CN113701383A - Multistage supersonic speed low-temperature refrigeration system driven by thermoacoustic compressor - Google Patents
Multistage supersonic speed low-temperature refrigeration system driven by thermoacoustic compressor Download PDFInfo
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- CN113701383A CN113701383A CN202010896912.7A CN202010896912A CN113701383A CN 113701383 A CN113701383 A CN 113701383A CN 202010896912 A CN202010896912 A CN 202010896912A CN 113701383 A CN113701383 A CN 113701383A
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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
- F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
- F25B9/006—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant containing more than one component
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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
- F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
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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
- F25B9/02—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point using Joule-Thompson effect; using vortex effect
- F25B9/04—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point using Joule-Thompson effect; using vortex effect using vortex effect
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Abstract
The invention relates to the technical field of refrigeration, and discloses a multistage supersonic speed low-temperature refrigeration system driven by a thermoacoustic compressor, which comprises: the system comprises a thermoacoustic compressor, a supersonic cyclone separator and an evaporator, wherein the outlet of the thermoacoustic compressor is sequentially connected with at least one supersonic cyclone separator in series, the gas outlet of the supersonic cyclone separator is connected with the inlet of the thermoacoustic compressor through a return pipeline, the inlet of the evaporator is connected with the liquid outlet of the supersonic cyclone separator, and the outlet of the evaporator is connected with the return pipeline. Compared with the traditional gas turbine expansion low-temperature technology, the supersonic cyclone separator has no moving part, the processing difficulty is low, and the operation reliability and stability are greatly improved; the thermo-acoustic compressor is adopted to replace the traditional compressor, no mechanical moving part exists, and the thermo-acoustic compressor has the advantages of low vibration and high reliability.
Description
Technical Field
The invention relates to the technical field of refrigeration, in particular to a multistage supersonic speed low-temperature refrigeration system driven by a thermoacoustic compressor.
Background
The traditional mechanical compression type refrigerating system consists of four main components, namely a compressor, a condenser, a throttling device, an evaporator and the like, wherein all the components are sequentially connected through pipelines to form a completely closed circulating system. Although the mechanical compression type refrigeration technology is mature, the defects that the refrigerant is harmful to the environment, mechanical moving parts in the compressor are easy to wear and damage and the like still exist.
And the traditional refrigeration system utilizes the actual gas throttling characteristic for refrigeration. Because of adopting the gas throttling refrigeration mode, the system is simple and reliable, so that the system is widely adopted in the common cold field and the low-temperature field. In the prior art, a turbo expander can be used for realizing gas throttling refrigeration. The turbo expander performs energy conversion by using the change of the speed of the working medium flowing in the flow passage, and is also called as a speed type expander. The working medium expands in the through-flow part of the turbo expander to obtain kinetic energy, and the working wheel shaft end outputs external work, so that the internal energy and the temperature of the working medium at the outlet of the expander are reduced. The low temperature can be obtained by adopting a turbo expander, and the turbo expansion low temperature technology is rapidly developed. However, the traditional gas turbine expansion low-temperature technology has the hidden troubles of mechanical moving parts, high processing requirement, unreliable and unstable operation and the like.
Disclosure of Invention
The embodiment of the invention provides a multi-stage supersonic speed low-temperature refrigeration system driven by a thermoacoustic compressor, which is used for solving or partially solving the problems of unreliable operation and unstable hidden danger of a mechanical motion part in the traditional refrigeration system.
The embodiment of the invention provides a multi-stage supersonic speed low-temperature refrigeration system driven by a thermoacoustic compressor, which comprises: the system comprises a thermoacoustic compressor, a supersonic cyclone separator and an evaporator, wherein the outlet of the thermoacoustic compressor is sequentially connected with at least one supersonic cyclone separator in series, the gas outlet of the supersonic cyclone separator is connected with the inlet of the thermoacoustic compressor through a return pipeline, the inlet of the evaporator is connected with the liquid outlet of the supersonic cyclone separator, and the outlet of the evaporator is connected with the return pipeline.
On the basis of the scheme, when the outlet of the thermoacoustic compressor is connected with a plurality of supersonic speed cyclone separators, the supersonic speed cyclone separators are connected with a plurality of evaporators in a one-to-one correspondence manner.
On the basis of the scheme, when the outlet of the thermoacoustic compressor is connected with a plurality of supersonic speed cyclone separators, the supersonic speed cyclone separators are connected with one evaporator.
On the basis of the scheme, a high-pressure one-way valve is arranged on an outlet pipeline of the thermoacoustic compressor; and a low-pressure one-way valve is arranged on the return pipeline.
On the basis of the scheme, the device also comprises a counter-flow heat exchanger, wherein the counter-flow heat exchanger is arranged at least one position between the thermoacoustic compressor and the supersonic cyclone separator and between two adjacent supersonic cyclone separators, a pipeline at least one position between the thermoacoustic compressor and the supersonic cyclone separator and between two adjacent supersonic cyclone separators flows through the high-temperature side of the counter-flow heat exchanger, and the return pipeline flows through the low-temperature side of the counter-flow heat exchanger.
On the basis of the scheme, the refrigerating working medium of the refrigerating system comprises CO2Or H2O、N2Or Ar, Ne or H2And He.
On the basis of the scheme, the number of the types of the refrigeration working media of the refrigeration system is larger than that of the supersonic speed cyclone separators.
