedance condition, promptly shown in the formula (1).
More than explanation the invention has the advantages that:
1. simple in structure, be easy to integratedly, can on high efficiency level, realize higher power output (or refrigeration);
2. the loop bypass measure that prolongs high resistance regions is succinctly feasible.Innovative point of the present invention is to break through traditional hot sound system mentality of designing, the ingenious sound wave propagation law that utilizes, and, guarantee the modulation (comprising prolongation) of the capable wave sound of local high impedance field with compact more novel acoustic construction by analysis to the sound field regularity of distribution and impedance matching feature.This is a kind of hot machine of travelling-wave type heat sound of being avoided the loss of lucky sound direct current, is different from the capable ripple machine of the annular ring structure of present thermo-acoustic technology fully.
Description of drawings
Fig. 1 is the long linear pattern tandem of four a kinds of all-waves thermoacoustics resonator;
Fig. 2 distributes for a kind of waveform space that is full of the long tandem acoustic resonator of the all-wave base frequency oscillation of 3MPa nitrogen;
Fig. 3 drives the device schematic diagram of hot sound refrigerating machine for the long linear pattern tandem of all-wave thermoacoustic engine;
Fig. 4 is the device schematic diagram that the long U type of a kind of all-wave thermoacoustic engine drives hot sound refrigerating machine;
Fig. 5 drives the thermoacoustic refrigeration device schematic diagram for the integrated tandem heat of a kind of connection in series-parallel mixed type;
Fig. 6 drives the thermoacoustic refrigeration device schematic diagram for the integrated dual wavelength tandem heat of a kind of tandem type (annular);
Fig. 7 a is a kind of hollow and annular pipe of effective prolongation high impedance areas;
Fig. 7 b is the sound field analysis chart of the hollow and annular pipe of prolongation high resistance regions.
The specific embodiment
The present invention will be further explained below in conjunction with accompanying drawing and explanation:
Present embodiment is the tandem thermoacoustic refrigeration system that is driven a travelling-wave type hot sound refrigerating machine by twin-stage cascade connection type thermoacoustic engine, its structure as shown in Figure 3, two λ/2 acoustic resonator are chained together mutually, the figure mean camber line is acoustic pressure (P
1) distribute along journey, contacting successively along the direction of sound merit propagation is provided with following element: first resonator 1, first resonatron 2, first water cooler 3, first thermoacoustic system 4, primary heater 5, first thermal buffer tube 6, second water cooler 7, first regenerator 8, secondary heater 9, second thermal buffer tube, 10, the first secondary water cooler 11, second resonator 13, second resonatron 14, the 3rd water cooler 15, second regenerator 16, cold head 17, the 3rd thermal buffer tube 18, the second secondary water cooler 19, the 3rd resonator 21.
In above-mentioned each element, the centre distance first resonatron 2 best point of articulation 0.025 λ～0.30 λ that listen of first thermoacoustic system 4; The best of the center of first regenerator 8 and first resonatron 2 listens point of articulation distance to be less than or equal to 1/8 λ, and the center of second regenerator 16 and second resonatron, the 14 best distances of the point of articulation of listening are less than or equal to 1/8 λ;
Regenerator in the present embodiment can adopt porous road structure, and the hydraulic radius of each microchannel is 0.1-0.5 a times of medium vibration heat leak layer; Thermoacoustic system can use the plate stack structure or be made up of woven wire, and wherein, the duct hydraulic radius is 1-2 a times of heat leak layer.
This device is actual to be the long resonator system of an all-wave, polyphone connection successively before and after each parts, promptly by orthoscopic tandem work before and after cascade thermoacoustic engine and the hot sound refrigerating machine, the work medium can use single working gas such as helium, nitrogen, carbon dioxide, argon gas or hydrogen, also can use the mist of their middle two kinds or more of gases.Between the primary heater 5 and first water cooler 3 thermograde surpass the critical-temperature gradient, the sound merit will produce in first thermoacoustic system 4, beginning is each element propagation downstream successively, and in first regenerator 8, obtain amplifying, multiplication factor is the ratio of the absolute temperature of the secondary heater 9 and first water cooler 7 in theory, in second regenerator 16, obtain consumption at last, thereby obtained the cryogenic temperature and the refrigerating capacity of cold head 17.
