CN114739037A - Double-ejector multi-loop evaporation vapor compression circulation system and working method - Google Patents
Double-ejector multi-loop evaporation vapor compression circulation system and working method Download PDFInfo
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- CN114739037A CN114739037A CN202210366915.9A CN202210366915A CN114739037A CN 114739037 A CN114739037 A CN 114739037A CN 202210366915 A CN202210366915 A CN 202210366915A CN 114739037 A CN114739037 A CN 114739037A
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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
- F25B9/08—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point using ejectors
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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
- F25B41/30—Expansion means; Dispositions thereof
- F25B41/385—Dispositions with two or more expansion means arranged in parallel on a refrigerant line leading to the same evaporator
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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
- F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
- Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating
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- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
Abstract
A vapor compression circulation system with double ejectors and multiple loops for evaporation and a working method thereof are provided, the system comprises a compressor, a condenser, a first ejector, a second ejector, a first evaporator, a second evaporator, a third evaporator, a first electronic expansion valve, a second electronic expansion valve and a gas-liquid separator. The system not only effectively improves the suction pressure of the compressor by using the double ejectors, but also reduces the power consumption of the compressor; three different evaporation temperatures are provided for the system by reasonably designing the connection mode of the double ejectors, so that the heat exchange temperature difference of each evaporator is reduced, and the evaporation temperature of part of refrigerants is increased; in addition, the system is also provided with a gas-liquid separator between the first evaporator and the second evaporator, so that gas generated in the evaporation process in the first evaporator is timely pumped out, the content of liquid refrigerant entering the subsequent evaporator is increased, and the heat exchange performance of the subsequent evaporator is improved; in conclusion, the invention can effectively improve the working performance of the refrigeration/heat pump circulating system.
Description
Technical Field
The invention belongs to the technical field of refrigeration/heat pumps, and particularly relates to a vapor compression circulation system for multi-loop evaporation of double ejectors and a working method.
Background
The vapor compression cycle system has economy and adaptability, and is widely applied to the aspects of heating of refrigerators, air conditioners, cold storages, heat pumps and the like. The evaporator is a key part in the circulating system, and in the refrigerating cycle, the evaporator absorbs heat from air so as to reduce the temperature and humidity of the air and realize the refrigerating and dehumidifying functions. In a heat pump cycle, an evaporator absorbs heat from the outside environment and transfers the heat from the outside environment to the indoor air for the purpose of supplying heat. Therefore, designing a high-efficiency evaporator is one of the key means for improving the performance of the refrigeration/heat pump cycle system.
In conventional vapor-compression refrigeration/heat pump cycles, only a single evaporator is typically employed, i.e., there is only one refrigerant evaporating temperature. When the evaporation temperature is lowered, the heat exchange temperature difference of the evaporator is increased, and the pressure ratio and the power consumption of the compressor are increased. In response to this problem, researchers have proposed dual evaporator systems, i.e., where there are two different evaporation temperatures in one system. On the one hand, the heat transfer medium passes through the evaporators with two different evaporation temperatures in sequence, and the temperature of the heat transfer medium is gradually reduced, so that the heat transfer temperature difference between the refrigerant and the heat transfer medium in each evaporator is reduced, and the irreversible loss of the evaporator caused by the large heat transfer temperature difference is effectively reduced. On the other hand, the dual evaporator system can increase the evaporation pressure of a part of the refrigerant, thereby reducing the power consumption of the compressor.
In addition, in the conventional vapor compression refrigeration/heat pump cycle system, a capillary tube or an expansion valve is usually used as a throttling mechanism to obtain a low-temperature and low-pressure two-phase refrigerant, and in this case, a large throttling loss is generated. Therefore, the ejector is adopted to replace a traditional throttling mechanism, expansion work can be effectively recovered, the suction pressure of the compressor is improved, the power consumption of the compressor is reduced, and the system performance can be further improved.
In recent years, both domestic and foreign scholars have proposed ejector enhanced dual circuit evaporator systems, however problems remain in these studies. In the double-loop evaporator, a refrigerant can generate gas in the evaporation process of the first loop evaporator, and if the gas in the first loop evaporator is not led out, the heat exchange performance of a subsequent evaporator can be affected; meanwhile, only a single ejector is adopted in the existing system, and the potential of expansion work recovery is not fully utilized.