On the basis of the scheme, the tail end of the supersonic cyclone separator is connected with a diffuser, and the outlet of the diffuser forms a gas outlet of the supersonic cyclone separator.
On the basis of the scheme, the supersonic cyclone separator further comprises a cyclone device, a Laval nozzle expander and a cyclone gas-liquid separator which are sequentially connected, a liquid collecting device is arranged on the cyclone gas-liquid separator, a liquid outlet is formed in the liquid collecting device, a gas outlet of the cyclone gas-liquid separator is connected to an inlet of the diffuser, and an outlet of the diffuser is connected with guide vanes.
On the basis of the scheme, the thermoacoustic compressor comprises a standing wave type thermoacoustic compressor or a traveling wave type thermoacoustic compressor.
Compared with the traditional gas turbine expansion low-temperature technology, the supersonic cyclone separator has no moving part, the processing difficulty is low, and the operation reliability and stability are greatly improved.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly described below, and it is obvious that the drawings in the following description are some embodiments of the present invention, and those skilled in the art can also obtain other drawings according to the drawings without creative efforts.
FIG. 1 is a schematic view of a first connection for a standing wave type thermoacoustic compressor in accordance with an embodiment of the present invention;
FIG. 2 is a second schematic connection diagram of a standing wave type thermoacoustic compressor in accordance with an embodiment of the present invention;
FIG. 3 is a schematic diagram illustrating the connection of a traveling-wave type thermoacoustic compressor in accordance with an embodiment of the present invention;
FIG. 4 is a schematic diagram of the configuration of a supersonic cyclonic separator in an embodiment of the present invention.
Reference numerals:
11. a standing wave type thermo-acoustic compressor; 111. a thermal chamber; 112. a heater; 113. a heat regenerator; 114. a room temperature heat exchanger; 115. a resonant tube; 12. a traveling wave type thermo-acoustic compressor; 121. a feedback tube; 122. a room temperature heat exchanger; 123. a heat regenerator; 124. a heater; 125. a thermal buffer tube; 126. a secondary heat exchanger; 127. an elastic film; 128. a resonant tube; 2. a counter-flow heat exchanger; 21. a primary counter-flow heat exchanger; 22. a secondary counter-flow heat exchanger; 23. a third stage counter-current heat exchanger; 3. a supersonic cyclonic separator; 31. a first supersonic cyclone; 32. a secondary supersonic cyclone separator; 33. a three-stage supersonic cyclone separator; 301. a swirling device; 302. a Laval nozzle expander; 303. a cyclonic gas-liquid separator; 304. a diffuser; 305. a guide blade; 306. a liquid collection device; 3021. a stabilization section; 3022. a subsonic contraction section; 3023. a throat; 3024. a supersonic expansion section; 4. an evaporator; 41. a first-stage evaporator; 42. a secondary evaporator; 43. a third-stage evaporator; 5. a high pressure check valve; 6. a low pressure check valve.
Detailed Description
In order to make the objects, technical solutions and advantages of the embodiments of the present invention clearer, the technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are some, but not all, embodiments of the present invention. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
Referring to fig. 1, an embodiment of the present invention provides a multi-stage supersonic cryogenic refrigeration system driven by a thermoacoustic compressor, the multi-stage supersonic refrigeration system comprising: the device comprises a thermoacoustic compressor, a supersonic cyclone separator 3 and an evaporator 4, wherein the outlet of the thermoacoustic compressor is sequentially connected with at least one supersonic cyclone separator 3 in series, the gas outlet of the supersonic cyclone separator 3 is connected with the inlet of the thermoacoustic compressor through a return pipeline, the inlet of the evaporator 4 is connected with the liquid outlet of the supersonic cyclone separator 3, and the outlet of the evaporator 4 is connected with the return pipeline.
The supersonic cyclone separator 3 based on supersonic refrigeration effect was first applied in 1989 for the separation of gas and liquid. Then the natural gas is introduced into the field of natural gas treatment and processing, and is mainly used for dehydration and heavy hydrocarbon removal of natural gas. The supersonic cyclone separator 3 has both refrigeration effect and gas-liquid separation function, and the end is provided with a diffuser 304. The refrigeration system provided by the embodiment proposes to provide a supersonic cyclonic separator 3 in place of the gas turboexpansion means of conventional refrigeration systems. The cooling effect of the traditional throttling device is achieved by utilizing the refrigeration effect of the supersonic cyclone separator 3; and the pressure and temperature increasing function of the uncondensed working medium can be realized by utilizing the pressure expansion function of the supersonic cyclone separator 3. Therefore, the pressure drop of the traditional turbine expansion device to the refrigeration working medium can be compensated.
Compared with the traditional gas turbine expansion low-temperature technology, the supersonic cyclone separator 3 has no moving part, the processing difficulty is low, and the operation reliability and stability are greatly improved. Compared with the traditional throttling devices in a vapor compression refrigeration system, such as a throttling valve, an expansion machine and the like, the device has the advantages of high efficiency, small pressure drop, large temperature drop, low energy consumption, good stability (the supersonic cyclone separator 3 has no rotating part), and long-term reliability.
Research shows that under the condition of the same pressure drop, the temperature drop in the supersonic cyclone separator 3 is larger than that of the traditional throttling devices such as a throttling valve, an expander and a vortex tube, and the supersonic cyclone separator has a better refrigeration effect. In addition, the supersonic cyclone 3 has advantages that the throttle valve, the expander, the vortex tube and the like do not have, namely the pressure can be boosted through the diffuser 304, and the pressure loss of the gas is greatly reduced.
