CN113701382B - Mechanical compression type driven multistage supersonic speed low-temperature refrigeration system - Google Patents
Mechanical compression type driven multistage supersonic speed low-temperature refrigeration system Download PDFInfo
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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 mechanical compression type driven multistage supersonic speed low-temperature refrigeration system which comprises a compressor, a condenser, a counter-flow heat exchanger, a supersonic speed cyclone separator and an evaporator, wherein an outlet of the compressor is connected with an inlet of the condenser, an outlet of the condenser is connected with the supersonic speed cyclone separator, a gas outlet of the supersonic speed cyclone separator is connected with an inlet of the compressor through a return pipeline, an inlet of the evaporator is connected with a liquid outlet of the supersonic speed cyclone separator, and an 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 parts, the processing difficulty is low, and the operation reliability is greatly improved; compared with the traditional mixed working medium self-overlapping throttling refrigeration technology, the system has the advantages of environment-friendly working medium and higher expansion refrigeration efficiency.
Description
Technical Field
The invention relates to the technical field of refrigeration, in particular to a mechanical compression type driven multistage supersonic speed low-temperature refrigeration system.
Background
Throttling refrigeration technology, which utilizes the actual gas throttling characteristics for refrigeration, is one of the earliest refrigeration technologies used. 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. There are two different circulation modes for throttling-based refrigerators: a throttle cycle and a self-cascade cycle. The cascade refrigeration cycle includes a classical cascade refrigeration cycle and a self-cascade refrigeration cycle. The classical cascade refrigeration cycle system is complex, and requires more investment from design and manufacture to production and maintenance. Since the self-cascade refrigeration cycle is proposed for the first time in the thirties of the twentieth century, natural gas is successfully liquefied by using a nitrogen-hydrocarbon multi-component mixed working medium as a refrigerant.
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. Low temperatures can be achieved with turboexpanders and the technology of turboexpansion low temperatures is rapidly evolving. However, the traditional gas turbine expansion low-temperature technology has the hidden troubles of mechanical moving parts, high processing requirements, unreliable and unstable operation and the like.
Disclosure of Invention
The embodiment of the invention provides a mechanical compression type driven multistage supersonic speed low-temperature refrigeration system, which is used for solving or partially solving the problems of mechanical moving parts, high processing requirement, unreliable operation and unstable hidden trouble in the traditional gas turbine expansion low-temperature technology.
The embodiment of the invention provides a mechanical compression type driven multistage supersonic speed low-temperature refrigeration system which comprises a compressor, a condenser, supersonic speed cyclone separators and an evaporator, wherein an outlet of the compressor is connected with an inlet of the condenser, an outlet of the condenser is sequentially connected with at least one supersonic speed cyclone separator in series, a gas outlet of each supersonic speed cyclone separator is connected with an inlet of the compressor through a return pipeline, an inlet of the evaporator is connected with a liquid outlet of the supersonic speed cyclone separator, and an outlet of the evaporator is connected with the return pipeline.
On the basis of the scheme, when the outlet of the condenser 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 condenser is connected with a plurality of supersonic cyclone separators, the supersonic cyclone separators are connected with one evaporator.
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 condenser and the supersonic cyclone separator and between two adjacent supersonic cyclone separators, a pipeline at least one position between the condenser 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 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 Laval nozzle expander comprises a stabilizing section, a subsonic contraction section, a throat part and a supersonic expansion section which are sequentially connected, wherein the stabilizing section is connected with an outlet of the rotational flow device.
Compared with the traditional gas turbine expansion low-temperature technology, the supersonic cyclone separator has no moving parts, 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 diagram of a first connection of a multi-stage supersonic cryogenic refrigeration system in an embodiment of the present invention;
FIG. 2 is a schematic diagram of a second connection of a multi-stage supersonic cryogenic refrigeration system in an embodiment of the present invention;
FIG. 3 is a schematic diagram of the connection of a single stage supersonic cryogenic refrigeration system in 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:
1. a compressor; 11. a high power compressor; 2. a condenser; 21. a high-efficiency condenser; 3. a counter-flow heat exchanger; 31. a primary counter-flow heat exchanger; 32. a secondary counter-flow heat exchanger; 33. a third stage counter-current heat exchanger; 4. a supersonic cyclonic separator; 41. a first-stage supersonic cyclone separator, 42, a second-stage supersonic cyclone separator; 43. a three-stage supersonic cyclone separator; 401. a swirling device; 402. a Laval nozzle expander; 403. a cyclonic gas-liquid separator; 404. a diffuser; 405. a guide blade; 406. a liquid collection device; 4021. a stabilization section; 4022. a subsonic contraction section; 4023. a throat; 4024. a supersonic expansion section; 5. an evaporator; 51. a first-stage evaporator; 52. a secondary evaporator; 53. and a third-stage evaporator.