Disclosure of Invention
In order to solve the problems of the prior art, the present invention provides a vapor compression cycle system with dual ejectors and multiple loops for evaporation and a working method thereof. The invention adopts the double ejectors to fully recover the expansion work and improve the suction pressure of the compressor, thereby reducing the pressure ratio and the power consumption of the compressor; the multi-loop evaporator is adopted, so that the problem of large heat exchange temperature difference of a single evaporator is solved, and the irreversible loss of the evaporator is reduced; the gas-liquid separator is arranged at the outlet of the first evaporator, so that gas generated in the first evaporator is separated in time, the content of refrigerant liquid entering a subsequent evaporator is increased, the heat exchange performance is improved, and the working performance of the system is obviously improved.
In order to achieve the purpose, the technical scheme of the invention is as follows:
a vapor compression cycle system of dual ejector multi-loop evaporation comprises a compressor 101, a condenser 102, a first ejector 103, a second ejector 104, a first evaporator 105, a second evaporator 106, a third evaporator 107, a first electronic expansion valve 108, a second electronic expansion valve 109 and a gas-liquid separator 110; in the circulation system, an outlet of the compressor 101 is connected to an inlet of the condenser 102; the outlet of the condenser 102 is divided into two paths, wherein one path is connected with the primary inlet of the first ejector 103, and the other path is connected with the primary inlet of the second ejector 104; the outlet of the first ejector 103 and the outlet of the second ejector 104 are connected to the inlet of a first evaporator 105; the outlet of the first evaporator 105 is connected with the inlet of the gas-liquid separator 110; the liquid phase outlet of the gas-liquid separator 110 is divided into two paths, wherein one path is connected with the inlet of the first electronic expansion valve 108; the outlet of the first electronic expansion valve 108 is connected to the inlet of the second evaporator 106; the outlet of the second evaporator 106 is connected with the secondary flow inlet of the first ejector 103; the other path of liquid phase outlet of the gas-liquid separator 110 is connected with the inlet of the second electronic expansion valve 109; the outlet of the second electronic expansion valve 109 is connected with the inlet of the third evaporator 107; the outlet of the third evaporator 107 is connected to the secondary flow inlet of the second ejector 104; the gas-phase outlet of the gas-liquid separator 110 is connected with the inlet of the compressor 101 to form the whole circulation system.
The heat exchange medium air sequentially flows through the first evaporator 105, the second evaporator 106 and the third evaporator 107, and sequentially exchanges heat with refrigerants at different evaporation temperatures, and finally the air is deeply cooled and dehumidified; the first evaporator 105 is an evaporator through which air passes first, and the evaporation temperature is highest; the second evaporator 106 is an intermediate evaporator, and the evaporation temperature is intermediate; the third evaporator 107 is the evaporator through which the air passes last, and the evaporation temperature is lowest; therefore, the circulation system has three evaporation temperatures, and cooled air passes through the first evaporator 105, the second evaporator 106 and the third evaporator in sequence, so that the gradual reduction of the air temperature is realized, the heat exchange temperature difference in each heat exchanger is reduced, and the irreversible loss of the heat exchanger is reduced.
The first ejector 103 and the second ejector 104 are key to realizing the single-compressor multiple-evaporator system. The high-temperature high-pressure primary fluid expands and reduces pressure at the nozzle outlet of the ejector to form a low-pressure area, the secondary fluid with relatively low pressure is ejected according to pressure difference, the two streams of fluid are fully mixed in a mixing chamber of the ejector, the velocity energy is converted into pressure energy in a diffusion chamber, and the pressure of the mixed fluid is lifted and then discharged out of the ejector. Thus, through the proper connection of the dual ejectors, three different evaporation pressures are provided for the single compressor system, with the first evaporator 105 at the outlet of the dual ejectors, with the highest evaporation pressure; the second evaporator 106 is arranged at a secondary flow injection port of the first ejector 103, and the evaporation pressure of the second evaporator is between the first evaporator 105 and the third evaporator 107 by adjusting the first electronic expansion valve 108; the third evaporator 107 is located at the secondary flow injection port of the second ejector 104, and the evaporation pressure thereof is minimized by adjusting the second electronic expansion valve 109. The three systems thus increase the partial refrigerant evaporating pressure, reducing the compressor pressure ratio and power consumption.