Further, the present embodiment provides at least one supersonic cyclone 3, and a multistage refrigeration cycle can be formed by providing a plurality of supersonic cyclones 3. The inlets and gas outlets of the supersonic cyclone separators 3 are sequentially connected end to end, and the gas outlet of the supersonic cyclone separator 3 at the tail end is connected with the inlet of the thermoacoustic compressor through a return pipeline. The refrigerating working medium circularly flows in the loop to form a cascade refrigeration cycle, and the cascade refrigeration cycle has many advantages: firstly, only a single compressor is adopted, so that the structure is compact and the control is simple; secondly, the low-temperature end has no moving part, so that the stability is good and the reliability is high; thirdly, because the high-boiling-point component forms liquid at a higher temperature and returns to the low-pressure channel, namely the return pipeline, through throttling, solid phase precipitation at a low temperature is avoided, the throttling element is blocked, and the reliability of the system is further improved; in addition, the high-boiling point component is throttled at a higher temperature and returns to a low-pressure channel, namely a return pipeline, so that the load of a next-stage heat exchanger is reduced, and the flow loss and the heat return loss caused by the high-boiling point component in circulation at a low-temperature section are reduced; finally, the high-boiling point component is throttled at a higher temperature and returns to a low-pressure channel, namely a return pipeline, so that the water equivalent ratio of high-pressure and low-pressure airflow is effectively changed, and the heat regeneration efficiency is improved.
Further, the thermoacoustic effect refers to a time-averaged energy effect generated by the acoustic oscillation of a compressible fluid and a solid medium due to thermal interaction, and can be divided into two types according to the difference of energy conversion directions: firstly, the heat energy is used for generating sound waves, namely, the thermoacoustic effect (thermoacoustic positive effect); the second is to use sound energy to generate refrigeration effect, i.e. sound refrigeration effect (thermoacoustic reverse effect). The thermoacoustic heat engine is a thermal-power conversion device which converts thermal energy into mechanical energy in the form of acoustic waves by utilizing thermoacoustic effect. Thermoacoustic heat engines are mainly divided into thermoacoustic engines (thermoacoustic compressors) and thermoacoustic refrigerators, which operate on the basis of thermoacoustic effects of thermoacoustic and acoustic refrigeration, respectively.
The thermoacoustic compressor is a device which constructs a proper sound field by using a pipe fitting and a heat exchanger and converts external heat energy into sound energy through the interaction between a working medium and a heat regenerator. For thermoacoustic compressors, if the heat input from an external high temperature heat source exceeds the hot end temperature by a certain threshold value (typically between 100 ℃ C. and 600 ℃ C.), the system will spontaneously generate periodic pressure fluctuations, i.e., utilize the heat to generate high intensity sound waves without the aid of any mechanical moving parts. The thermoacoustic technology becomes a novel energy conversion technology which is environment-friendly, reliable and has application prospect due to unique advantages.
The multistage supersonic speed low-temperature refrigeration system driven by the thermoacoustic compressor provided by the embodiment adopts the thermoacoustic compressor to replace the traditional compressor, firstly, the thermoacoustic compressor is used as an external combustion type heat engine, and can be driven by low-grade energy or solar energy and the like, so that the energy utilization rate (energy conservation) is improved; secondly, helium, nitrogen and other environment-friendly gas working media (environmental protection) can be adopted; in addition, the thermoacoustic compressor generally comprises a hollow pipe section, a porous medium and a heat exchanger, does not have a mechanical moving part, has the advantages of low vibration, high reliability, long service life and the like (reliability), and solves the problem that the mechanical moving part of the existing compressor is easy to wear and damage.
On the basis of the above embodiment, further, referring to fig. 1, when a plurality of supersonic cyclone separators 3 are connected to the outlet of the thermo-acoustic compressor, a plurality of evaporators 4 are connected to the plurality of supersonic cyclone separators 3 in one-to-one correspondence. I.e. one evaporator 4 is connected to each supersonic cyclone 3. The plurality of evaporators 4 are connected to the return lines, respectively.
Alternatively, referring to fig. 2, when a plurality of supersonic cyclones 3 are connected to the outlet of the thermo-acoustic compressor, the plurality of supersonic cyclones 3 are commonly connected to one evaporator 4. That is, a plurality of supersonic cyclone separators 3 are connected to one evaporator 4, so that higher refrigerating capacity can be obtained.
Further, as shown in FIG. 2, when a plurality of supersonic cyclones 3 are connected to one evaporator 4, the evaporator 4 may have a plurality of inlets connected to the plurality of supersonic cyclones 3 in a one-to-one correspondence, and may have an outlet for collecting the refrigerant flowing out. In addition, a plurality of independent heat exchange pipelines can be arranged in the evaporator 4, namely a plurality of inlets and a plurality of outlets are arranged, the plurality of heat exchange pipelines are correspondingly connected with the plurality of supersonic cyclone separators 3 one by one, and the plurality of outlets can be respectively connected with the return pipeline. The specific form and number of the evaporators 4 are not limited.
