CN2526750Y - Assembly for reducing resonance frequency of thermoacoustic system - Google Patents
Assembly for reducing resonance frequency of thermoacoustic system Download PDFInfo
- Publication number
- CN2526750Y CN2526750Y CN 02205906 CN02205906U CN2526750Y CN 2526750 Y CN2526750 Y CN 2526750Y CN 02205906 CN02205906 CN 02205906 CN 02205906 U CN02205906 U CN 02205906U CN 2526750 Y CN2526750 Y CN 2526750Y
- Authority
- CN
- China
- Prior art keywords
- thermoacoustic
- thermoacoustic system
- assembly
- utility
- frequency
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
Links
Images
Abstract
The utility model relates to an assembly for reducing resonance frequency of thermoacoustic system, which includes a piece of solid mass block and at least one metal membrane box; wherein, the end surface of the solid mass block is connected with one end of the metal membrane box. The assembly is arranged at any part of a resonatron of the thermoacoustic system and two ends of the resonatron of the thermoacoustic system are closed. The utility model can remarkably reduce the natural frequency of the thermoacoustic system without increasing the dimension of device, thereby solving the problem caused by overlarge dimension of the existing thermoacoustic system. The utility model remarkably reduces the natural frequency of the thermoacoustic system. While the exchange efficiency of the existing thermoacoustic system can be effectively improved after the thermoacoustic frequency is reduced. The utility model can increase the selecting freeness on working substances.
Description
Technical field
The utility model relates to a kind of parts that are used for thermoacoustic system, particularly relates to a kind of elastic diaphragm capsule-mass assembly that uses in the device of thermoacoustic system resonant frequency that reduces.
Background technology
The operating frequency of thermoacoustic system can not be excessive, because the thermoacoustic system conversion efficiency generally reduces along with the rising of frequency, this can be shown by following sound merit generation rate equation:
The physical significance of relevant symbol can list of references [1] in this formula (Xiao Jiahua. " theoretical research of the hot machine of thermoacoustic effect and back-heating type (comprising refrigeration machine) ", the 24th page, Beijing: Inst. of Physics, CAS, 1991) year is introduced: in the following formula, first of the right is illustrated in following theoretical maximum merit that can produce of certain thermograde, and second and the 3rd then represent owing to limited exchange capability of heat and sound power consumption that viscous drag caused are diffusing.This formula shows that the power consumption that the deficiency of exchange capability of heat and viscous drag cause is loose to be increased along with the increase of frequency, so, for a thermoacoustic system, if can reduce frequency, will reduce to dissipate, improve the conversion efficiency of thermoacoustic system.
Usually, the resonant frequency of a sound system (comprising thermoacoustic system) depends mainly on three factors: the length dimension of the geometry, particularly system of (1) system; (2) boundary condition of system; (3) velocity of sound of the used working media characteristic, particularly working media of system.
The acoustic construction of existing thermoacoustic system mainly contains: (1) standing wave type half-wavelength (or claiming 1/2nd wavelength) sound system; (2) standing wave type quarter-wave system; (3) has the quarter-wave system in partial row ripple loop.
The lowest resonance frequency of these sound systems is mainly determined by the velocity of sound of working gas, the length of pipe and the boundary condition of sound system.
Table 1 has provided above-mentioned three kinds of sound systems in the minimum natural reonant frequency data that adopt under gas with various medium and the different pipe ranges.As can be seen from Table 1, for the resonant frequency that makes sound system is lower than 50 hertz, then the length of pipeline generally will be at (to helium) more than 5 meters, otherwise resonant frequency will be far above 50 hertz.As seen, be lower than 50 hertz acoustic resonance system if make a frequency, its size is general huger so, not only increases the occupation of land space of system but also consume lot of materials, is unfavorable for practicability.Do not increasing under the size situation of system, can take to change the gas working medium kind, its velocity of sound is reduced, thereby reducing the resonant frequency of thermoacoustic system.But the working medium that is applicable to thermoacoustic system usually generally all adopts environmental protection, nontoxic and safe inert gas, as helium, neon, argon gas, nitrogen, carbon dioxide etc.The molecular weight of these gases is generally less, is difficult to reduce effectively the velocity of sound.Particularly, in the sound-driving low-temperature thermoacoustic refrigerator of heat, the general helium that adopt could obtain low temperature as working media more, but the velocity of sound of helium is very high, reaches about 1000 meter per seconds.As seen, these two kinds of methods are limited in the ability that reduces frequency, reduce aspect the system dimension.
