CN113028668B - Micro-channel near-isothermal compression type transcritical carbon dioxide circulating system and method - Google Patents
Micro-channel near-isothermal compression type transcritical carbon dioxide circulating system and method 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
- F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
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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
- F25B29/00—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously
- F25B29/003—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously of the compression type system
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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
- F25B31/00—Compressor arrangements
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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
- F25B39/00—Evaporators; Condensers
- F25B39/02—Evaporators
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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
- F25B40/00—Subcoolers, desuperheaters or superheaters
- F25B40/06—Superheaters
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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
- F25B41/00—Fluid-circulation arrangements
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- 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
- F25B49/00—Arrangement or mounting of control or safety devices
- F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
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Abstract
The invention provides a micro-channel near-isothermal compression type transcritical carbon dioxide circulating system and a method, wherein the system comprises: the low-pressure outlet of the heat regenerator is connected with the central inlet of a centrifugal impeller through an isothermal compression air suction pipe, the circumferential outlet of the centrifugal impeller is connected with the inlets of a plurality of convergent-divergent micro-channel heat exchangers, the outlet of the convergent-divergent micro-channel heat exchanger is connected with the inlet of an air collector, the outlet of the air collector is connected with the inlet of an auxiliary gas cooler through an isothermal compression exhaust pipe, and the outlet of the auxiliary gas cooler is connected with the high-pressure inlet of the heat regenerator; the high-pressure outlet of the heat regenerator is connected with the inlet of the evaporator through an electronic expansion valve, and the outlet of the evaporator is connected with the inlet of the gas-liquid separator; and a gas outlet of the gas-liquid separator is connected with a low-pressure inlet of the heat regenerator. The invention uses the near-isothermal compression process to replace the conventional near-isentropic compression process, thereby not influencing the transcritical CO2The power consumption of the compressor is obviously reduced on the premise of the refrigerating capacity of the system, so that the cycle energy efficiency ratio is greatly improved.
Description
Technical Field
The invention belongs to the technical field of refrigeration and heat pumps, and relates to a micro-channel near-isothermal compression type transcritical carbon dioxide circulating system and a method.
Background
After global ozone layer protection has been first achieved, intense temperatureThe control and reduction of the chamber effect gas become the main content of technical transformation of the refrigeration industry, and in the background, the gas is used as a pure natural working medium, namely CO2The view of the public is regressed. Compared with other alternatives such as CFC, HCFC refrigerant, HFC refrigerant with extremely high greenhouse effect index and the like which have extremely destructive power to the ozone layer, CO2The working medium is the only non-toxic and non-flammable refrigerant substitution scheme with ODP (ozone destruction index) of 0, extremely low GWP (greenhouse effect index) and good low-temperature fluidity/heat exchange performance. At the same time, when CO2After the transcritical operation mode of the working medium is proposed, the transcritical CO is subjected to unique advantages of incomparable high-temperature heating performance, low-environment temperature adaptability and the like2The technology can meet most of refrigerating and heating requirements in the industrial, commercial and civil range.
Although considering the aspects of environmental protection, economy and the like, transcritical CO2The technology has very wide application prospect in the fields of vehicle air conditioning, building heating and hot water supply, drying industry, commercial super-cold chain, ice and snow movement and other cold and hot comprehensive supply in the traffic field, however, the technology still has certain performance short plates under most specific working conditions, and under some working conditions, transcritical CO exists2The energy efficiency of the circulation full-working-condition refrigeration is only about 80 percent of that of the traditional R134a and R407C systems, which is transcritical CO2The most major technical bottleneck of refrigeration and heating technology still faces before large-scale popularization.
Disclosure of Invention
The invention aims to provide a micro-channel near-isothermal compression type transcritical carbon dioxide circulating system and method, in the conventional transcritical CO2In circulation, a method for realizing a near-isothermal compression process instead of a conventional near-isentropic compression process is adopted, so that transcritical CO is not influenced2The power consumption of the compressor is obviously reduced on the premise of the refrigerating capacity of the system, the energy efficiency ratio of the cycle is greatly improved, and the practical problem that the performance coefficients of the conventional transcritical CO2 refrigerating and heating technology application means are poor under more working conditions is finally solved.