When a plurality of supersonic cyclone separators 3 are arranged, a mixed working medium is adopted by the refrigerating system. The refrigerating system adopts mixed working media, and the liquefaction temperatures of different working media are different. So that different supersonic cyclone separators 3 liquefy different working media to obtain different refrigeration temperatures. Two or more different refrigerants can be used, and the self-cascade refrigeration cycle is formed by combining two or more single-stage refrigeration systems. The self-cascade refrigeration cycle can realize the refrigeration temperature range from a liquid nitrogen temperature range lower than 80K to a traditional vapor compression refrigeration cycle of 230K, and has great practical value in the fields of common refrigeration and cryogenic refrigeration such as blood, medicine preservation, food freezing storage, gas liquefaction and the like in the semiconductor industry and low-temperature medicine.
On the basis of the above embodiment, further, a high-pressure one-way valve 5 is arranged on an outlet pipeline of the thermoacoustic compressor; a low-pressure one-way valve 6 is arranged on the return pipeline. The smooth flow of the refrigeration working medium in the loop can be controlled. The high pressure check valve 5 and the low pressure check valve 6 are relatively speaking, the pressure of the working medium flowing through the high pressure check valve 5 is higher than the pressure of the working medium flowing through the low pressure check valve 6.
On the basis of the above embodiment, further, referring to fig. 1, a multi-stage supersonic cryogenic refrigeration system driven by a thermoacoustic compressor further comprises a counter-flow heat exchanger 2. A counter-flow heat exchanger 2 is arranged at least one position between the thermoacoustic compressor and the supersonic cyclone separator 3 and between two adjacent supersonic cyclone separators. At least one pipeline between the thermoacoustic compressor and the supersonic cyclone separator 3 and between two adjacent supersonic cyclone separators 3 flows through the high-temperature side of the counter-flow heat exchanger 2, and the return pipeline flows through the low-temperature side of the counter-flow heat exchanger 2.
The high temperature side of the counterflow heat exchanger 2, i.e., the side with the higher temperature, is the heat source in the heat exchanger. The low temperature side of the counter flow heat exchanger 2, i.e. the side with lower temperature, is the cold source in the heat exchanger. Specifically, a counter-flow heat exchanger 2 can be arranged between the thermoacoustic compressor and the supersonic cyclone separator 3; a counter-flow heat exchanger 2 can also be arranged between two adjacent supersonic cyclone separators 3; and a counter-flow heat exchanger 2 can be arranged between the thermoacoustic compressor and the supersonic cyclone separator 3 and between two adjacent supersonic cyclone separators 3. The counter-flow heat exchanger 2 is favorable for improving the energy utilization rate and the refrigeration efficiency.
On the basis of the above embodiment, further, the refrigerant of the refrigeration system includes CO2Or H2O、N2Or Ar, Ne or H2And He. The refrigeration working medium is environment-friendly, and can obtain a better refrigeration effect through phase change. Namely, the difference of the liquefaction temperatures of different types of refrigeration working media is greater than or equal to the preset difference.
The liquefaction temperatures of different types of refrigeration working media are changed in a step mode and are different from each other greatly; CO 22、N2The liquefaction temperatures of the Ne working medium and the He working medium are different greatly and are reduced in a step-type mode, and the Ne working medium and the He working medium can be used as four layers of refrigeration working media to realize multi-stage refrigeration; and CO2And H2The O liquefaction temperature has small difference and is used as the same-level refrigeration working medium for replacement; n is a radical of2The temperature difference between the refrigerant and the Ar liquefaction temperature is not large, and the refrigerant is used as the same-level refrigerant for replacement; ne and H2The liquefaction temperature difference is not large, and the refrigerant is used as the same-level refrigerant for replacement. In the high temperature first stage refrigeration, CO2For condensing working medium, the remainder being Ar or N2Ne or H2He and the like are isentropic expansion gases and exist in a mixture form; then, a second stage of refrigeration, Ar or N2For condensing working substances, Ne or H2And He is an isentropic expansion working medium; third stage refrigeration, Ne or H2Is a condensing working medium, and He is an isentropic expansion working medium.
Further, the refrigerant in the refrigeration system described in each of the above embodiments may also be other gases, so as to achieve the purpose of obtaining a better refrigeration effect through phase change by liquefaction, and is not particularly limited. Preferably, the refrigerant in the refrigeration system is a mixture of at least two gases having different liquefaction temperatures. During multi-stage refrigeration, each component of the mixed gas can be sequentially liquefied according to different liquefaction temperatures, so that a multi-stage refrigeration effect is achieved.
Furthermore, different refrigeration temperature regions can be realized by adopting different refrigeration working medium combinations. Different combinations of refrigerant media can be used to achieve a wide range of refrigeration from the refrigeration temperature region to the low temperature region.
On the basis of the above embodiment, further, the number of types of the refrigerant of the refrigeration system is greater than the number of the supersonic cyclone separators 3, and different types of the refrigerant have different liquefaction temperatures. Thereby liquefying one working medium at each supersonic cyclone 3, and obtaining different refrigeration temperature gradients by liquefying different working media in different supersonic cyclones 3.
In addition to the above-described embodiments, a diffuser 304 is connected to a tip end of the supersonic cyclone 3, and an outlet of the diffuser 304 forms a gas outlet of the supersonic cyclone 3. The supersonic cyclone 3 has a liquid outlet connected to the inlet of the evaporator 4, and the uncondensed gaseous working medium in the supersonic cyclone 3 directly enters the diffuser 304 and is discharged. The supersonic cyclone 3 has the function of gas-liquid separation. A liquid outlet is provided before the diffuser 304 for the outflow of liquid. The temperature of the refrigeration working medium introduced into the supersonic cyclone separator 3 is further reduced, and the refrigeration working medium liquid generated after the temperature is reduced and liquefied is collected from the liquid outlet and flows out; the refrigerant gas that is not liquefied flows directly into the diffuser 304, and joins the refrigerant that flows back from the evaporator 4 to diffuse.