The gas-liquid separator 110 is disposed between the first evaporator 105 and the second evaporator 106, and is used for separating gas generated in the evaporation process of the first evaporator 105 and increasing the liquid content of the refrigerant in the other two loop evaporators (the second evaporator 106 and the third evaporator 107), so as to improve the heat exchange performance of the other two loop evaporators.
In the working method of the vapor compression circulating system with the double-ejector multi-loop evaporation, the outlet of the compressor 101 discharges overheated gaseous refrigerant, and the superheated gaseous refrigerant is fully condensed into saturated liquid in the condenser 102 to form high-temperature and high-pressure liquid refrigerant; the high-temperature and high-pressure liquid refrigerant is divided into two paths, which are respectively used as primary fluid of the first ejector 103 and the secondary fluid of the second ejector 104, and the two paths expand and reduce pressure at the nozzle outlet to form a low-pressure area, so that the secondary fluid from the second evaporator 106 and the third evaporator 107 is ejected; the mixed fluid of the first ejector 103 and the second ejector 104 respectively completes the pressure boosting process in the respective pressure-expanding chambers, and then the outlets of the two ejectors are converged and connected with the inlet of the first evaporator 105; the two-phase fluid after the two ejector outlets are boosted is evaporated and absorbs heat in the first evaporator 105, and the air is primarily cooled; then the two-phase refrigerant is fully separated into gas phase and liquid phase in the gas-liquid separator 110, and the gaseous refrigerant generated in the evaporation process is extracted, so that the heat exchange performance of the subsequent evaporator is improved; the gas-liquid separator 110 has an inlet and two outlets, wherein the separated saturated liquid refrigerant is discharged from the liquid outlet and continues to be evaporated; the saturated liquid refrigerant is divided into two paths, controlled by a first electronic expansion valve 108 and a second electronic expansion valve 109, and respectively supplies liquid to a second evaporator 106 and a third evaporator 107; the two-phase refrigerant evaporates and absorbs heat in the second evaporator 106 and the third evaporator 107 to a saturated gas, and is then injected through the secondary inlets of the first ejector 103 and the second ejector 104, respectively; at this time, the air is further cooled down through the second evaporator 106 and is cooled down to a specified temperature at the outlet of the third evaporator 107; the gas phase outlet of the gas-liquid separator 110 is connected to the inlet of the compressor 101, and the gaseous refrigerant generated in the evaporation process of the first evaporator 105 is drawn by the compressor 101, thereby completing the whole cycle process.
Compared with the conventional vapor compression refrigeration/heat pump system, the multi-evaporator system with the double ejectors has the following beneficial effects:
(1) the multi-loop evaporator is adopted to effectively reduce the heat exchange temperature difference between the evaporator and the heat exchange medium.
(2) The double ejectors are adopted to effectively recover expansion work and convert the expansion work into the lifting of the pressure of the refrigerant, so that the suction pressure of the compressor is improved, and the power consumption of the compressor is reduced.
(3) A gas-liquid separator is introduced into the multi-loop evaporator, and gas generated in the evaporation process in the first loop evaporator is led out, so that the heat exchange performance of the subsequent evaporator is improved.
Drawings
FIG. 1 is a schematic view of a circulation system of the present invention;
FIG. 2 is a pressure-enthalpy diagram (P-h diagram) of the cycle system operation of the present invention;
in the figure: 1-10, each state point of refrigerant in the circulation system, 101, compressor, 102, condenser, 103, first ejector, 104, second ejector, 105, first evaporator, 106, second evaporator 107, third evaporator, 108, first electronic expansion valve, 109, second electronic expansion valve, 110, gas-liquid separator.
Detailed Description
The invention is further described below with reference to the accompanying drawings.