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 obtained by a person skilled in the art without inventive step based on the embodiments of the present invention, are within the scope of protection of the present invention.
Referring to fig. 1, the embodiment of the present invention provides a mechanical compression type driven multistage supersonic cryogenic refrigeration system, which includes a compressor 1, a condenser 2, a supersonic cyclone separator 4 and an evaporator 5. The outlet of the compressor 1 is connected to the inlet of the condenser 2. The outlet of the condenser 2 is sequentially connected with at least one supersonic cyclone separator 4 in series, and the gas outlet of the supersonic cyclone separator 4 is connected with the inlet of the compressor 1 through a return pipeline. The inlet of the evaporator 5 is connected to the liquid outlet of the supersonic cyclonic separator 4 and the outlet of the evaporator 5 is connected to the return line.
The supersonic cyclone separator 4 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 4 has both refrigeration effect and gas-liquid separation function, and the end is provided with a diffuser 404. The refrigeration system provided by the embodiment provides that the supersonic cyclone separator 4 is arranged to replace a gas turboexpansion device in the traditional refrigeration system. The cooling effect of the traditional throttling device is achieved by utilizing the refrigeration effect of the supersonic cyclone separator 4; 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 4. 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 4 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 4 does not have a rotating part per se) and long-term reliability.
Research shows that under the condition of the same pressure drop, the temperature drop in the supersonic cyclone separator 4 is larger than that of the traditional throttling devices such as a throttling valve, an expansion machine and a vortex tube, and the supersonic cyclone separator has a better refrigeration effect. In addition, the supersonic cyclone 4 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 404, and the pressure loss of the gas is greatly reduced.
On the basis of the above embodiment, further, with reference to fig. 1, a plurality of supersonic cyclones 4 are connected in series in sequence between the outlet of the condenser 2 and the inlet of the compressor 1. Multi-stage refrigeration is formed. The inlets and gas outlets of the plurality of supersonic cyclones 4 are connected end to end in sequence, and the gas outlet of the endmost supersonic cyclone 4 is connected to the inlet of the compressor 1 via a return line.
On the basis of the above embodiment, further, referring to fig. 1, a plurality of evaporators 5 are connected to the plurality of supersonic cyclone separators 4 in one-to-one correspondence. I.e. one evaporator 5 is connected to each supersonic cyclone 4. The plurality of evaporators 5 are connected to the return lines, respectively.
Alternatively, referring to FIG. 2, a plurality of supersonic cyclones 4 are commonly connected to an evaporator 5. That is, a plurality of supersonic cyclone separators 4 are connected to one evaporator 5, so that higher refrigerating capacity can be obtained. Further, as shown in FIG. 2, when a plurality of supersonic cyclones 4 are connected to one evaporator 5, the evaporator 5 may have a plurality of inlets connected to the plurality of supersonic cyclones 4 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 5, 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 4 one by one, and the plurality of outlets can be respectively connected with the return pipeline. The specific form and number of the evaporators 5 are not limited.
When a plurality of supersonic cyclone separators 4 are arranged, the refrigerating system adopts mixed working media. So that different supersonic cyclone separators 4 liquefy different working media to obtain different refrigeration temperatures. The refrigerating medium flows circularly in the loop to form cascade refrigerating circulation, and two or more different refrigerants may be used. 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.
The self-cascade refrigeration cycle has many advantages: firstly, only a single compressor 1 is adopted, so that the structure is compact and the control is simple; secondly, no moving part is arranged at the low-temperature end, 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 a low-pressure channel, namely a return pipeline, through throttling, solid phase precipitation at a low temperature is avoided, a throttling element is prevented from being 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.