In order to achieve the purpose, the invention adopts the following technical scheme:
a microchannel near-isothermal compression type transcritical carbon dioxide circulation system comprises: the device comprises a heat regenerator, an electronic expansion valve, an evaporator, a gas-liquid separator, an auxiliary gas cooler, a gas collector, a scaling type micro-channel heat exchanger and a centrifugal impeller;
the low-pressure outlet of the heat regenerator is connected with the central inlet of a centrifugal impeller through an isothermal compression air suction pipe, the circumferential outlet of the centrifugal impeller is connected with the inlets of a plurality of convergent-divergent micro-channel heat exchangers, the outlet of the convergent-divergent micro-channel heat exchanger is connected with the inlet of an air collector, the outlet of the air collector is connected with the inlet of an auxiliary gas cooler through an isothermal compression exhaust pipe, and the outlet of the auxiliary gas cooler is connected with the high-pressure inlet of the heat regenerator; the high-pressure outlet of the heat regenerator is connected with the inlet of the evaporator through an electronic expansion valve, and the outlet of the evaporator is connected with the inlet of the gas-liquid separator; and a gas outlet of the gas-liquid separator is connected with a low-pressure inlet of the heat regenerator.
The invention further improves the following steps: the evaporator is provided with an axial flow fan, and an air flow channel driven by the axial flow fan of the evaporator is a gap between the finned tubes of the evaporator.
The invention further improves the following steps: the auxiliary gas cooler and the scaling type micro-channel heat exchanger in the isothermal compressor are jointly provided with an axial flow fan, an air channel in the auxiliary gas cooler is a gap between finned tubes, and an air channel in the scaling type micro-channel heat exchanger is a gap between micro-channel fins.
The invention further improves the following steps: an air passage passing air valve is arranged between the air passage in the auxiliary gas cooler and the air passage in the convergent-divergent micro-channel heat exchanger.
The invention further improves the following steps: the air valve is in a complete closing mode, and air flow channels among the fins of the scaling type microchannel heat exchanger are completely cut off; low pressure CO2The gas enters a centrifugal impeller of an isothermal compressor through a gas suction pipe of the compressor to be accelerated to a supersonic state, and then enters a scaling type micro-channel heat exchanger in a high-speed state, and high-speed CO (carbon monoxide)2And in the processes of speed reduction and pressure increase, the pressure increase of the gas is realized according to the near-isentropic compression process.
The invention further improves the following steps: the air valve is in the fully open mode, zoomingAir flow channels among fins of the heat exchanger with the micro-channels are completely opened; low pressure CO2The gas enters a centrifugal impeller of the isothermal compressor through the isothermal compression gas suction pipe to be accelerated to a supersonic speed state, and then enters the scaling type microchannel heat exchanger to realize the processes of speed reduction, pressurization and quick heat release, so that kinetic energy is converted into pressure energy in a near-isothermal compression mode.
A microchannel near-isothermal compression type transcritical carbon dioxide circulation method comprises the following steps:
low pressure CO2The gas enters a centrifugal impeller of the isothermal compressor through the isothermal compression air suction pipe to be accelerated to a supersonic speed state, then enters the scaling type microchannel heat exchanger, and the outlet of the scaling type microchannel heat exchanger is pressurized to CO in a high-pressure state2The gas is collected by the gas collector, enters the auxiliary gas cooler through the isothermal compression exhaust pipe, exchanges heat with the refrigerant in the gas suction state, is throttled to the low pressure state through the electronic expansion valve, provides refrigerating capacity in the evaporator, and then enters the gas suction pipe of the isothermal compressor again after passing through the gas-liquid separator and the heat regenerator, so that circulation is realized.