As shown in FIG. 1, the present invention relates to a vapor compression cycle system with dual ejector multi-loop evaporation, which comprises a compressor 101, wherein the outlet of the compressor 101 is connected with the inlet of a condenser 102; the outlet of the condenser 102 is divided into two paths, wherein one path is connected with the primary inlet of the first ejector 103, and the other path is connected with the primary inlet of the second ejector 104; the outlet of the first ejector 103 and the outlet of the second ejector 104 are connected to the inlet of a first evaporator 105; an outlet of the first evaporator 105 is connected with an inlet of the gas-liquid separator 110; the liquid phase outlet of the gas-liquid separator 110 is divided into two paths, wherein one path is connected with the inlet of the first electronic expansion valve 108; the outlet of the first electronic expansion valve 108 is connected with the inlet of the second evaporator 106; the outlet of the second evaporator 106 is connected with the secondary flow inlet of the first ejector 103; the other path of liquid phase outlet of the gas-liquid separator 110 is connected with the inlet of the second electronic expansion valve 109; the outlet of the second electronic expansion valve 109 is connected with the inlet of the third evaporator 107; the outlet of the third evaporator 107 is connected to the secondary flow inlet of the second ejector 104; the gas-phase outlet of the gas-liquid separator 110 is connected with the inlet of the compressor 101 to form the whole circulation system.
Figure 2 is a pressure-enthalpy diagram (P-h diagram) corresponding to the operation of the circulation system of the present invention. With reference to fig. 2, the specific working process of the circulation system of the present invention is as follows: the compressor 101 outlet discharges superheated gaseous refrigerant (at point 2 in fig. 2) and is fully condensed in condenser 102 to a saturated liquid (at point 3 in fig. 2); the high-temperature and high-pressure liquid refrigerant is divided into two paths, which are respectively used as primary fluid of the first ejector 103 and the secondary fluid of the second ejector 104, and the two paths expand and reduce pressure at the nozzle outlet to form a low-pressure area, so that the secondary fluid from the second evaporator 106 and the third evaporator 107 is ejected; the mixed fluid of the first ejector 103 and the second ejector 104 respectively completes the pressure boosting process in the respective pressure-expanding chambers, and then the outlets of the two ejectors are converged and connected with the inlet of the first evaporator 105; the two-phase fluid (4 points in fig. 2) after the two ejector outlets are boosted is evaporated and absorbs heat in the first evaporator 105, and the air is primarily cooled; then the two-phase refrigerant (point 5 in fig. 2) is subjected to sufficient separation of gas phase and liquid phase in the gas-liquid separator 110, and the gaseous refrigerant generated in the evaporation process is extracted, so that the heat exchange performance of the rear-row evaporator is improved; the gas-liquid separator 110 has an inlet and two outlets, wherein the saturated liquid refrigerant (at point 6 in fig. 2) is separated and discharged from the liquid phase outlet and continues to be evaporated; the saturated liquid refrigerant is divided into two paths, and the two paths are controlled by a first electronic expansion valve 108 (point 7 in figure 2) and a second electronic expansion valve 109 (point 9 in figure 2) to respectively supply liquid to a second evaporator 106 and a third evaporator 107; the two-phase refrigerant evaporates in the second evaporator 106 (at point 8 in fig. 2) and the third evaporator 107 (at point 10 in fig. 2) to absorb heat to a saturated gas, and is then drawn through the secondary inlets of the first ejector 103 and the second ejector 104, respectively; at this time, the air is further cooled down via the second evaporator 106 and is cooled down to a specified temperature at the outlet of the third evaporator 107; the gas phase outlet of the gas-liquid separator 110 is connected to the inlet (point 1 in fig. 2) of the compressor 101, and the gaseous refrigerant generated in the evaporation process of the first evaporator 105 is pumped by the compressor 101, thereby completing the entire cycle process.
In the working process of the circulation system of the invention, four different working pressures exist, as shown in fig. 2, the working pressures are respectively condensation pressure (P)c) First evaporation pressure (P)e1) Second evaporation pressure (P)e2) And a third evaporation pressure (P)e3) Wherein the condensing pressure is the highest pressure in the system and is determined by the combined influence of the ambient temperature, the condenser and the ejector nozzle. Among the evaporation pressures, the first evaporation pressure is higher than the second evaporation pressure, which is higher than the third evaporation pressure. Wherein the first evaporation pressure is determined by the boosting capacity of the ejector, and the second evaporation pressure and the third evaporation pressure are determined by the opening degrees of the first electronic expansion valve and the second electronic expansion valve, respectively. Therefore, compared with the traditional vapor compression circulation system, the heat exchange temperature difference of each evaporator in the multi-loop evaporator system adopting the double ejectors is obviously reduced; meanwhile, the suction pressure of the compressor is higher than that of the traditional vapor compression circulating system, so that the pressure ratio and the power consumption of the compressor are reduced; and finally, a gas-liquid separator is arranged between the first loop evaporator and the subsequent evaporator, so that the gas generated in the evaporation process of the first loop evaporator is extracted in time, and the heat exchange performance of the other two loop evaporators is improved. In conclusion, the working performance of the vapor compression circulation system adopting the double-ejector multi-loop evaporation is effectively improved.