The relation of the minimum intrinsic frequency of the different sound systems of table 1 and working gas, pipeline length
Annotate: (in the calculating of table 1, helium, neon, argon gas and the nitrogen velocity of sound when temperature T=300K is respectively 1019.4m/s, 353m/s, 455.9m/s, 322.4m/s.In addition, row ripple loop length is 0.2m in the travelling-wave type quarter-wave system)
Summary of the invention
The purpose of this utility model: be lower than 50 hertz acoustic resonance system in order to solve frequency of the existing making of above-mentioned prior art, its size is huger, not only increases the occupation of land space of system but also consume lot of materials, is unfavorable for the problem of practicability; It is generally less that next is to overcome the gas working medium kind molecular weight that is applicable to thermoacoustic system usually, is difficult to reduce effectively the problem of the velocity of sound; Thereby provide a kind of elastic diaphragm capsule-mass assembly that is used to reduce the thermoacoustic system resonant frequency.
The assembly that is used to reduce the thermoacoustic system resonant frequency that the utility model provides comprises: the metal bellows of at least one multilayer; It is characterized in that: also comprise a solid masses piece, the end face of this solid masses piece is connected with the metal bellows of a multilayer.
The both ends of the surface that also are included in the solid masses piece are fixed the metal bellows of a multilayer respectively.
The metal bellows of described multilayer such as wavy metal bellows.
During use the described assembly that is used for reducing the thermoacoustic system resonant frequency is installed in any part of the resonatron of thermoacoustic system, the other end and the resonatron of solid masses piece are fixed, the resonatron of the other end thermoacoustic system of the metal bellows of multilayer is fixed, the closed at both ends of the resonatron of this thermoacoustic system.
For make mass in sound system with gas motion, the assembly that the utility model provides is installed on any part in the resonatron of thermoacoustic system, the vibrational system of forming a quality-spring, wherein, gaseous mass in the system just is equivalent to the oscillating mass of this vibrational system, the compressibility of gas has then constituted the effective spring in this vibrational system, when the equivalent mass that can control this vibrational system and equivalent spring, so just might change the eigentone of this vibrational system, according to the General Principle of quality-spring vibration system, thereby effective oscillating mass of increase thermoacoustic system just can reduce the purpose that the intrinsic frequency of thermoacoustic system reaches the natural reonant frequency that reduces thermoacoustic system.
The utility model is as follows to the benefit that existing hot vocal cords come:
(1) needn't solve existing thermoacoustic system because of the oversize difficulty that produces by increasing the intrinsic frequency that device size just can reduce thermoacoustic system significantly;
(2) add the size that measure of the present utility model can greatly reduce existing thermoacoustic system, and reduce the intrinsic frequency of thermoacoustic system significantly; And hot acoustic frequency can improve the conversion efficiency that has thermoacoustic system now after reducing effectively.
(3) can increase the free degree that working medium is selected.For example, can mainly be conceived to the heat sound conversion performance of working medium and not necessarily pay close attention to the situation of its velocity of sound.
Description of drawings
Metal bellows spring-mass assembly assumption diagram of using in the device of Fig. 1 reduction thermoacoustic system of the present utility model resonant frequency.
Fig. 2 is the structural representation that has 1/2nd wavelength thermoacoustic systems of metal bellows spring-mass assembly.