Compared with the prior art, the invention has the following advantages:
1. creatively provides that the near-isothermal compression process is adopted to replace the traditional near-isentropic compression process, and the transcritical CO is obviously reduced on the premise of not reducing the circulating refrigeration capacity2The power consumption of the circulating compressor is greatly improved to cross-critical CO2Theoretical performance of the cycle, transcritical CO2The performance improvement in each application field provides a sufficient theoretical basis;
2. creatively converts the isothermal compression process from the traditional positive displacement compressor into a form of a centrifugal impeller and a scaling type microchannel flow channel, and skillfully converts the CO through the conversion between kinetic energy and pressure energy2Two relatively independent processes of pressure increase and full heat release of gas can occur in the same flow channel at the same time, so that the near-isothermal compression which generally only stays at a theoretical layer can be realized in reality;
3. creatively provides isothermal compression type transcritical CO2Method for calculating circulating near-isothermal compression workThe main performance index calculation method, the optimum exhaust pressure of the isothermal compression cycle and other concepts are convenient for accurately predicting the isothermal compression transcritical CO in industrial application2The main properties of the cycle;
4. creatively provides isothermal compression type transcritical CO2The method for switching the circulating operation mode can realize the switching of the circulation from the high-efficiency refrigeration mode to the strong-efficiency heating mode through the mode switching, so that the isothermal compression type transcritical CO is subjected to2The system can simultaneously take refrigeration and heating working conditions into consideration, and the maximum value of comprehensive energy efficiency is achieved;
5. creatively provides isothermal compression type transcritical CO2The method for controlling the rotating speed of the centrifugal impeller in the circulation in real time can ensure that the isothermal compressor can ensure CO in any air inlet state2When the gas flows to the throat part of the convergent-divergent microchannel heat exchange tube, the local sound velocity is exactly reached, so that high-speed CO can be ensured2The gas always generates supersonic speed pressurization in the reducing section of the heat exchange tube of the scaling type microchannel, and generates subsonic speed pressurization in the gradually expanding section, so that the failure conditions of pressure reduction and the like can not occur.
Drawings
The accompanying drawings, which are incorporated in and constitute a part of this application, illustrate embodiments of the invention and, together with the description, serve to explain the invention and not to limit the invention. In the drawings:
FIG. 1 is a schematic structural diagram of a microchannel near-isothermal compression type transcritical carbon dioxide circulation system of the present invention;
FIG. 2 is a T-S diagram of a micro-channel near-isothermal compression type transcritical carbon dioxide circulation system.
Detailed Description
The present invention will be described in detail below with reference to the embodiments with reference to the attached drawings. It should be noted that the embodiments and features of the embodiments in the present application may be combined with each other without conflict.
The following detailed description is exemplary in nature and is intended to provide further details of the invention. Unless otherwise defined, all technical terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this application belongs. The terminology used herein is for the purpose of describing particular embodiments only and is not intended to be limiting of exemplary embodiments according to the invention.
Example 1
Referring to fig. 1, the invention provides a microchannel near-isothermal compression type transcritical carbon dioxide circulation system, including: the device comprises a heat regenerator 1, an electronic expansion valve 2, an evaporator 3, a gas-liquid separator 4, an axial flow fan 5, an auxiliary gas cooler 6, an air valve 7, a gas collector 8, a convergent-divergent micro-channel heat exchanger 9 and a centrifugal impeller 10.
In the invention, a low-pressure outlet of a heat regenerator 1 is connected with a central inlet of a centrifugal impeller 10 through an isothermal compression air suction pipe, a circumferential outlet of the centrifugal impeller 10 is connected with inlets of a plurality of scaling type micro-channel heat exchangers 9, outlets of the scaling type micro-channel heat exchangers 9 are connected with an inlet of an air collector 8, an outlet of the air collector 8 is connected with an inlet of an auxiliary gas cooler 6 through an isothermal compression exhaust pipe, and an outlet of the auxiliary gas cooler 6 is connected with a high-pressure inlet of the heat regenerator 1; the high-pressure outlet of the heat regenerator 1 is connected with the inlet of an evaporator 3 through an electronic expansion valve 2, and the outlet of the evaporator 3 is connected with the inlet of a gas-liquid separator 4; and a gas outlet of the gas-liquid separator 4 is connected with a low-pressure inlet of the regenerator 1.
