CN1673649A - Thermoacoustic driving pulse tube refrigerator - Google Patents
Thermoacoustic driving pulse tube refrigerator Download PDFInfo
- Publication number
- CN1673649A CN1673649A CN 200510064340 CN200510064340A CN1673649A CN 1673649 A CN1673649 A CN 1673649A CN 200510064340 CN200510064340 CN 200510064340 CN 200510064340 A CN200510064340 A CN 200510064340A CN 1673649 A CN1673649 A CN 1673649A
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- pipe
- thermoacoustic
- refrigerating machine
- engine
- pulse tube
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- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims description 17
- 238000005057 refrigeration Methods 0.000 claims description 11
- 239000001307 helium Substances 0.000 claims description 6
- 229910052734 helium Inorganic materials 0.000 claims description 6
- SWQJXJOGLNCZEY-UHFFFAOYSA-N helium atom Chemical compound [He] SWQJXJOGLNCZEY-UHFFFAOYSA-N 0.000 claims description 6
- 239000007789 gas Substances 0.000 claims description 4
- 239000003638 chemical reducing agent Substances 0.000 claims description 2
- 230000010355 oscillation Effects 0.000 description 8
- RYGMFSIKBFXOCR-UHFFFAOYSA-N Copper Chemical compound [Cu] RYGMFSIKBFXOCR-UHFFFAOYSA-N 0.000 description 3
- 229910052802 copper Inorganic materials 0.000 description 3
- 239000010949 copper Substances 0.000 description 3
- 238000007789 sealing Methods 0.000 description 3
- 229910001220 stainless steel Inorganic materials 0.000 description 3
- 239000010935 stainless steel Substances 0.000 description 3
- 210000003462 vein Anatomy 0.000 description 3
- 238000005406 washing Methods 0.000 description 3
- IJGRMHOSHXDMSA-UHFFFAOYSA-N Atomic nitrogen Chemical compound N#N IJGRMHOSHXDMSA-UHFFFAOYSA-N 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 238000011160 research Methods 0.000 description 2
- 230000003321 amplification Effects 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000002474 experimental method Methods 0.000 description 1
- 238000011835 investigation Methods 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 230000007774 longterm Effects 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 229910052757 nitrogen Inorganic materials 0.000 description 1
- 238000003199 nucleic acid amplification method Methods 0.000 description 1
- 238000012546 transfer Methods 0.000 description 1
Images
Classifications
-
- 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
-
- 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
- F25B2309/1403—Pulse-tube cycles with heat input into acoustic driver
-
- 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
-
- 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
- F25B2309/1407—Pulse-tube cycles with pulse tube having in-line geometrical arrangements
-
- 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
- F25B2309/1413—Pulse-tube cycles characterised by performance, geometry or theory
-
- 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
- F25B2309/1424—Pulse tubes with basic schematic including an orifice and a reservoir
- F25B2309/14241—Pulse tubes with basic schematic including an orifice reservoir multiple inlet pulse tube
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Compressor (AREA)
- Devices That Are Associated With Refrigeration Equipment (AREA)
Abstract
The invention relates to a thermoacoustic driving pulse tube refrigerator, which comprises a thermoacoustic engine, a pulse tube refrigerator and a connecting tube for connecting the thermoacoustic engine and the pulse tube refrigerator, wherein the length of the connecting tube is 1/10-1/4 sound wave length. The cross-sectional area of the connecting pipe is smaller than that of an engine runner at the joint of the connecting pipe and the thermoacoustic engine; the shape of the pipe can be a pipe with equal diameter, a long pipe formed by connecting 2 to 4 pipes with different diameters, or a pipe with the diameter continuously changing from a position close to the thermoacoustic engine to a pulse pipe refrigerator. Compared with the prior art, the thermoacoustic driven pulse tube refrigerator provided by the invention has the advantages that the long tube is inserted between the thermoacoustic engine and the pulse tube refrigerator driven by the thermoacoustic driven pulse tube refrigerator, so that the characteristic that the thermoacoustic driven pulse tube refrigerator has no moving part is kept, and the fluctuation amplitude of pressure waves in the engine is increased after the pressure waves pass through the long tube, namely the thermoacoustic driven pulse tube refrigerator provided by the invention has a larger pressure ratio, so that the refrigerating performance is improved.