The drawing explanation:
Folded-2 room temperature coolers-3 of high temperature heater (HTH)-1 heat plate
Resonatron-4 mass-5 metal bellows spring-6
Weld-7
The specific embodiment
Make (elastic diaphragm capsule-mass) assembly that is used to reduce the thermoacoustic system resonant frequency by Fig. 1, this assembly comprises: the wavy metal bellows 6 of a solid masses piece 5 that metallic copper material is made and a commercially available multilayer, and the end face of copper solid masses piece 5 welds (weld is 7 among the figure) mutually with the wavy metal bellows 6 of this multilayer.And the other end of the other end of the solid masses piece 5 of this assembly and wavy metal bellows 6 is separately fixed at any part in the resonatron 4 of thermoacoustic system, the closed at both ends of the resonatron 4 of thermoacoustic system.In the present embodiment, the diameter of resonatron 4 is 50 millimeters, a segment length L on the left side
1=0.2 meter, one section L on the right
2Length can change.Adopt the stainless steel wave bellows spring 6 of solder type, coefficient of elasticity is 2400N/m (Newton/meter), and the quality of the mass 5 that welds together with spring is 0.2kg (kilogram).
Make (elastic diaphragm capsule-mass) assembly that is used to reduce thermoacoustic system (1/2nd wavelength thermoacoustic systems) resonant frequency by Fig. 2.
This assembly has the wavy metal bellows 6 of a solid masses piece 5 that metallic copper material makes and a commercially available multilayer, and the end face of copper solid masses piece 5 welds (weld is 7 among the figure) mutually with the wavy metal bellows 6 of commercially available multilayer, the other end of the end face of copper solid masses piece 5 is at welding one wavy metal bellows 6, and the other end of the other end of solid masses piece 5 and wavy metal bellows 6 is installed in the resonatron closed at both ends of the resonatron of this thermoacoustic system.Thermoacoustic system is 1/2nd wavelength thermoacoustic systems in the present embodiment, and it mainly comprises common thermic sound converting unit, resonatron; Present embodiment as shown in Figure 2.Wherein, thermic sound unit is folded 2 by high temperature heater (HTH) 1, heat sound plate, room temperature cooler 3, and installs by being disposed in order shown in Fig. 2 and to form.Resonatron 4 is an isodiametric pipe, and two end faces all seal about it, metal bellows quality-spring assembly of the present utility model with it cut into about two sections, the assembly 1,2,3 of thermic sound unit is arranged in the pipe on resonatron 4 left sides.As further specifying of this embodiment, present embodiment provides a concrete structure size and relevant parameter designing, so that superiority of the present utility model to be described.In the present embodiment, the diameter of resonatron 4 is 50 millimeters, a segment length L on the left side
1=0.2 meter, one section L on the right
2Length can change.Adopt the stainless steel wave bellows spring 6 of solder type, coefficient of elasticity is 2400N/m (Newton/meter), and the quality of the mass 5 that welds together with spring is 0.2kg (kilogram).The working gas medium adopts helium, neon, argon gas and nitrogen respectively, and operating pressure is 2.0MPa.
Claims (3)
1, a kind of assembly that is used to reduce the thermoacoustic system resonant frequency comprises: at least one multiple layer metal bellows is characterized in that: also comprise a solid masses piece; Wherein the end face of solid masses piece is connected with a multiple layer metal bellows one end.
2. by the described assembly that is used to reduce the thermoacoustic system resonant frequency of claim 1; It is characterized in that: also be included in solid masses piece other end and be connected with a multiple layer metal bellows one end.