On the basis of the above embodiment, referring to fig. 4, the supersonic cyclone 3 further includes a cyclone device 301, a Laval nozzle expander 302 and a cyclone gas-liquid separator 303 connected in sequence, the cyclone gas-liquid separator 303 is provided with a liquid collecting device 306, the liquid collecting device 306 is provided with a liquid outlet, a gas outlet of the cyclone gas-liquid separator 303 is connected to an inlet of a diffuser 304, and an outlet of the diffuser 304 is connected to a guide vane 305.
Based on the above embodiment, further, the Laval nozzle expander 302 comprises a stabilizing section 3021, a subsonic convergent section 3022, a throat section 3023 and a supersonic divergent section 3024 connected in series, wherein the stabilizing section 3021 is connected to the outlet of the swirling device 301.
Referring to fig. 4, the supersonic cyclone 3 is generally composed of 4 parts such as a cyclone 301, a Laval nozzle expander 302, a cyclone gas-liquid separator 303, and a diffuser 304. Both gas expansion refrigeration and liquefaction processes occur primarily within the Laval nozzle expander 302. The Laval nozzle expander 302 may be divided into 4 sections, a stationary section 3021, a subsonic convergent section 3022, a throat section 3023, and a supersonic divergent section 3024. The working principle is as follows: the gas enters the cyclone device 301 to rotate and has certain acceleration; the gas is expanded to supersonic speed rapidly in a Laval nozzle expander 302 to form a low-temperature low-pressure environment (the temperature is reduced because part of the heat of the gas is converted into kinetic energy), and part of the gas is condensed and liquefied to form gas-liquid two-phase flow; liquid drops are thrown to the pipe wall under the action of tangential speed generated by rotation and strong cyclone field centrifugal force, discharged from a special liquid outlet in the cyclone gas-liquid separator 303, and gas is discharged through a diffuser 304 to realize gas-liquid separation; after the speed reduction, the pressure increase and the temperature rise of the diffuser 304, most of the pressure loss of the gas through the supersonic cyclone separator 3 can be recovered, and the pressure loss of the gas is greatly reduced.
On the basis of the above-described embodiments, the thermoacoustic compressor further comprises a standing-wave thermoacoustic compressor 11 or a traveling-wave thermoacoustic compressor 12.
Specifically, referring to fig. 1, the thermoacoustic compressor includes a thermal chamber 111, a heater 112, a heat regenerator 113, a room temperature heat exchanger 114, and a resonance tube 115, which are connected in sequence; the thermo-acoustic compressor in this embodiment is a standing wave type thermo-acoustic compressor 11. The outlet and inlet of the standing wave type thermo-acoustic compressor 11 are both arranged on the resonance tube 115. The outlet and inlet should be placed at locations where pressure fluctuations are large and may be close. A high-pressure one-way valve 5 is arranged between the thermoacoustic compressor and the supersonic cyclone separator 3; the inlet pipeline of the thermoacoustic compressor is provided with a low-pressure one-way valve 6. The high-pressure one-way valve and the low-pressure one-way valve are close to the thermoacoustic engine as much as possible; the valve is arranged at the position where the pressure fluctuation of the thermoacoustic system is large, so that a large pressure ratio can be obtained.
Further, referring to FIG. 3, the present embodiment provides a traveling-wave type thermoacoustic compressor 12. The traveling-wave type thermoacoustic compressor 12 includes, in series, a room temperature heat exchanger 122, a regenerator 123, a heater 124, a thermal buffer tube 125, a secondary heat exchanger 126, and a resonator tube 128. In addition, the resonance tube 128 may be connected to one end of the feedback tube 121, and the other end of the feedback tube 121 is connected to the room temperature heat exchanger 122. Referring to fig. 3, the outlet and inlet of traveling-wave type thermoacoustic compressor 12 are disposed on resonating tube 128. The outlet and inlet should be placed at locations where pressure fluctuations are large and may be close. A high-pressure one-way valve 5 is arranged between the thermoacoustic compressor and the supersonic cyclone separator 3; the inlet pipeline of the thermoacoustic compressor is provided with a low-pressure one-way valve 6. The high-pressure one-way valve and the low-pressure one-way valve are close to the thermoacoustic engine as much as possible; the valve is arranged at the position where the pressure fluctuation of the thermoacoustic system is large, so that a large pressure ratio can be obtained. A resilient membrane 127 may also be disposed within the traveling-wave thermo-acoustic compressor 12.