Above-mentioned critical-temperature gradient branch computing formula is
P in the formula
1Be sound pressure amplitude in the thermoacoustic system, U
1Volume flow speed for the medium vibration of working in the thermoacoustic system; A is a work medium circulation area in the thermoacoustic system; Cp is a work medium specific heat at constant pressure in the thermoacoustic system; ω is the hunting angle frequency.
The waveform space that Fig. 2 has provided the base frequency oscillation when said apparatus adopts 3MPa nitrogen as working media distributes, PAN represents the antinode of acoustic pressure among the figure, the node of VN representation speed, as can be seen from the figure bestly have two local high impedance areas near listening the point of articulation, and acoustic pressure and velocity fluctuation phase difference that should the zone connect near traveling wave.
For effectively prolonging row ripple section length, also can adopt shown in Fig. 7 a perpendicular to resonatron at first regenerator 8 and second regenerator, 16 places and be attached thereto logical hollow and annular pipe, the connection intersection point that described hollow and annular pipe is connected with the resonatron of described λ/2 acoustic resonator and the best of described λ/2 acoustic resonator listen between the point of articulation distance to be less than or equal to 1/8 λ, and satisfy formula p
J/ U
J=ρ a/Acot (2 π L/ λ), wherein p
JFor described hollow and annular pipe is communicated with the acoustic pressure of intersection point, U with the resonatron of described λ/2 acoustic resonator
JFor being communicated with the volume flow speed of intersection point place work medium in the resonatron of described λ/2 acoustic resonator, ρ is the averag density of the interior work of the resonatron medium of described λ/2 acoustic resonator, a is the velocity of sound of the interior work of the resonatron medium of described λ/2 acoustic resonator, A is the cross-sectional area of hollow and annular pipe, and L is the length of hollow and annular pipe; The best point of articulation of listening is meant that acoustic pressure is zero point with the hunting speed phase difference in the resonatron.
The hollow and annular pipe is circular, ellipse or rectangle, the ratio of its length and hollow and annular pipe caliber between 8-20 can, the caliber of hollow and annular pipe is 1/4-1/2 with the ratio of the caliber of resonatron.Numerical simulation shows that two ends and middle acoustic resonance cavity place slightly depart from the acoustic pressure node, this device resonatron length is about 1.2 times of all-wave length, engine thermal efficiency is more than 25%, and the COP that the COP of hot sound refrigerating machine domestic refrigerator warm area and electricity drive the steam compression type refrigeration mode is suitable substantially.This is far above the efficient with the refrigerating plant of sound-driving pass through " major diameter pipe+air reservoir " of warm area heat or " aperture+air reservoir " phase modulation, because the COP of structure can not be above 1 like that.
λ/2 acoustic resonator that present embodiment uses, comprise resonatron and the resonator that lays respectively at the resonatron two ends, wherein resonator can have different sizes, also can have different shapes, as shown in Figure 1, A and figure B are made up of two sections elongated acoustic resonance pipes and three resonators among the figure, can have different sizes between the resonator, resonator also can take different shapes, be the employing spherical cavity resonator as A, can reduce that surface sound dissipates and abrupt change of cross-section loss, B for utilization than the pipe of tubbiness as resonator; C is the open-ended form of border resonatron, and D is the terminal form that adopts mobile piston, is connected resonator in the middle of C and the D and also can adopts sphere.