Claims (5)
1. A vapor compression cycle system with dual ejectors and multi-loop evaporation is characterized in that: the system comprises a compressor (101), a condenser (102), a first ejector (103), a second ejector (104), a first evaporator (105), a second evaporator (106), a third evaporator (107), a first electronic expansion valve (108), a second electronic expansion valve (109) and a gas-liquid separator (110); in the circulation system, an outlet of a compressor (101) is connected with an inlet of a condenser (102); the outlet of the condenser (102) is divided into two paths, wherein one path is connected with the primary inlet of the first ejector (103), and the other path is connected with the primary inlet of the second ejector (104); the outlet of the first ejector (103) and the outlet of the second ejector (104) are connected with the inlet of a first evaporator (105); the outlet of the first evaporator (105) is connected with the inlet of the gas-liquid separator (110); the liquid phase outlet of the gas-liquid separator (110) is divided into two paths, wherein one path is connected with the inlet of the first electronic expansion valve (108); the outlet of the first electronic expansion valve (108) is connected with the inlet of the second evaporator (106); the outlet of the second evaporator (106) is connected with the secondary flow inlet of the first ejector (103); the other path of liquid phase outlet of the gas-liquid separator (110) is connected with the inlet of a second electronic expansion valve (109); the outlet of the second electronic expansion valve (109) is connected with the inlet of a third evaporator (107); the outlet of the third evaporator (107) is connected with the secondary flow inlet of the second ejector (104); and a gas-phase outlet of the gas-liquid separator (110) is connected with an inlet of the compressor (101) to form a whole circulating system.
2. A dual ejector multi-circuit evaporative vapor compression cycle system as defined in claim 1, wherein: the heat exchange medium air sequentially flows through the first evaporator (105), the second evaporator (106) and the third evaporator (107) and sequentially exchanges heat with refrigerants at different evaporation temperatures, and finally the air is deeply cooled and dehumidified; wherein the first evaporator (105) is the evaporator through which air passes first, and the evaporation temperature is highest; the second evaporator (106) is a middle evaporator, and the evaporation temperature is intermediate; the third evaporator (107) is the evaporator through which the air finally passes, and the evaporation temperature is lowest; therefore, the circulation system has three evaporation temperatures, and cooled air passes through the first evaporator (105), the second evaporator (106) and the third evaporator (107) in sequence, so that the gradual reduction of the air temperature is realized, the heat exchange temperature difference in each heat exchanger is reduced, and the irreversible loss of the heat exchanger is reduced.
3. A dual ejector multi-circuit evaporative vapor compression cycle system as defined in claim 1, wherein: the first ejector (103) and the second ejector (104) are key for realizing a single-compressor multi-evaporator system; the high-temperature high-pressure primary fluid expands and reduces pressure at a nozzle outlet of the ejector to form a low-pressure area, the secondary fluid with relatively low pressure is ejected according to pressure difference, the two streams of fluid are fully mixed in a mixing chamber of the ejector, the velocity energy is converted into pressure energy in a diffusion chamber, and the pressure of the mixed fluid is lifted and then discharged out of the ejector; thus, by the connection of the double ejectors, three different evaporation pressures are provided for the single compressor system, wherein the first evaporator (105) is at the outlet of the double ejectors, the evaporation pressure being highest; the second evaporator (106) is arranged at the secondary flow injection port of the first ejector (103), and the evaporation pressure of the second evaporator is between the first evaporator (105) and the third evaporator (107) by adjusting the first electronic expansion valve (108); the third evaporator (107) is arranged at a secondary flow injection port of the second ejector (104), and the evaporation pressure of the third evaporator is lowest by adjusting the second electronic expansion valve (109); the circulation system thus increases the evaporation pressure of a portion of the refrigerant, reducing the compressor pressure ratio and power consumption.