Based on the above embodiments, in particular, fig. 1 provides a method and a system for implementing multistage supersonic low-temperature refrigeration driven by a thermally driven standing wave thermoacoustic compressor. The system mainly comprises a standing wave type thermoacoustic compressor 11, a counter-flow heat exchanger 2, a supersonic cyclone separator 3, an evaporator 4, a high-pressure one-way valve 5 and a low-pressure one-way valve 6. The standing wave type thermoacoustic compressor 11 is composed of a thermal cavity 111, a heater 112, a heat regenerator 113, a room temperature heat exchanger 114 and a resonant tube 115. The counter-flow heat exchanger 2 consists of a primary counter-flow heat exchanger 21, a secondary counter-flow heat exchanger 22 and a tertiary counter-flow heat exchanger 23 which are all identical. The supersonic cyclone 3 is composed of a first supersonic cyclone 31, a second supersonic cyclone 32 and a third supersonic cyclone 33 which are all identical. Each stage of supersonic cyclone separator 3 is composed of a cyclone device 301, a Laval nozzle expander 302, a cyclone gas-liquid separator 303, a diffuser 304, guide vanes 305 and a liquid collecting device 306. Laval nozzle expander 302 is comprised of a stabilizing section 3021, a subsonic convergent section 3022, a throat section 3023, and a supersonic divergent section 3024. The evaporator 4 is composed of a primary evaporator 41, a secondary evaporator 42, and a tertiary evaporator 43 which are identical.
Unlike the traditional refrigerant in mechanical compression type refrigerating system, the system adopts CO2、N2(or Ar, N)2Close to the liquefaction temperature of Ar), Ne (or H)2Ne and H2The liquefaction temperature is close), and the mixed gas of He and the like can be used as the circulating working medium to realize the closed low-temperature refrigeration circulation within the range of 120K-20K,is friendly to the environment.
When the system is in operation, heat is input to the system by the heater 112, the heat source may be solar energy or low-grade energy such as industrial waste heat, etc., and the room temperature heat exchanger 114 transfers the excess heat to the outside. When the axial temperature gradient formed by the temperature difference at the two sides of the regenerator 113 (the regenerator is a conventional regenerator with a porous structure, such as a wire mesh structure, a silk floss structure or a stainless steel ball) reaches a certain value, the system can oscillate by self-excitation, and the heat of the room temperature heat exchanger 114, the regenerator 113 and the heater 112 can be converted into mechanical energy in the form of acoustic power in the regenerator 113 by the sub-component of the standing wave type thermoacoustic compressor 11, so that the thermal power conversion process is realized. The sound work generated by the thermoacoustic compressor 11 is transmitted to the first-stage counter-flow heat exchanger 21 through the resonance tube 115 and the high-pressure one-way valve 5, and enters the first-stage supersonic cyclone separator 31 after sufficient heat exchange. The resonator tubes 115 act as phase modulators.
CO2、N2(Ar)、Ne(H2) The He mixed gas enters a first-stage supersonic cyclone separator 31, firstly forms a cyclone flow state after passing through a cyclone device 301, then enters a Laval nozzle expander 302, sequentially flows through a stable section 3021, a subsonic contraction section 3022, a throat 3023 and a supersonic expansion section 3024, the gas mixture is rapidly expanded to supersonic speed in the Laval nozzle expander 302 to generate a refrigeration effect, a low-temperature and low-pressure environment is formed (the temperature is reduced because part of the heat of the gas is converted into kinetic energy), and firstly, high-boiling point CO (carbon monoxide) is mixed with high-boiling point CO2The gas is condensed and liquefied, and CO is generated under the action of tangential speed generated by rotation and the centrifugal force of a strong cyclone field2The droplets are thrown to the tube wall, discharged by a special liquid collecting device 306 in the cyclone gas-liquid separator 303, and enter the primary evaporator 41 where they are evaporated (boiled) to CO in the primary evaporator 412Vapour, absorbing heat from the environment or the substance to be cooled, lowering the temperature of the environment or the substance to be cooled, CO2The vapor is discharged from the primary evaporator 41 into a low-pressure passage. The remaining N2(Ar)、Ne(H2) The mixed gas of He flows out of the first-stage supersonic cyclone separator 31 through the diffuser 304 and the guide vanes 305 stably, and enters the second stageCounter-flow heat exchanger 22. After the speed reduction, the pressure increase and the temperature rise of the diffuser, most of the pressure lost by the gas through the supersonic cyclone separator can be recovered, and the pressure loss of the gas is greatly reduced. The process is identical to the above process and will not be described in detail.
It should be noted that N is obtained after the secondary refrigeration2(Ar) is condensed and evaporated (boiled) in the secondary evaporator 42 to become N2The (Ar) vapor, absorbing heat from the environment or the substance to be cooled, exits the secondary evaporator 42 into a low pressure channel. Ne (H) after three-stage refrigeration2) Condensed and evaporated (boiled) in the tertiary evaporator 43 to Ne (H)2) The vapor, absorbing the heat of the environment or the substance to be cooled, is discharged from the three-stage evaporator 43, enters the low-pressure channel, passes through the low-pressure one-way valve 6, enters the low-pressure port of the thermoacoustic compressor, and further forms a closed low-temperature refrigeration cycle.
The system adopts CO2、N2(Ar)、Ne(H2) The mixed gas of He and the like is used as a circulating working medium, so that closed low-temperature refrigeration circulation within the range of 120K-20K can be realized, and the environment is friendly; the refrigeration working medium is driven to circulate in the closed system by the thermoacoustic compressor based on the thermoacoustic effect, and the refrigeration system has the advantages of no mechanical moving part, high reliability, long service life and full utilization of solar energy or low-grade energy; the mixed working medium self-overlapping throttling refrigeration cycle is adopted, and the system has the advantages of reduced operating pressure, simple and compact structure, low construction cost, high system efficiency and the like; the supersonic cyclone separator based on supersonic refrigeration effect is used as an expansion cooling element, and simultaneously plays the roles of a gas-liquid separator and a throttle valve in the traditional self-cascade refrigeration cycle, and has the advantages of high efficiency, small pressure drop, large temperature drop, low energy consumption, good stability (the supersonic cyclone separator has no rotating part), long-term reliability and the like. It is emphasized that the number and location of the counter-flow heat exchangers, supersonic cyclones and evaporators arranged in the system can be adjusted according to the specific refrigeration requirement; the number of the thermoacoustic compressors is determined according to the refrigeration requirement of the system; the adopted mixed working medium can also be selected and proportioned according to the specific refrigeration requirement.