Present embodiment adopts tandem type thermoacoustic system shown in Figure 4; This system forms U type structure by two λ/2 acoustic resonator polyphone, and setting, position and working method, the course of work of each element are all identical with embodiment 1 in the resonator;
Adopt U type tandem moor, make system's physical length reduce, effective conserve space, simultaneously, because the work medium mostly is nitrogen, helium, carbon dioxide, argon gas, hydrogen or is the mist of above-mentioned two or more gas compositions, far below the acoustic impedance of λ/2 acoustic resonator tube wall stainless steel materials,, just can increase some local viscosity losses so the acoustic resonance pipe of U type elbow part still can be regarded as plane wave propagation.
Present embodiment adopts system architecture shown in Figure 5; First order thermoacoustic devices by three built-in thermoacoustic engines of difference λ/parallel connection of 2 acoustic resonator is stronger drive unit, and then the λ of a built-in hot sound refrigerating machine of tandem/2 acoustic resonator, as second level thermoacoustic devices.The resonatron inside of each λ in the first order thermoacoustic devices/2 acoustic resonator all is provided with a standing wave type thermoacoustic engine and a travelling-wave type thermoacoustic engine, among the figure, first, second, the 3rd standing wave type thermoacoustic engine 34,36,38 insert and put thermoacoustic system by two cold and hot end heat exchangers forms, first, second, the third line undulant fever phonomotor 35,37,39 and travelling-wave type hot sound refrigerating machine 40 insert and put regenerator by two cold and hot end heat exchangers and form, the distance between the best tin point of articulation of the center of the regenerator in each travelling-wave type thermoacoustic engine and the λ of this travelling-wave type thermoacoustic engine/2 acoustic resonator is less than or equal to 1/8 λ; The center of the regenerator in the described travelling-wave type hot sound refrigerating machine and the λ of this travelling-wave type hot sound refrigerating machine/2 acoustic resonator are best listens the distance between the point of articulation to be less than or equal to 1/8 λ, and the thermograde of each standing wave type thermoacoustic engine is identical, the thermograde of each travelling-wave type thermoacoustic engine all thermograde with each standing wave type thermoacoustic engine is identical, and the thermograde of travelling-wave type hot sound refrigerating machine is opposite with the thermograde of each standing wave type thermoacoustic engine;
The sound merit produces with the thermoacoustic effect of standing wave mechanism in first, second, third standing wave type thermoacoustic engine 34,36,38, then in first, second, third travelling-wave type thermoacoustic engine 35,37,39, effectively amplified respectively, then be pooled to and obtain consumption in the travelling-wave type hot sound refrigerating machine 40.This is a kind of long resonator system of all-wave of integrated form, can strengthen the compactedness of real system greatly, and one of shortcoming of current thermoacoustic devices maximum is exactly not compact, and heat sound unit only accounts for resonator system ratio seldom, and the hot acoustic Stirling machine of mixed type is more obvious.
Among Fig. 5 in parallel three independently λ/2 acoustic resonator can not replace by 3 times of thick single λ/2 acoustic resonator of sectional area, reason has two, the one, enlarged-diameter must make radial velocity component and disturbance proportion strengthen, and regenerator cross section temperature distributing disproportionation influences system effectiveness; The 2nd, strengthen the increase that the regenerator diameter can cause the regenerator acoustic capacitance, cause that phase difference departs from traveling-wave phase between local acoustic pressure and speed, in other words, the Hang Bo district can shorten greatly, is unfavorable for that regenerator gives full play to the effect of amplification sound merit.