Description
Technical field
The invention belongs to refrigeration and cryogenic technique field, specifically relate to a kind of thermoacoustic driving pulse pipe refrigerating machine.
Background technology
Pulse tube refrigerating machine is because the moving component under the no low temperature becomes the focus and emphasis in the small-sized Cryo Refrigerator research field over past ten years.Usually, pulse tube refrigerating machine needs the mechanical oilless (oil free) compressor under the room temperature that pressure wave is provided, and this compressor arrangement complexity, the cost height, and restricted the pulse tube refrigerating machine long term reliability.
Thermoacoustic engine be a kind of novel be the device of acoustic energy with thermal power transfer, can need not any moving component and pressure wave is provided.It comes down to a kind of compressor that utilizes heat energy, and is simple in structure and reliability is very high.Along with people's close attention and further investigation, the actual performance of thermoacoustic engine is largely increased in nearly ten years, and the hot merit conversion efficiency of thermoacoustic engine has reached 30% at present.
The thermoacoustic driving pulse pipe refrigerating machine that the coupling of thermoacoustic engine and pulse tube refrigerating machine is obtained in the past is the direct-connected mode of connecting pipe of having only several centimetre lengths that adopts between the two.This thermoacoustic driving pulse pipe refrigerating machine can form the Cryo Refrigerator of complete movement-less part, has incomparable advantage aspect cost and the reliability.The obtainable minimum temperature of this coupled system is 68.8K at present, has broken through liquid nitrogen temperature.Limit this coupled system and obtain more that the bottleneck of low temperature is the pressure ratio lower (pressure ratio is defined as the maximum of surge pressure divided by minimum of a value) that common thermoacoustic engine can provide.Adopt helium working medium generally can only obtain pressure ratio about 1.2, even and if this pressure ratio also be not easy to realize.
In order to obtain lower cryogenic temperature and bigger refrigerating capacity, high pressure ratio is one of emphasis of research at present promptly to need the sound-driving pulse tube refrigerating machine of feasible heat to obtain more.
Summary of the invention
The pressure ratio of thermoacoustic driving pulse pipe refrigerating machine that the objective of the invention is to overcome prior art is lower, thereby by increasing the length of connecting pipe, provides a kind of thermoacoustic driving pulse pipe refrigerating machine that has than high pressure ratio, higher refrigeration performance.
The objective of the invention is to realize by the following technical solutions:
Thermoacoustic driving pulse pipe refrigerating machine provided by the invention, comprise a thermoacoustic engine and a pulse tube refrigerating machine, between described thermoacoustic engine and pulse tube refrigerating machine, connect pipe, the length of described connection pipe is between 1/10 sound wave length is long to 1/4 sound wave, in this scope, can select different optimum lengths according to refrigeration machine impedance operator difference.
For example: with the helium is working medium to the optimum length of described connection pipe and different according to Working medium gas, operating temperature and operating frequency different, 69 hertz of operating frequencies, and temperature 300K, the optimum length that then connects pipe is between 1.5～7.4 meters.
The cross-sectional area of described connection pipe is less than long-pending with the engine flow channel cross-section of thermoacoustic engine joint, and its diameter is 1 millimeter～5 centimetres.
Described connection pipe comprises three kinds of shapes:
(1) equal diameter pipe;
(2) long tube that is formed by connecting by the pipe of 2 to 4 kinds of different-diameters;
(3) near thermoacoustic engine to pulse tube refrigerating machine place diameter continually varying reducer pipe.
Described thermoacoustic engine is traveling wave thermoacoustic engine or standing wave thermoacoustic engine.
Described pulse tube refrigerating machine is the single-stage pulse tube refrigerating machine of straight line, U type layout or coaxial arrangement, perhaps is the multi-stage pulse tube refrigeration machine of straight line, U type layout or coaxial arrangement.