Example 2
In the circulating system, an evaporator 3 is provided with an axial flow fan, an air flow channel driven by the axial flow fan of the evaporator is a gap between finned tubes of the evaporator 3, an auxiliary gas cooler 6 and a retractable micro-channel heat exchanger 9 in an isothermal compressor are provided with the axial flow fan 5 together, an air channel in the auxiliary gas cooler 6 is a gap between the finned tubes, and an air channel in the retractable micro-channel heat exchanger 9 is a gap between the micro-channel fins; an air passage passing air valve 7 is arranged between an air passage in the auxiliary gas cooler 6 and an air passage in the convergent-divergent micro-channel heat exchanger 9; the air duct in the scaling type micro-channel heat exchanger 9 realizes stepless regulation of air quantity through the air valve 7.
Example 3
Low pressure CO in the circulating system of the invention2After the gas enters the isothermal compressor through the isothermal compression air suction pipeThe kinetic energy is converted into pressure energy in the form of near isothermal compression by first accelerating to supersonic state by centrifugal impeller 10, see state 1 to state 2 in fig. 2, and then entering scaled microchannel heat exchanger 9 to realize the processes of speed reduction, pressure increase and rapid heat release, see state 2 to state 3 in fig. 2.
According to the micro-channel near-isothermal compression type transcritical carbon dioxide circulation method, due to the fact that heat exchange temperature difference exists in the scaling type micro-channel heat exchanger 9 in practical application, CO in a tube cannot be recycled2The gas is cooled to room temperature and therefore the pressurisation process can only be regarded as a near isothermal compression process. Subsequently, the outlet of the plurality of the convergent-divergent micro-channel heat exchangers 9 is pressurized to CO in a high-pressure state2The gas is collected by the gas collector 8 and then enters the auxiliary gas cooler 6 through the isothermal compression exhaust pipe to exchange heat with the room temperature again, which is shown in the state 3 to the state 4 in fig. 2. Then, supercritical CO2The gas exchanges heat with the refrigerant in a gas suction state through the heat regenerator 1 (see state 4 to state 5 in fig. 2), then is throttled to a low-pressure state through the electronic expansion valve 2 (see state 5 to state 6 in fig. 2), provides refrigerating capacity in the evaporator 3 (see state 6 to state 7 in fig. 2), absorbs heat through the gas-liquid separator 4 and the heat regenerator 1 (see state 7 to state 1 in fig. 2), and then enters the gas suction pipe of the isothermal compressor again to realize circulation.
The circulation system of the invention has the following main performance indexes: the method comprises the following steps of calculating the performance indexes of refrigerating capacity, heating capacity, compressor power consumption, total power consumption, refrigerating energy efficiency ratio, heating energy efficiency ratio and isothermal compression efficiency:
power consumption W of isothermal compression processpol：
The suction and exhaust state parameters can be directly read by a temperature and pressure sensor; while the compression factor Z1And Z3The pressure and temperature values of the isothermal compression air suction state and the exhaust state can be found in a general compression factor table;
isothermal compression type transcritical CO2Circulating refrigerating capacity:
isothermal compression type transcritical CO2Cyclic heating quantity:
isothermal compression type transcritical CO2And circulating total power consumption: wtot＝Wpol+Wfan；
Isothermal compression type transcritical CO2Energy efficiency ratio of circulating refrigeration: COPc＝Qc/Wtot；
Isothermal compression type transcritical CO2The energy efficiency ratio of circulating heating is as follows: COPh＝Qh/Wtot；
Isothermal compression type transcritical CO2Cyclic isothermal compression efficiency:
wherein the content of the first and second substances,
is the refrigerant flow, p is the pressure, v is the specific volume, T is the temperature, h is the enthalpy, WfanSubscripts 1-7 are the state point numbers for fan power.