Present embodiment adopts 4 λ/2 acoustic resonator to be composed in series a toroidal, as shown in Figure 6, and wherein,
Be provided with the 4th standing wave type thermoacoustic engine 42 and fourth line undulant fever phonomotor 43 in the resonatron of the one λ/2 acoustic resonator 41, the 4th standing wave type thermoacoustic engine 42 is positioned at the standing wave district, and the best of centre distance the one λ/2 acoustic resonator of its thermoacoustic system is listened the point of articulation 0.025 λ～0.30 λ; Fourth line undulant fever phonomotor 43 is positioned at the Hang Bo district of a λ/2 acoustic resonator, the λ of the center of its regenerator and this travelling-wave type hot sound refrigerating machine/2 acoustic resonator are best listens the distance between the point of articulation to be less than or equal to 1/8 λ, and the thermograde of fourth line undulant fever phonomotor 43 is identical with the thermograde of the 4th standing wave type thermoacoustic engine 42;
Hang Bo district in second, third λ/2 acoustic resonator 44,46 is provided with the 5th, the 6th travelling-wave type thermoacoustic engine 45,47 respectively, and the position is all identical with fourth line undulant fever phonomotor 43 with thermograde;
Be provided with travelling-wave type hot sound refrigerating machine 49 in the 4th λ/2 acoustic resonator 48; Its position is identical with fourth line undulant fever phonomotor 43, and thermograde is identical opposite with fourth line undulant fever phonomotor 43.
The sound merit produces in the 4th standing wave type thermoacoustic engine 42, is amplified step by step successively in the 4th, the 5th, the 6th travelling-wave type thermoacoustic engine 43,45,47, and at travelling-wave type refrigeration machine 49 internal consumptions, acoustic energy is converted to refrigerating capacity at last.Simultaneously the travelling-wave type hot sound refrigerating machine 49 of the 4th λ/2 acoustic resonator 48 can be used as Cryo Equipments such as the refrigerator that obtains cold, air-conditioning, liquefier and uses (from the cool end heat exchanger of the 4th regenerator 9 as output) according to the difference of purposes, also can be used as heat pump heating and uses (from the cold and hot end heat exchanger of the 4th regenerator 9 as output).This also is a kind of thrifty scheme of practicability, and heat sound nuclear section proportion increases.This device is one 2 wavelength system, just offers the power consumption unit through three exponential increase formulas amplifications after the sound merit produces, and has improved efficiency of energy utilization greatly, can reach 40% relative Carnot efficiency in theory.
On the architecture basics of said apparatus, described travelling-wave type hot sound refrigerating machine 49 can also be replaced with acoustic-electrical transducer, thereby acoustic energy is converted to electric energy.
Claims (10)
1, a kind of tandem type thermoacoustic system, this system comprises the acoustic device of two levels of thermal at least of mutual polyphone;
Described first order thermoacoustic devices comprises:
One or at least two λ parallel with one another/2 acoustic resonator; λ is a wave length of sound; With
Be loaded on a standing wave type thermoacoustic engine in each λ/2 acoustic resonator resonatron standing internal wave districts; Be loaded on the travelling-wave type thermoacoustic engine in high impedance Hang Bo district in each λ/2 acoustic resonator resonatrons, described travelling-wave type thermoacoustic engine thermograde is identical with the thermograde of described standing wave type thermoacoustic engine;
Described afterbody thermoacoustic devices comprises:
One or at least two λ parallel with one another/2 acoustic resonator; λ is a wave length of sound; With
Be loaded on the travelling-wave type hot sound refrigerating machine or the acoustic-electrical transducer in the expert ripple of each λ/2 acoustic resonator resonatrons district, the thermograde of described travelling-wave type hot sound refrigerating machine is opposite with the thermograde of the standing wave type thermoacoustic engine of described first order thermoacoustic devices.
2, by the described tandem type thermoacoustic system of claim 1, it is characterized in that the intergrade thermoacoustic devices that also further comprises between first order thermoacoustic devices and afterbody thermoacoustic devices and contact with it;
Described intergrade thermoacoustic devices comprises:
One or at least two λ parallel with one another/2 acoustic resonator; λ is a wave length of sound; With
Be loaded on the travelling-wave type thermoacoustic engine in each λ/2 acoustic resonator resonatron high impedance Hang Bo districts, described travelling-wave type thermoacoustic engine thermograde is identical with the thermograde of the standing wave type thermoacoustic engine of described first order thermoacoustic devices.