One end of described connection pipe can be connected in any position on the thermoacoustic engine, and typical position is: for the standing wave thermoacoustic engine, generally be the joint that is connected in the resonatron and the water cooler of thermoacoustic engine; For traveling wave thermoacoustic engine, generally be the joint of main water cooler with the feedback pipe of thermoacoustic engine.
When prior art is used thermoacoustic engine driving pulse pipe refrigeration machine, it is conventionally believed that connecting pipe is short more good more, generally have only several centimetres, in the hope of reducing flow losses.By comparison, thermoacoustic driving pulse pipe refrigerating machine provided by the invention, key is to have inserted a long tube between the pulse tube refrigerating machine of thermoacoustic engine and its driving, when having kept thermoacoustic engine driving pulse pipe refrigeration machine not have the characteristics of any moving component, make in-engine pressure wave become big through fluctuation amplitude behind this long tube, be that thermoacoustic driving pulse pipe refrigerating machine provided by the invention has than high pressure ratio, thereby its refrigeration performance is improved.
For further specify that the present invention proposes in the principle that is connected long tube lifting pressure ratio between thermoacoustic engine and the pulse tube refrigerating machine, simultaneously also further specify required some principles of following when choosing tube length, will make an explanation to its supercharging principle theoretically below.
When sound wave transmitted in can the harmony wavelength comparable pipeline of a length, it had typical distribution formula parameter characteristic.Give certain pressure wave as openend a at end opening one by one, pipeline end sealing, long 1/4 wavelength, because the other end b of pipeline sealing, will form standing-wave sound field in the time of in the pipeline, the amplitude of pressure wave changes along pipe range, can occur the maximum of amplitude on the sealing interface.The distribution of pressure wave amplitude when the blind end at pipeline is connected to the acoustics load, equally also can occur, adopt linear heat sound theory to analyze here.Linear heat sound theory is the common tool that is used for analyzing little amplitude sound field in the thermoacoustics, and formula (1) and formula (2) are its two equations that are used for describing sound field.
ω wherein, A, γ, P
0, ρ is that angular frequency, flow channel cross-section are long-pending respectively, specific heat ratio, average pressure and gas density.f
μ, f
kBe and relevant functions such as runner geometric parameter, gas rerum natura, operating frequency.
The surge pressure at openend a place
With fluctuation volume flow amplitude
The surge pressure amplitude at blind end b place
With fluctuation volume flow amplitude
So (1) (2) formula is found the solution and can be obtained following relational expression:
Openend a is the input of pressure wave, and blind end b is connected to the pulse tube refrigerating machine load.If the surge pressure at a place
Known, the impedance of pulse tube refrigerating machine
Known, pressure oscillation magnification ratio r is defined as so
Typically, select 10mm internal diameter copper tube for use, as Z=(3.9-3.4i) * 10
8The time, adopt helium working medium, average pressure 2.0Mpa, temperature 300K, in the pressure oscillation of openend input 0.1MPa, 90Hz, Fig. 1 shows the situation of change of impedance inlet pressure fluctuation amplitude with different pipe ranges, can see the pressure oscillation amplification effect significantly, especially when pipe range was 2.65 meters, the pressure oscillation amplitude of load end can be increased to about 10 times
Description of drawings
Fig. 1 is the situation of change of impedance inlet pressure fluctuation amplitude with different pipe ranges;
Fig. 2 is the schematic diagram that the traveling wave thermoacoustic engine of embodiment 1 drives single-stage linear pattern pulse tube refrigerating machine;
Fig. 3 is the schematic diagram that the standing wave thermoacoustic engine of embodiment 2 drives U type two-stage pulse tube refrigerating machine;
Wherein: the A thermoacoustic engine, B connects long tube, C pulse tube refrigerating machine, 1 main water cooler, 2 regenerators, 3 heaters, 4 thermal buffer tubes, 5 secondary water coolers, 6 feedback pipes, 7 taper resonatrons; 8 hot chambeies, 9 heaters, 10 plates are folded, 11 water coolers, the resonator that 12 equal diameter pipes and cavity are formed, 13 water coolers, 14 regenerators, 15 cold heads, 16 pulse tubes, 17 little ports valves, 18 air reservoirs, 19 two-way valves, 20 secondary regenerators, 21 one-level air reservoirs, 22 one-level inertance tubes, 23 one-level pulse tubes, 24 secondary air reservoirs, 25 secondary inertance tubes, 26 secondary vein washing pipes, 27 water coolers, 28 one-level regenerators.