On the basis of the above embodiment, further, referring to fig. 1 and fig. 3, a mechanical compression type driven supersonic cryogenic refrigeration system further comprises a counterflow heat exchanger 3. A counter-flow heat exchanger 3 is arranged at least at one position between the condenser 2 and the supersonic cyclone separator 4 and between two adjacent supersonic cyclone separators, wherein at least one position between the condenser 2 and the supersonic cyclone separator 4 and between two adjacent supersonic cyclone separators 4 is provided with a pipeline which flows through the high-temperature side of the counter-flow heat exchanger 3, and a return pipeline flows through the low-temperature side of the counter-flow heat exchanger 3.
The high temperature side of the counterflow heat exchanger 3, 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 3, i.e. the side with lower temperature, is the cold source in the heat exchanger. Specifically, a counter-flow heat exchanger 3 may be provided between the condenser 2 and the supersonic cyclone 4; a counter-flow heat exchanger 3 can also be arranged between two adjacent supersonic cyclone separators 4; a counter-flow heat exchanger 3 may also be provided between the condenser 2 and the supersonic cyclone 4 and between two adjacent supersonic cyclones 4. The arrangement of the countercurrent heat exchanger 3 is beneficial to 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 rest (Ar or N)2Ne 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 refrigerant of the refrigeration system is larger than the number of supersonic cyclone separators 4. Namely, the specific number of the refrigeration working mediums is at least the same as the number of the supersonic cyclone separators 4, and different kinds of working mediums in the refrigeration working mediums have different liquefaction temperatures. Thus liquefying one working medium at each supersonic cyclone 4, and obtaining different refrigeration temperature gradients by liquefying different working media in different supersonic cyclones 4.
This embodiment is directed at the following problem that current cryogenic refrigeration technology exists: the traditional mixed working medium self-cascade throttling refrigeration technology has the problems that the working medium is not environment-friendly and the like; the traditional gas turbine expansion low-temperature technology has the hidden dangers of mechanical moving parts, high processing requirements, unreliable and unstable operation and the like. The embodiment provides a method and a system for realizing mechanical compression type driven multistage supersonic speed low-temperature refrigeration, wherein the system adopts CO2、N2(or Ar), ne (or H)2) The mixed gas of He and the like is used as the circulating working medium, so that closed low-temperature refrigeration circulation in the temperature range of 120K-20K can be realized, the working medium is environment-friendly, and the expansion refrigeration efficiency is higher; the multistage supersonic cyclone separator 4 based on supersonic refrigeration effect is used as an expansion cooling element, and 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 4 does not rotate per se)Parts), long-term reliability, etc.
Compared with the traditional mixed working medium self-overlapping throttling refrigeration technology, the working medium adopted by the system is environment-friendly, and the expansion refrigeration efficiency is higher; compared with the traditional gas turbine expansion low-temperature technology, the supersonic cyclone separator 4 has no moving part, the processing difficulty is low, and the operation reliability and the stability are greatly improved.
In addition to the above embodiments, a diffuser 404 is connected to the end of the supersonic cyclone 4, and the outlet of the diffuser 404 forms the gas outlet of the supersonic cyclone 4. The supersonic cyclone 4 has a liquid outlet connected to the inlet of the evaporator 5, and the uncondensed gaseous working medium in the supersonic cyclone 4 directly enters the diffuser 404 and is discharged. The supersonic cyclone 4 has the function of gas-liquid separation. A liquid outlet is provided before the diffuser 404 for the outflow of liquid. The temperature of the refrigeration working medium introduced into the supersonic cyclone separator 4 is further reduced, and the refrigeration working medium liquid generated after the temperature is reduced and liquefied is converged and flows out from the liquid outlet; the refrigerant gas that is not liquefied flows directly into the diffuser 404, joins the refrigerant flowing back from the evaporator 54, and expands the refrigerant.
On the basis of the above embodiment, the supersonic cyclone separator 4 further includes a cyclone device 401, a Laval nozzle expander 402 and a cyclone gas-liquid separator 403 which are connected in sequence, the cyclone gas-liquid separator 403 is provided with a liquid collecting device 406, the liquid collecting device 406 is provided with a liquid outlet, the gas outlet of the cyclone gas-liquid separator 403 is connected to the inlet of a diffuser 404, and the outlet of the diffuser 404 is connected to a guide vane 405.
Based on the above embodiment, further, the Laval nozzle expander 402 comprises a stabilizing section 4021, a subsonic convergent section 4022, a throat section 4023 and a supersonic divergent section 4024 connected in series, wherein the stabilizing section 4021 is connected to the outlet of the swirling device 401.