3, by claim 1 or 2 described tandem type thermoacoustic systems, it is characterized in that the resonatron of described λ/2 acoustic resonator is provided with and is attached thereto logical hollow and annular pipe; The plane at described hollow and annular pipe place is perpendicular to the resonatron of described λ/2 acoustic resonator; The connection intersection point that described hollow and annular pipe is connected with the resonatron of described λ/2 acoustic resonator and the best of described λ/2 acoustic resonator listen between the point of articulation distance to be less than or equal to 1/8 λ, and satisfy formula p
J/ U
J=ρ a/Acot (2 π L/ λ), wherein p
JFor described hollow and annular pipe is communicated with the acoustic pressure of intersection point, U with the resonatron of described λ/2 acoustic resonator
JFor being communicated with the volume flow speed of intersection point place work medium in the resonatron of described λ/2 acoustic resonator, ρ is the averag density of the interior work of the resonatron medium of described λ/2 acoustic resonator, a is the velocity of sound of the interior work of the resonatron medium of described λ/2 acoustic resonator, A is the cross-sectional area of hollow and annular pipe, and L is the length of hollow and annular pipe; The best point of articulation of listening is meant that acoustic pressure is zero point with the hunting speed phase difference in the resonatron.
4, according to the described tandem type thermoacoustic system of claim 3, it is characterized in that, described hollow and annular pipe be shaped as circle, ellipse or rectangle closed-loop path loop pipe.
According to the described tandem type thermoacoustic system of claim 3, it is characterized in that 5, the resonatron of described λ/2 acoustic resonator is 2-4 with the caliber of described hollow and annular pipe ratio, described hollow and annular length of tube is 8-20 with the ratio of described hollow and annular caliber.
6, according to claim 1 or 2 described tandem type thermoacoustic systems, it is characterized in that the center of the regenerator in the described travelling-wave type thermoacoustic engine and the λ of this travelling-wave type thermoacoustic engine/2 acoustic resonator are best listens the distance between the point of articulation to be less than or equal to 1/8 λ.
7, according to claim 1 or 2 described tandem type thermoacoustic systems, it is characterized in that the center of the regenerator in the described travelling-wave type hot sound refrigerating machine and the λ of this travelling-wave type hot sound refrigerating machine/2 acoustic resonator are best listens the distance between the point of articulation to be less than or equal to 1/8 λ.
8, according to claim 1 or 2 described tandem type thermoacoustic systems, it is characterized in that, described standing wave type thermoacoustic engine comprises cooler, heater and is positioned at described cooler and the thermoacoustic system of heater centre that it is 0.025 λ-0.3 λ that the best of the center of described thermoacoustic system and λ/2 acoustic resonator is listened the distance between the point of articulation.
According to the described tandem type thermoacoustic system of claim 8, it is characterized in that 9, described thermoacoustic system is that plate stack structure or woven wire are formed, the 1-2 that its microchannel hydraulic radius is the heat leak layer doubly.
According to the described tandem type thermoacoustic system of claim 8, it is characterized in that 10, the work medium of described λ/2 acoustic resonator is nitrogen, helium, carbon dioxide, argon gas, hydrogen or is the mist of above-mentioned two or more gas compositions.
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| CN101726133B (en) * | 2009-10-21 | 2011-11-30 | 北京理工大学 | Thermo-acoustic refrigerator device driven by cascade thermo-acoustic engine |
| WO2014043790A1 (en) | 2012-09-19 | 2014-03-27 | Etalim Inc. | Thermoacoustic transducer apparatus including a transmission duct |
| CN103017401B (en) * | 2012-12-12 | 2015-06-03 | 浙江大学 | Acoustic power amplifying device capable of adopting cold energy |
| CN103758657B (en) * | 2014-01-21 | 2015-05-06 | 中国科学院理化技术研究所 | Acoustic resonance type traveling wave thermoacoustic power generation system |
| CN105276855B (en) * | 2015-11-17 | 2018-07-24 | 中国科学院理化技术研究所 | Loop multistage traveling wave thermal driving refrigerating system |
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