The specific embodiment
Describe the thermoacoustic driving pulse pipe refrigerating machine that has than high pressure ratio, higher refrigeration performance provided by the invention in detail below in conjunction with Fig. 2 and Fig. 3.
Adopt constructional device as shown in Figure 2, use traveling wave thermoacoustic engine to drive single-stage linear pattern pulse tube refrigerating machine, wherein A is a traveling wave thermoacoustic engine, mainly comprises main water cooler 1, regenerator 2, heater 3, thermal buffer tube 4, secondary water cooler 5, feedback pipe 6, taper resonatron 7; C is a single-stage linear pattern pulse tube refrigerating machine, mainly comprises water cooler 13, regenerator 14, cold head 15, pulse tube 16, aperture valve 17, air reservoir 18, two-way valve 19; The two connects by connecting long tube B, and described connection pipe is connected in the joint of main water cooler with the feedback pipe of traveling wave thermoacoustic engine.
The diameter of the feedback pipe of this traveling wave thermoacoustic engine is 80mm, and backfeed loop is about 2m, taper resonatron length 4.5m.Adopt helium as working medium, average pressure 2.46MPa, operating frequency is 69Hz (the long 14.8m of being of the corresponding sound wave of this frequency), and single-stage linear pattern pulse tube refrigerating machine regenerator is of a size of the 15mm internal diameter, and length 48mm fills 400 order stainless steel cloths; Pulse tube is of a size of 6mm internal diameter, length 77mm.The isodiametric red copper pipe that adopts 8mm is as connecting long tube, and its length is 2.8m.Experimental result shows, from the amplitude of thermoacoustic engine be the pressure oscillation of 0.128MPa (being that pressure ratio is 1.11) to be amplified to amplitude be that the pressure oscillation of 0.34MPa (being that pressure ratio is 1.32) enters pulse tube refrigerating machine, drive this refrigeration machine and obtain the 65.7K lowest temperature.
Adopt constructional device as shown in Figure 3, use the standing wave thermoacoustic engine to drive U type two-stage pulse tube refrigerating machine, wherein A is the standing wave thermoacoustic engine, mainly comprises hot chamber 8, heater 9, and plate folds 10, water cooler 11, the resonator 12 that equal diameter pipe and cavity are formed; C is a U type two-stage pulse tube refrigerating machine, mainly comprises secondary regenerator 20, one-level air reservoir 21, one-level inertance tube 22, one-level pulse tube 23, secondary air reservoir 24, secondary inertance tube 25, secondary vein washing pipe 26, water cooler 27, one-level regenerator 28; The two connects by connecting long tube B, and described connection pipe is connected in the joint of the resonatron and the water cooler of standing wave thermoacoustic engine.
The heater of this standing wave thermoacoustic engine, plate superimposition water cooler internal diameter are 80mm, and the resonatron internal diameter is 50mm, and length 3.3m adopts helium as working medium, average pressure 3.0MPa, and operating frequency is 88Hz (the long 11.6m of being of the corresponding sound wave of this frequency).The one-level regenerator is of a size of the 25mm internal diameter in the two-stage pulse tube refrigerating machine, and length 55mm fills 400 order stainless steel cloths; The one-level pulse tube is of a size of 10mm internal diameter, length 100mm; The secondary regenerator is of a size of the 10mm internal diameter, and length 35mm fills 500 order stainless steel cloths; The secondary vein washing pipe is of a size of 6mm internal diameter, length 70mm.The isodiametric red copper pipe that adopts internal diameter 8mm is as connecting long tube, its length is 2.6m, be that the pressure oscillation of 0.073MPa (being that pressure ratio is 1.05) is amplified to the pressure oscillation that amplitude is 0.19MPa (being that pressure ratio is 1.14) and enters the two-stage pulse tube refrigerating machine from the amplitude of standing wave thermoacoustic engine in the experiment, drive this refrigeration machine and obtain the 60K lowest temperature.