4. A dual ejector multi-circuit evaporative vapor compression cycle system as defined in claim 1, wherein: the gas-liquid separator (110) is arranged between the first evaporator (105) and the second evaporator (106) and is used for separating gas generated in the evaporation process of the first evaporator (105) and increasing the liquid content of the refrigerant entering the other two loop evaporators, namely the second evaporator (106) and the third evaporator (107), so that the heat exchange performance of the other two loop evaporators is improved.
5. A method of operating a dual ejector multi-circuit evaporative vapour compression cycle system according to any one of claims 1 to 4, wherein: the outlet of the compressor (101) discharges superheated gaseous refrigerant, and the gaseous refrigerant is fully condensed into saturated liquid in the condenser (102) to form high-temperature and high-pressure liquid refrigerant; the high-temperature and high-pressure liquid refrigerant is divided into two paths, the two paths are respectively used as primary fluid of the first ejector (103) and the primary fluid of the second ejector (104), the primary fluid is expanded and decompressed at the outlet of the nozzle, and a low-pressure area is formed, so that secondary fluid from the second evaporator (106) and the third evaporator (107) is injected; the mixed fluid of the first ejector (103) and the second ejector (104) respectively completes the pressure boosting process in the respective pressure-expanding chambers, and then the outlets of the two ejectors are converged and connected with the inlet of the first evaporator (105); the two-phase fluid after the pressure boosting of the outlets of the two ejectors is evaporated and absorbs heat in a first evaporator (105), and the air is preliminarily cooled; then the two-phase refrigerant is fully separated into gas phase and liquid phase in a gas-liquid separator (110), and the gaseous refrigerant generated in the evaporation process is pumped out to improve the heat exchange performance of the rear-row evaporator; the gas-liquid separator (110) has an inlet and two outlets, wherein the separated saturated liquid refrigerant is discharged from the liquid outlet and continues to be evaporated; the saturated liquid refrigerant is divided into two paths, is controlled by a first electronic expansion valve (108) and a second electronic expansion valve (109), and respectively supplies liquid to a second evaporator (106) and a third evaporator (107); the two-phase refrigerant evaporates and absorbs heat in the second evaporator (106) and the third evaporator (107) to form saturated gas, and is injected through secondary inlets of the first ejector (103) and the second ejector (104) respectively; the air is further cooled down through the second evaporator (106) and is cooled down to a specified temperature at the outlet of the third evaporator (107); the gas phase outlet of the gas-liquid separator (110) is connected with the inlet of the compressor (101), and the gaseous refrigerant generated in the evaporation process of the first evaporator (105) is pumped by the compressor (101), so that the whole circulation process is completed.
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN115111808A (en) * | 2022-07-14 | 2022-09-27 | 太原理工大学 | Compression injection type double-temperature heat pump system |
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| CN208920650U (en) * | 2018-09-19 | 2019-05-31 | 东莞市华通电器有限公司 | A kind of refrigeration system |
| CN110410904A (en) * | 2019-07-24 | 2019-11-05 | 华中科技大学 | A kind of densification and high performance humiture independence control air conditioner system |
| CN210688806U (en) * | 2019-10-31 | 2020-06-05 | 广东美的白色家电技术创新中心有限公司 | Refrigeration device |
| CN110986414A (en) * | 2019-11-25 | 2020-04-10 | 西安交通大学 | Multi-temperature-zone and large-temperature-span heat pump circulating system adopting ejector for increasing efficiency |
| CN112229085A (en) * | 2020-09-30 | 2021-01-15 | 西安交通大学 | Low-temperature heat pump circulating system and circulating method suitable for large temperature span |
| CN113701376A (en) * | 2021-09-14 | 2021-11-26 | 珠海格力电器股份有限公司 | Air conditioner circulation system and control method of air conditioner |
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| CN115111808A (en) * | 2022-07-14 | 2022-09-27 | 太原理工大学 | Compression injection type double-temperature heat pump system |
| CN115111808B (en) * | 2022-07-14 | 2023-09-26 | 太原理工大学 | Compression injection type dual-temperature heat pump system |
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