Based on the above embodiments, fig. 3 further provides a method and a system for implementing multistage supersonic low-temperature refrigeration driven by a thermally-driven traveling wave thermoacoustic compressor. Unlike the embodiment shown in fig. 1, in this embodiment, the traveling-wave type thermo-acoustic compressor is used to drive the circulating fluid to refrigerate in the closed system, and the efficiency of the acoustic power generated by the traveling-wave type thermo-acoustic compressor 12 is higher. When the system is in operation, heat is input to the system by the heater 124, and the room temperature heat exchanger 122 transfers the excess heat to the outside. When the axial temperature gradient formed by the temperature difference at the two sides of the regenerator 123 (the regenerator is a regenerator with a conventional porous structure, such as a wire mesh structure, a silk floss structure or a stainless steel ball) reaches a certain value, the system can oscillate by self-excitation, and the traveling wave type thermoacoustic compressor 12 sub-component composed of the room temperature heat exchanger 122, the regenerator 123 and the heater 124 can convert the heat into mechanical energy in the form of acoustic power in the regenerator 123, thereby realizing the thermal power conversion process. A part of the acoustic power generated by the traveling-wave type thermoacoustic compressor 12 is transmitted to the first-stage counter-flow heat exchanger 21 through the thermal buffer tube 125, the secondary heat exchanger 126, the resonance tube 128 and the high-pressure check valve 5, and the following process is consistent with the embodiment shown in fig. 1 and will not be described again; the other part returns to the room temperature heat exchanger 122 along the feedback pipe 121 to be amplified again and repeatedly. The elastic membrane 127 in the feedback tube 121 acts to cancel the loop dc current.
The system adopts CO2、N2(Ar)、Ne(H2) The mixed gas of He and the like is used as a circulating working medium, so that closed low-temperature refrigeration circulation within the range of 120K-20K can be realized, and the environment is friendly; the refrigeration working medium is driven to circulate in the closed system by the thermoacoustic compressor based on the thermoacoustic effect, and the refrigeration system has the advantages of no mechanical moving part, high reliability, long service life and full utilization of solar energy or low-grade energy; the mixed working medium self-overlapping throttling refrigeration cycle is adopted, and the system has the advantages of reduced operating pressure, simple and compact structure, low construction cost, high system efficiency and the like; the supersonic cyclone separator based on supersonic refrigeration effect is used as an expansion cooling element, has the functions of a gas-liquid separator and a throttle valve in the traditional self-cascade refrigeration cycle, and has the advantages of high efficiency, small pressure drop, large temperature drop, low energy consumption and good stability (the supersonic cyclone separator does not have the function of the throttle valve per se)Rotating parts), long-term reliability, etc. It is emphasized that the number and location of the counter-flow heat exchangers, supersonic cyclones and evaporators arranged in the system can be adjusted according to the specific refrigeration requirement; the number of the thermoacoustic compressors is determined by the refrigeration requirement of the system, and the forms of loop multistage structures and the like can be adopted according to the specific working environment and the refrigeration requirement; the adopted mixed working medium can also be selected and proportioned according to the specific refrigeration requirement.
The above embodiments address the following problems of the existing cryogenic refrigeration technology: the refrigerant in the traditional mechanical compression type refrigerating system is harmful to the environment, and mechanical moving parts in the compressor are easy to wear and damage; the classic cascade refrigeration system has the problems of complex structure and high manufacturing and maintenance cost; the traditional throttling device in the self-cascade refrigeration system has the problems of low efficiency, large pressure drop and high energy consumption. Provides a method and a system for realizing multistage supersonic speed low-temperature refrigeration driven by a thermally-driven thermoacoustic compressor, wherein the system adopts CO2、N2(or Ar), Ne (may be H)2) The mixed gas of He and the like is used as a circulating working medium, so that closed low-temperature refrigeration circulation within the range of 120K-20K can be realized, and the environment is friendly; the refrigeration working medium is driven to circulate in the closed system by the thermoacoustic compressor based on the thermoacoustic effect, and the refrigeration system has the advantages of no mechanical moving part, high reliability, long service life and full utilization of solar energy or low-grade energy; the mixed working medium self-overlapping throttling refrigeration cycle is adopted, and the system has the advantages of reduced operating pressure, simple and compact structure, low construction cost, high system efficiency and the like; the supersonic cyclone separator based on supersonic refrigeration effect is used as an expansion cooling element, and simultaneously plays the roles of a gas-liquid separator and a throttle valve in the traditional self-cascade refrigeration cycle, and has the advantages of high efficiency, small pressure drop, large temperature drop, low energy consumption, good stability (the supersonic cyclone separator has no rotating part), long-term reliability and the like.