Referring to FIG. 4, the supersonic cyclonic separator 4 is generally comprised of 4 sections including a cyclone device 401, a Laval nozzle expander 402, a cyclone gas-liquid separator 403, and a diffuser 404. Both gas expansion refrigeration and liquefaction processes occur primarily within the Laval nozzle expander 402. Laval nozzle expander 402 may be divided into 4 sections, including a stabilizing section 4021, a subsonic convergent section 4022, a throat section 4023, and a supersonic divergent section 4024. The working principle is as follows: the gas enters the cyclone device 401 to rotate, and has a certain acceleration; the gas is expanded to supersonic speed rapidly in a Laval nozzle expander 402 to form a low-temperature and 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 velocity generated by rotation and strong cyclone field centrifugal force, discharged from a special liquid outlet in the cyclone gas-liquid separator 403, and gas is discharged through a diffuser 404 to realize gas-liquid separation; after the speed reduction, the pressure increase and the temperature rise of the diffuser 404, the pressure loss of the gas through the supersonic cyclone separator 4 can be mostly recovered, and the pressure loss of the gas is greatly reduced.
On the basis of the above embodiments, fig. 1 further provides a method and a system for implementing mechanical compression-driven multistage supersonic cryogenic refrigeration. The system mainly comprises a compressor 1, a condenser 2, a counter-current heat exchanger 3, a supersonic cyclone separator 4 and an evaporator 5. The counter-flow heat exchanger 3 is composed of a primary counter-flow heat exchanger 31, a secondary counter-flow heat exchanger 32 and a tertiary counter-flow heat exchanger 33 which are all identical. Supersonic cyclone 4 is composed of identical first-stage supersonic cyclone 41, second-stage supersonic cyclone 42, and third-stage supersonic cyclone 43. Each stage of supersonic cyclone separator 4 consists of a cyclone device 401, a Laval nozzle expander 402, a cyclone gas-liquid separator 403, a diffuser 404, guide vanes 405 and a liquid collecting device 406. Laval nozzle expander 402 is comprised of a stabilizing section 4021, a subsonic convergent section 4022, a throat 4023, and a supersonic divergent section 4024. The evaporator 5 is composed of a first-stage evaporator 51, a second-stage evaporator 52, and a third-stage evaporator 53 which are identical. 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), mixed gas such as He is taken as the cycle working medium, and closed low-temperature refrigeration cycle within the range of 120K-20K can be realized.
When the system is in operation, the system is,compressor 1 compresses low-temperature and low-pressure CO2、N2(Ar)、Ne(H2) He mixed vapor is sucked back from a low-pressure channel, namely a return pipeline, and forms high-temperature and high-pressure CO after compression2、N2(Ar)、Ne(H2) And He mixed gas. The condenser 2 cools the high-temperature high-pressure mixed gas discharged from the compressor 1, releases heat, and forms a gas-liquid mixture after passing through the first-stage counter-flow heat exchanger 31, and the gas-liquid mixture enters the first-stage supersonic cyclone 41.CO 22、N2(Ar)、Ne(H2) The He gas-liquid mixture enters a first-stage supersonic cyclone separator 41, firstly forms a cyclone flow state after passing through a cyclone device 401, then enters a Laval nozzle expander 402, and flows through a stable section 4021, a subsonic contraction section 4022, a throat 4023 and a supersonic expansion section 4024 in sequence, the gas-liquid mixture is suddenly expanded to supersonic speed in the Laval nozzle expander 402 to generate a refrigeration effect, and a low-temperature low-pressure environment (the temperature is reduced because part of the heat of the gas is converted into kinetic energy) and high-boiling-point CO is formed2Firstly, condensation liquefaction is carried out, and CO is generated under the action of tangential velocity generated by rotation and centrifugal force of strong rotational flow field2The droplets are thrown to the tube wall, discharged by a special liquid collecting device 406 in the cyclone gas-liquid separator 403, enter the primary evaporator 51, and are evaporated (boiled) in the primary evaporator 51 into CO2Vapour, 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 51 into a low-pressure passage.