Example 4
The invention relates to a circulating system, which inevitably has an optimal exhaust pressure under a specific working condition, so that the circulating refrigeration and heating energy efficiency ratio under the exhaust pressure is maximum, when the exhaust pressure is higher or lower than the optimal value, the circulating refrigeration and heating energy efficiency ratio is reduced, meanwhile, the optimal exhaust pressure is obviously influenced by the working condition, so that the optimal exhaust pressure presents different values under different running conditions, the prediction method of the optimal exhaust pressure is determined by taking the refrigerant temperature and pressure parameters of an isothermal compressor suction, a centrifugal impeller outlet and an auxiliary gas cooler outlet and the isothermal compression efficiency as independent variables, and the specific form of the formula can be fully determined based on limited tests by controlling a variable method and combining the configuration condition of an actual prototype:
Popt＝f(p1,p2,p4,T1,T2,T4,ηit)
example 5
The circulating system can realize the switching from a common refrigeration mode to a forced heating mode, when the circulation needs to realize the forced heating mode under a certain working condition, the air valve 7 is adjusted to be in a complete closing mode, the air flow channel between the fins of the convergent-divergent micro-channel heat exchanger 9 is completely cut off, and under the condition, low-pressure CO is used2After entering the compressor part through the suction pipe of the compressor, the gas is firstly accelerated to a supersonic speed state through a centrifugal impeller 10 and then enters a scaling type micro-channel heat exchanger 9 in a high-speed state, and because an air circulation channel between fins of the micro-channel heat exchanger is cut off, high-speed CO (carbon monoxide)2The gas can not realize the heat release process in the speed reduction and pressure increase processes, so the pressure increase is realized according to the near isentropic compression process, the near isothermal compressor is converted into the near isentropic compressor, and the compression power consumption and the cyclic heating capacity are greatly improved.
Example 6
The circulating system ensures that the isothermal compressor can enable CO to be in any air suction state of different modes, different working conditions and the like2The invention provides a method for controlling the rotating speed of a centrifugal impeller, namely the outlet speed of the centrifugal impeller 10 in real time, wherein the real-time speed set value of the centrifugal impeller 10 is based on the outlet temperature and pressure parameters of the centrifugal impeller of an isothermal compressor, the isentropic efficiency of the diffusion process of the scaling type microchannel heat exchanger, the equivalent diameter of an inlet of the scaling type microchannel heat exchanger, the equivalent diameter of the throat of the scaling type microchannel heat exchanger, the equivalent area of an inlet and an outlet of an accelerating channel of the centrifugal impeller and the isothermal compression efficiency are self-variableThe amount is determined, and the specific form of the formula can be fully determined based on limited tests by controlling a variable method and combining the configuration condition of an actual prototype:
ncen＝f(p2,T2,ηis,Ain,Aout,dp,in,dp,throat)
wherein eta isisIs the isentropic efficiency of the diffusion process of a scaling type micro-channel heat exchanger 9, AinIs the equivalent area of the inlet of the acceleration channel of the centrifugal impeller, AoutFor equivalent area of the outlet of the acceleration channel of the centrifugal impeller, dp,inIs the equivalent diameter of the inlet of a scaled micro-channel heat exchanger 9, dp,throatIs the equivalent diameter of the throat of the scaled microchannel heat exchanger 9.
It will be appreciated by those skilled in the art that the invention may be embodied in other specific forms without departing from the spirit or essential characteristics thereof. The embodiments disclosed above are therefore to be considered in all respects as illustrative and not restrictive. All changes which come within the scope of or equivalence to the invention are intended to be embraced therein.