Claims (9)
1, a kind of thermoacoustic driving pulse pipe refrigerating machine, comprise a thermoacoustic engine and a pulse tube refrigerating machine, connect pipe between described thermoacoustic engine and pulse tube refrigerating machine, it is characterized in that: the length of described connection pipe is between 1/10 sound wave length is long to 1/4 sound wave.
2, thermoacoustic driving pulse pipe refrigerating machine as claimed in claim 1 is characterized in that: when Working medium gas is a helium, operating frequency is 69 hertz, and when operating temperature was 300K, the length of described connection pipe was 1.5～7.4 meters.
3, thermoacoustic driving pulse pipe refrigerating machine as claimed in claim 1 is characterized in that: the cross-sectional area of described connection pipe is than long-pending little with the engine flow channel cross-section of thermoacoustic engine joint.
4, thermoacoustic driving pulse pipe refrigerating machine as claimed in claim 1 is characterized in that: the diameter of described connection pipe is 1 millimeter～5 centimetres.
5, thermoacoustic driving pulse pipe refrigerating machine as claimed in claim 1 is characterized in that: described connection pipe comprises three kinds of shapes:
(1) equal diameter pipe;
(2) long tube that has the pipe of 2 to 4 kinds of different-diameters to be formed by connecting;
(3) near thermoacoustic engine to pulse tube refrigerating machine place diameter continually varying reducer pipe.
6, thermoacoustic driving pulse pipe refrigerating machine as claimed in claim 1 is characterized in that: described thermoacoustic engine is traveling wave thermoacoustic engine or standing wave thermoacoustic engine.
7, thermoacoustic driving pulse pipe refrigerating machine as claimed in claim 1, it is characterized in that: described pulse tube refrigerating machine is that straight line, U type are arranged or coaxial arrangement single-stage pulse tube refrigerating machine, perhaps is that straight line, U type are arranged or coaxial arrangement multi-stage pulse tube refrigeration machine.
8, thermoacoustic driving pulse pipe refrigerating machine as claimed in claim 1 is characterized in that: the link position of described connection pipe and standing wave thermoacoustic engine is the joint of the resonatron and the water cooler of engine.
9, thermoacoustic driving pulse pipe refrigerating machine as claimed in claim 1 is characterized in that: the link position of described connection pipe and traveling wave thermoacoustic engine is the joint of main water cooler with the feedback pipe of engine.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB2005100643401A CN100572987C (en) | 2005-04-14 | 2005-04-14 | Thermoacoustic driving pulse tube refrigerator |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB2005100643401A CN100572987C (en) | 2005-04-14 | 2005-04-14 | Thermoacoustic driving pulse tube refrigerator |
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| Publication Number | Publication Date |
|---|---|
| CN1673649A true CN1673649A (en) | 2005-09-28 |
| CN100572987C CN100572987C (en) | 2009-12-23 |
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| Application Number | Title | Priority Date | Filing Date |
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| CNB2005100643401A Expired - Fee Related CN100572987C (en) | 2005-04-14 | 2005-04-14 | Thermoacoustic driving pulse tube refrigerator |
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Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2007053809A2 (en) | 2005-10-31 | 2007-05-10 | Clever Fellows Innovation Consortium, Inc. | Acoustic cooling device with coldhead and resonant driver separated |