Furthermore, the existing supersonic cyclone separator is mainly used for removing impurities such as water vapor and heavy hydrocarbon in natural gas, and a proper working medium is not selected to construct a closed supersonic refrigeration cycle suitable for a low-temperature region. The invention can realize closed supersonic low-temperature refrigeration circulation within the range of 120K-20K.
The thermoacoustic compressor is composed of a thermoacoustic engine in the forms of standing wave type, traveling wave type or loop multistage and the like, and a high-pressure and low-pressure one-way valve is arranged at a proper thermoacoustic position (high pressure ratio position), so that stable high-pressure flow and low-pressure flow can be generated. The refrigeration working medium is driven to circulate in the closed system by the thermoacoustic compressor based on the thermoacoustic effect, and the refrigeration system has the advantages of no mechanical moving part, high reliability, long service life and full utilization of solar energy or low-grade energy; the standing wave type and traveling wave type thermo-acoustic compressors are adopted to play a role of the compressor in the traditional mechanical compression type refrigerating system, and solar energy or low-grade energy sources such as industrial waste heat, waste heat and the like can be fully utilized to carry out heat-driven refrigeration.
The multistage supersonic speed low-temperature refrigeration system driven by the thermoacoustic compressor overcomes the defects that a refrigerant in the traditional mechanical compression type refrigeration system is harmful to the environment, mechanical moving parts in the compressor are easy to wear and damage and the like, and solves the problems that the traditional cascade refrigeration system is complex in structure, high in manufacturing and maintenance cost, low in efficiency, large in pressure drop, high in energy consumption and the like of the traditional throttling device in the self-cascade refrigeration system.
Finally, it should be noted that: the above examples are only intended to illustrate the technical solution of the present invention, but not to limit it; although the present invention has been described in detail with reference to the foregoing embodiments, it will be understood by those of ordinary skill in the art that: the technical solutions described in the foregoing embodiments may still be modified, or some technical features may be equivalently replaced; and such modifications or substitutions do not depart from the spirit and scope of the corresponding technical solutions of the embodiments of the present invention.
Claims (10)
1. A multi-stage supersonic cryogenic refrigeration system driven by a thermoacoustic compressor, comprising: the system comprises a thermoacoustic compressor, a supersonic cyclone separator and an evaporator, wherein the outlet of the thermoacoustic compressor is sequentially connected with at least one supersonic cyclone separator in series, the gas outlet of the supersonic cyclone separator is connected with the inlet of the thermoacoustic compressor through a return pipeline, the inlet of the evaporator is connected with the liquid outlet of the supersonic cyclone separator, and the outlet of the evaporator is connected with the return pipeline.
2. The multi-stage supersonic cryogenic refrigeration system driven by a thermoacoustic compressor according to claim 1, wherein when a plurality of supersonic cyclones are connected to an outlet of the thermoacoustic compressor, a plurality of evaporators are connected to the plurality of supersonic cyclones in a one-to-one correspondence.
3. The thermoacoustic compressor driven multistage supersonic cryogenic refrigeration system of claim 1, wherein when a plurality of supersonic cyclones are connected to an outlet of said thermoacoustic compressor, a plurality of said supersonic cyclones are commonly connected to one said evaporator.
4. The thermoacoustic compressor driven multistage supersonic cryogenic refrigeration system of claim 1, wherein a high pressure check valve is disposed on an outlet conduit of the thermoacoustic compressor; and a low-pressure one-way valve is arranged on the return pipeline.
5. The thermoacoustic compressor driven multistage supersonic cryogenic refrigeration system according to any one of claims 1 to 4, further comprising a counter flow heat exchanger, said counter flow heat exchanger being disposed at least one of between said thermoacoustic compressor and said supersonic cyclone separator and between two adjacent supersonic cyclone separators, wherein piping at least one of between said thermoacoustic compressor and said supersonic cyclone separator and between two adjacent supersonic cyclone separators flows through a high temperature side of said counter flow heat exchanger, and said return piping flows through a low temperature side of said counter flow heat exchanger.
6. The thermoacoustic compressor driven multistage supersonic cryogenic refrigeration system of any one of claims 1 to 4, wherein the refrigerant of said refrigeration system comprises CO2Or H2O、N2Or Ar, Ne or H2And He.
7. The thermoacoustic compressor driven multistage supersonic cryogenic refrigeration system of claim 6, wherein the number of types of refrigeration media of said refrigeration system is greater than the number of said supersonic cyclones.
8. The thermoacoustic compressor driven multistage supersonic cryogenic refrigeration system according to any one of claims 1 to 4, wherein a diffuser is connected to an end of the supersonic cyclone separator, an outlet of the diffuser forming a gas outlet of the supersonic cyclone separator.
9. The multi-stage supersonic cryogenic refrigeration system driven by a thermoacoustic compressor according to claim 8, wherein the supersonic cyclone separator further comprises a cyclone device, a Laval nozzle expander and a cyclone gas-liquid separator connected in sequence, the cyclone gas-liquid separator is provided with a liquid collecting device, the liquid collecting device is provided with the liquid outlet, the gas outlet of the cyclone gas-liquid separator is connected to the inlet of the diffuser, and the outlet of the diffuser is connected with guide vanes.
10. The thermoacoustic compressor driven multistage supersonic cryogenic refrigeration system according to any one of claims 1 to 4, wherein said thermoacoustic compressor comprises a standing wave type thermoacoustic compressor or a traveling wave type thermoacoustic compressor.
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