Claims (7)
1. A microchannel near-isothermal compression type transcritical carbon dioxide circulation system is characterized by comprising: the system comprises a heat regenerator (1), an electronic expansion valve (2), an evaporator (3), a gas-liquid separator (4), an auxiliary gas cooler (6), a gas collector (8), a convergent-divergent micro-channel heat exchanger (9) and a centrifugal impeller (10);
a low-pressure outlet of the heat regenerator (1) is connected with a central inlet of a centrifugal impeller (10) through an isothermal compression air suction pipe, a circumferential outlet of the centrifugal impeller (10) is connected with inlets of a plurality of scaling-type micro-channel heat exchangers (9), outlets of the scaling-type micro-channel heat exchangers (9) are connected with an inlet of an air collector (8), an outlet of the air collector (8) is connected with an inlet of an auxiliary gas cooler (6) through an isothermal compression exhaust pipe, and an outlet of the auxiliary gas cooler (6) is connected with a high-pressure inlet of the heat regenerator (1); a high-pressure outlet of the heat regenerator (1) is connected with an inlet of the evaporator (3) through the electronic expansion valve (2), and an outlet of the evaporator (3) is connected with an inlet of the gas-liquid separator (4); the gas outlet of the gas-liquid separator (4) is connected with the low-pressure inlet of the heat regenerator (1).
2. The micro-channel near-isothermal compression type transcritical carbon dioxide circulation system according to claim 1, wherein the evaporator (3) is provided with an axial flow fan, and an air flow channel driven by the axial flow fan of the evaporator is a gap between finned tubes of the evaporator (3).
3. The micro-channel near-isothermal compression type transcritical carbon dioxide circulation system according to claim 1, wherein the auxiliary gas cooler (6) and the scaled micro-channel heat exchanger (9) in the isothermal compressor are equipped with an axial fan (5), the air channel in the auxiliary gas cooler (6) is the gap between the finned tubes, and the air channel in the scaled micro-channel heat exchanger (9) is the gap between the micro-channel fins.
4. The micro-channel near-isothermal compression type transcritical carbon dioxide circulation system according to claim 3, wherein an air channel passing air valve (7) is arranged between an air channel in the auxiliary gas cooler (6) and an air channel in the convergent-divergent micro-channel heat exchanger (9).
5. The micro-channel near-isothermal compression type transcritical carbon dioxide circulation system according to claim 4, wherein when the air valve (7) is in a full-closed mode, the air flow channel between the fins of the scaled micro-channel heat exchanger (9) is completely cut off; low pressure CO2The gas enters a centrifugal impeller (10) of the isothermal compressor through a compressor suction pipe and is accelerated to a supersonic state, and then enters a scaling type microchannel heat exchanger (9) at a high speed state, and high-speed CO2And in the processes of speed reduction and pressure increase, the pressure increase of the gas is realized according to the near-isentropic compression process.
6. The micro-channel near-isothermal compression type transcritical carbon dioxide circulation system according to claim 4, wherein when the air valve (7) is in a full-open mode, the air flow channels between the fins of the scaled micro-channel heat exchanger (9) are completely open, and the low-pressure CO is completely discharged2Gas-passing isothermal compression air suction pipeThe kinetic energy is converted into pressure energy in a near isothermal compression mode by entering a centrifugal impeller (10) of an isothermal compressor to accelerate to a supersonic speed state and then entering a scaling type microchannel heat exchanger (9) to realize the processes of speed reduction, pressure boosting and quick heat release.
7. A microchannel near-isothermal compression type transcritical carbon dioxide circulating method, which is based on the microchannel near-isothermal compression type transcritical carbon dioxide circulating system of claim 1, and comprises:
low pressure CO2The gas enters a centrifugal impeller (10) of the isothermal compressor through an isothermal compression gas suction pipe to be accelerated to a supersonic speed state, then enters a scaling type micro-channel heat exchanger (9), and the outlet of a plurality of scaling type micro-channel heat exchangers (9) is pressurized to CO in a high-pressure state2The gas is collected by the gas collector (8) uniformly and then enters the auxiliary gas cooler (6) through the isothermal compression exhaust pipe, and exchanges heat with the room temperature again; then, supercritical CO2The fluid is subjected to heat exchange with a refrigerant in a gas suction state through the heat regenerator (1), throttled to a low pressure state through the electronic expansion valve (2), refrigerating capacity is provided in the evaporator (3), and then the fluid enters the gas suction pipe of the isothermal compressor again after passing through the gas-liquid separator (4) and the heat regenerator (1), so that circulation is realized.
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