The remaining N2(Ar)、Ne(H2) The mixed gas of He and He flows out of the first-stage supersonic cyclone 41 through the diffuser 404 and the guide vanes 405 and enters the second-stage counter-current heat exchanger 32. 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 after the secondary refrigeration, N2(Ar) is condensed and evaporated (boiled) in the secondary evaporator 52 to become N2The (Ar) vapor, absorbing heat from the environment or the substance to be cooled, exits the secondary evaporator 52 into a low pressure channel. Warp beamAfter passing through three-stage refrigeration Ne (H)2) Condensed and evaporated (boiled) in the three-stage evaporator 53 to Ne (H)2) The vapor, absorbing the heat of the environment or the substance to be cooled, exits the tertiary evaporator 53 into the low pressure passage, thereby forming a closed refrigeration cycle.
The multi-stage refrigeration system adopts CO2、N2(Ar)、Ne(H2) The mixed gas of He and the like is used as the circulating working medium, so that closed low-temperature refrigeration circulation in the temperature range of 120K-20K can be realized, the working medium is environment-friendly, and the expansion refrigeration efficiency is higher; the multi-stage 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 to specific refrigeration requirements; the mixed working medium adopted in the system can be selected and proportioned according to the specific refrigeration requirement.
On the basis of the above embodiments, further, fig. 3 provides a method and a system for implementing single-stage supersonic cryogenic refrigeration driven by mechanical compression. Unlike the embodiment shown in FIG. 1, this embodiment employs a high power compressor 11 and a high efficiency condenser 21, using H2And the mixed gas and the He binary gas are subjected to refrigeration cycle, the structure is simple and compact, and the low-temperature refrigeration of a 20K temperature zone can be realized.
When the system is working, the high-power compressor 11 will be used for compressing H with low temperature and low pressure2The mixed vapor of He and H is sucked back from the low-pressure channel and compressed to form H with high temperature and high pressure2And He binary mixed gas. The high-efficiency condenser 21 cools the high-temperature high-pressure mixed gas discharged by the high-power compressor 11, releases heat, and fully exchanges heat through the counter-flow heat exchanger 3 to form a gas-liquid mixture which enters the supersonic cyclone separator 4.H2The He gas-liquid mixture enters a supersonic cyclone separator 4, firstly forms a cyclone flow state after passing through a cyclone device 401, and then enters a Laval nozzle expander 402, the mixture flows through the stable section 4021, the subsonic contraction section 4022, the throat 4023 and the supersonic expansion section 4024 in sequence, and the gas-liquid mixture is rapidly expanded to supersonic speed in the Laval nozzle expander 402 to generate a refrigeration effect, so that a low-temperature and low-pressure environment (the temperature is reduced because part of the heat of the gas is converted into kinetic energy) is formed (H is the heat of part of the gas is converted into kinetic energy)2Condensation and liquefaction occur, and H is generated under the action of tangential velocity generated by rotation and centrifugal force of strong rotational flow field2The droplets are thrown to the tube wall, discharged by a special liquid collecting device 406 in the cyclone gas-liquid separator 403, enter the evaporator 5, and are evaporated (boiled) in the evaporator 5 into H2The vapour, absorbing the heat of the environment or the substance to be cooled, bringing the temperature of the environment or the substance to be cooled down, H2The vapor is discharged from the evaporator 5, enters a low-pressure channel, and is sucked into the high-power compressor 11 after being subjected to full heat exchange by the counter-flow heat exchanger 3. The rest He gas passes through a diffuser 404, stably flows out of the supersonic cyclone separator 4 through guide vanes 405, enters a low-pressure passage, is fully subjected to heat exchange through a counter-flow heat exchanger 3, and is sucked into the high-power compressor 11, so that a closed refrigeration cycle is formed.
After the speed reduction, the pressure increase and the temperature rise of the diffuser, most of the pressure energy lost by the gas through the supersonic cyclone separator can be recovered, and the pressure loss of the gas is greatly reduced. It should be emphasized that this embodiment is merely illustrative of a simple configuration, and that the high capacity compressor and high efficiency condenser employed in the system may be selected according to the particular refrigeration requirements; the mixed working medium adopted in the system can be selected and proportioned according to the specific refrigeration requirement.