| CN100357676C (en) * | 2006-01-17 | 2007-12-26 | 浙江大学 | Corrugated pipe connecting device of conpled heat sound motor and pulse pipe refrigerator |
| CN100427848C (en) * | 2006-01-17 | 2008-10-22 | 浙江大学 | Heat sound driving pulse pipe refrigeration machine system |
| CN100565039C (en) * | 2007-04-03 | 2009-12-02 | 中国科学院理化技术研究所 | Coupling device for thermoacoustic engine and refrigerator driven by thermoacoustic engine |
| CN101275793B (en) * | 2007-03-27 | 2010-05-19 | 中国科学院理化技术研究所 | Thermo-acoustic magnetic refrigeration low-temperature system |
| CN101566405B (en) * | 2008-04-22 | 2011-05-11 | 中国科学院理化技术研究所 | Heat-driven thermoacoustic refrigerator device with traveling and standing wave type sound field |
| CN107609276A (en) * | 2017-09-15 | 2018-01-19 | 湖南科技大学 | Axial symmetry Thermoacoustic resonator Optimization Design based on pressure amplification factor |
| CN107633130A (en) * | 2017-09-15 | 2018-01-26 | 湖南科技大学 | Axial symmetry Thermoacoustic resonator performance estimating method based on pressure at two ends amplitude ratio |
Family Cites Families (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP3623659B2 (en) * | 1998-06-12 | 2005-02-23 | エア・ウォーター株式会社 | Cryopump |
| JP3814418B2 (en) * | 1998-06-19 | 2006-08-30 | アイシン精機株式会社 | Regenerator material, regenerator and regenerative refrigerator using these |
| CN1201127C (en) * | 2000-09-15 | 2005-05-11 | Lg电子株式会社 | Cooler of pulse tube refrigerator |
| KR100393792B1 (en) * | 2001-02-17 | 2003-08-02 | 엘지전자 주식회사 | Pulstube refrigerator |
| CN1225625C (en) * | 2001-11-05 | 2005-11-02 | 富士电机株式会社 | Pulse-tube low temperature cooler |
| JP2004162587A (en) * | 2002-11-12 | 2004-06-10 | Sharp Corp | Cylinder structure, stirling engine and compressor |
| CN2819127Y (en) * | 2005-05-12 | 2006-09-20 | 中国科学院理化技术研究所 | Pulse tube refrigerator driven by thermoacoustic engine |
-
2005
- 2005-04-14 CN CNB2005100643401A patent/CN100572987C/en not_active Expired - Fee Related
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2007053809A2 (en) | 2005-10-31 | 2007-05-10 | Clever Fellows Innovation Consortium, Inc. | Acoustic cooling device with coldhead and resonant driver separated |
| JP2009526962A (en) * | 2005-10-31 | 2009-07-23 | クレヴァー フェローズ イノヴェイション コンソーティアム， インコーポレイテッド | Acoustic cooling device with cold head and resonant drive isolated |
| EP1952076A4 (en) * | 2005-10-31 | 2010-10-13 | Clever Fellows Innovation Cons | Acoustic cooling device with coldhead and resonant driver separated |
| CN100357676C (en) * | 2006-01-17 | 2007-12-26 | 浙江大学 | Corrugated pipe connecting device of conpled heat sound motor and pulse pipe refrigerator |
| CN100427848C (en) * | 2006-01-17 | 2008-10-22 | 浙江大学 | Heat sound driving pulse pipe refrigeration machine system |
| CN101275793B (en) * | 2007-03-27 | 2010-05-19 | 中国科学院理化技术研究所 | Thermo-acoustic magnetic refrigeration low-temperature system |
| CN100565039C (en) * | 2007-04-03 | 2009-12-02 | 中国科学院理化技术研究所 | Coupling device for thermoacoustic engine and refrigerator driven by thermoacoustic engine |
| CN101566405B (en) * | 2008-04-22 | 2011-05-11 | 中国科学院理化技术研究所 | Heat-driven thermoacoustic refrigerator device with traveling and standing wave type sound field |
| CN107609276A (en) * | 2017-09-15 | 2018-01-19 | 湖南科技大学 | Axial symmetry Thermoacoustic resonator Optimization Design based on pressure amplification factor |
| CN107633130A (en) * | 2017-09-15 | 2018-01-26 | 湖南科技大学 | Axial symmetry Thermoacoustic resonator performance estimating method based on pressure at two ends amplitude ratio |
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| Publication number | Publication date |
|---|---|
| CN100572987C (en) | 2009-12-23 |
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