3. by claim 1 or 2 each described assemblies that are used to reduce the thermoacoustic system resonant frequency; It is characterized in that: described metal bellows can be the wavy metal bellows.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CN 02205906 CN2526750Y (en) | 2002-03-12 | 2002-03-12 | Assembly for reducing resonance frequency of thermoacoustic system |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CN 02205906 CN2526750Y (en) | 2002-03-12 | 2002-03-12 | Assembly for reducing resonance frequency of thermoacoustic system |
Publications (1)
Publication Number | Publication Date |
---|---|
CN2526750Y true CN2526750Y (en) | 2002-12-18 |
Family
ID=33687437
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
CN 02205906 Expired - Fee Related CN2526750Y (en) | 2002-03-12 | 2002-03-12 | Assembly for reducing resonance frequency of thermoacoustic system |
Country Status (1)
Country | Link |
---|---|
CN (1) | CN2526750Y (en) |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN100557345C (en) * | 2006-05-16 | 2009-11-04 | 中国科学院理化技术研究所 | The non-resonant DC heat exchanger that a kind of pressure wave drives |
CN1821048B (en) * | 2005-02-18 | 2014-01-15 | 中国科学院理化技术研究所 | Micronl nano thermoacoustic vibration excitor based on thermoacoustic conversion |
CN105066499A (en) * | 2015-04-28 | 2015-11-18 | 中国科学院理化技术研究所 | Gas multi-stage liquefying plant driven by acoustic resonance type thermo-acoustic engine |
CN111295556A (en) * | 2017-11-08 | 2020-06-16 | 三菱重工制冷空调系统株式会社 | Refrigerating machine |
-
2002
- 2002-03-12 CN CN 02205906 patent/CN2526750Y/en not_active Expired - Fee Related
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN1821048B (en) * | 2005-02-18 | 2014-01-15 | 中国科学院理化技术研究所 | Micronl nano thermoacoustic vibration excitor based on thermoacoustic conversion |
CN100557345C (en) * | 2006-05-16 | 2009-11-04 | 中国科学院理化技术研究所 | The non-resonant DC heat exchanger that a kind of pressure wave drives |
CN105066499A (en) * | 2015-04-28 | 2015-11-18 | 中国科学院理化技术研究所 | Gas multi-stage liquefying plant driven by acoustic resonance type thermo-acoustic engine |
CN111295556A (en) * | 2017-11-08 | 2020-06-16 | 三菱重工制冷空调系统株式会社 | Refrigerating machine |
US11536499B2 (en) | 2017-11-08 | 2022-12-27 | Mitsubishi Heavy Industries Thermal Systems, Ltd. | Refrigeration machine |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
Swift | Thermoacoustic engines | |
US6658862B2 (en) | Cascaded thermoacoustic devices | |
Zink et al. | CFD simulation of a thermoacoustic engine with coiled resonator | |
Xiao | Thermoacoustic heat transportation and energy transformation Part 1: Formulation of the problem | |
Hamood et al. | Design and construction of a two-stage thermoacoustic electricity generator with push-pull linear alternator | |
CN2526750Y (en) | Assembly for reducing resonance frequency of thermoacoustic system | |
Yang et al. | Performance of a looped thermoacoustic engine with multiple loads capable of utilizing heat source below 200° C | |
CN1215298C (en) | Method for reducing resonance frequency of thermoacoustic system and its equipment | |
Chen et al. | Development of a small-scale piezoelectric-driven thermoacoustic cooler | |
Xiao | Thermoacoustic theory for cyclic flow regenerators. Part I: fundamentals | |
Tan et al. | Performance of an air‐cooled looped thermoacoustic engine capable of recovering low‐grade thermal energy | |
Nathad et al. | Experimental analysis of an economical lab demonstration prototype of a thermo acoustic refrigerator (TAR) | |
CN2557889Y (en) | thermoacoutic system with low resonance frequency and small size | |
Minner | Theoretical evaluation of the optimal performance of a thermoacoustic refrigerator | |
Tamura et al. | Experimental and numerical analysis of a liquid-piston Stirling engine with multiple unit sections | |
Auriemma et al. | Performance of additive manufactured stacks in a small scale thermoacoustic heat engine | |
Chen et al. | Design and experimental investigations on a small scale traveling wave thermoacoustic engine | |
Dhuchakallaya et al. | The performance improvement of a cascade thermoacoustic engine by adjusting the acoustic impedance in the regenerator | |
Tew et al. | Recent Stirling engine loss-understanding results | |
Ibrahim et al. | Constraints and challenges in the development of loudspeaker-driven thermoacoustic refrigerator | |
Hamood et al. | Two-stage thermoacoustic electricity generator for waste heat recovery | |
Kamble et al. | Experimental and simulation studies on the performance of standing wave thermoacoustic prime mover for pulse tube refrigerator | |
Al-Mufti et al. | Thermoacoustic Refrigeration: Short Review | |
US20210108858A1 (en) | Monocoque shell and tube heat exchanger | |
Matsumoto et al. | Study of the reduction of the onset temperature in a loop-tube-type thermoacoustic prime mover using conical phase adjuster.—Based study on the installation position and onset temperature of conical phase adjuster |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
C14 | Grant of patent or utility model | ||
GR01 | Patent grant | ||
C19 | Lapse of patent right due to non-payment of the annual fee | ||
CF01 | Termination of patent right due to non-payment of annual fee |