The mechanical compression type driven multistage supersonic speed low-temperature refrigeration system provided in each embodiment adopts CO2、N2(Ar)、Ne(H2) The mixed gas of He and the like is used as the circulating working medium, so that closed low-temperature refrigeration circulation in the temperature range of 120K-20K can be realized, the working medium is environment-friendly, and the expansion refrigeration efficiency is higher; the multistage supersonic cyclone separator based on supersonic speed refrigeration effect is used as an expansion cooling element, and 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 (supersonic speed refrigeration effect)The fast cyclone separator has no rotating part per se), and is reliable for a long time. Compared with the traditional mixed working medium self-cascade throttling refrigeration technology, the working medium adopted by the system is environment-friendly, and the expansion refrigeration efficiency is higher; compared with the traditional gas turbine expansion low-temperature technology, the supersonic cyclone separator has no moving parts, low processing difficulty and greatly improved operation reliability and stability.
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 (7)
1. A mechanical compression type driven multistage supersonic speed low-temperature refrigeration system is characterized by comprising a compressor, a condenser, supersonic speed cyclone separators and an evaporator, wherein an outlet of the compressor is connected with an inlet of the condenser, an outlet of the condenser is sequentially connected with at least one supersonic speed cyclone separator in series, a gas outlet of each supersonic speed cyclone separator is connected with an inlet of the compressor through a return pipeline, an inlet of the evaporator is connected with a liquid outlet of each supersonic speed cyclone separator, and an outlet of the evaporator is connected with the return pipeline;
the condenser is arranged between the supersonic cyclone separators and at least one position between two adjacent supersonic cyclone separators is provided with the counter-flow heat exchanger, wherein at least one position between the condenser and the supersonic cyclone separators and between two adjacent supersonic cyclone separators is provided with a pipeline flowing 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;
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.
2. The mechanical compression-driven multistage supersonic cryogenic refrigeration system of claim 1, wherein when a plurality of supersonic cyclones are connected to the outlet of the condenser, a plurality of evaporators are connected to the plurality of supersonic cyclones in a one-to-one correspondence.
3. The mechanical compression-driven multistage supersonic cryogenic refrigeration system of claim 1, wherein when a plurality of said supersonic cyclones are connected to an outlet of said condenser, a plurality of said supersonic cyclones are connected in common to one said evaporator.
4. The mechanical compression-driven multistage supersonic cryogenic refrigeration system according to any one of claims 1 to 3, wherein the refrigerant of the refrigeration system comprises CO2Or H2O、N2Or Ar, ne or H2And He.
5. The mechanical compression-driven multistage supersonic cryogenic refrigeration system of claim 4, wherein the number of types of refrigeration media of the refrigeration system is greater than the number of supersonic cyclones.
6. The mechanical compression-driven multistage supersonic cryogenic refrigeration system according to claim 1, wherein the supersonic cyclone separator further comprises a cyclone device, a Laval nozzle expander and a cyclone gas-liquid separator which are connected in sequence, a liquid collection device is arranged on the cyclone gas-liquid separator, the liquid collection device is provided with the liquid outlet, 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.
7. The mechanical compression-driven multistage supersonic cryogenic refrigeration system of claim 6, wherein said Laval nozzle expander comprises a stabilizing section, a subsonic constriction section, a throat section and a supersonic expansion section connected in series, wherein said stabilizing section is connected to the outlet of said swirling device.
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| CN102268309A (en) * | 2011-07-18 | 2011-12-07 | 中国石油大学(北京) | Full liquefaction process for natural gas by using supersonic speed cyclone separator |
| CN105546863A (en) * | 2015-12-12 | 2016-05-04 | 西安交通大学 | Auto-cascade single-temperature or double-temperature refrigeration cycle system adopting ejector for synergism |
| CN205316733U (en) * | 2015-12-30 | 2016-06-15 | 深圳市富达冷冻设备有限公司 | Automatic cascade refrigeration system of level four |
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| JPH0960992A (en) * | 1995-08-29 | 1997-03-04 | Mitsubishi Heavy Ind Ltd | Refrigerating device |
| JP5197820B2 (en) * | 2011-09-12 | 2013-05-15 | 三菱電機株式会社 | Refrigeration cycle equipment |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN102268309A (en) * | 2011-07-18 | 2011-12-07 | 中国石油大学(北京) | Full liquefaction process for natural gas by using supersonic speed cyclone separator |
| CN105546863A (en) * | 2015-12-12 | 2016-05-04 | 西安交通大学 | Auto-cascade single-temperature or double-temperature refrigeration cycle system adopting ejector for synergism |
| CN205316733U (en) * | 2015-12-30 | 2016-06-15 | 深圳市富达冷冻设备有限公司 | Automatic cascade refrigeration system of level four |
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