CN109737622B - Two-stage auto-cascade low-temperature refrigeration cycle system and circulation method for enhancing efficiency of two-stage ejector - Google Patents
Two-stage auto-cascade low-temperature refrigeration cycle system and circulation method for enhancing efficiency of two-stage ejector Download PDFInfo
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- CN109737622B CN109737622B CN201811593998.5A CN201811593998A CN109737622B CN 109737622 B CN109737622 B CN 109737622B CN 201811593998 A CN201811593998 A CN 201811593998A CN 109737622 B CN109737622 B CN 109737622B
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Abstract
The invention discloses a two-stage auto-cascade low-temperature refrigeration cycle system with two-stage ejector synergy and a cycle method, wherein a compressor, a condenser and an inlet of a gas-liquid separator I of the system are sequentially connected, saturated gas obtained by the gas-liquid separator I enters a gas-liquid separator II through an evaporative condenser I, and saturated liquid obtained by the gas-liquid separator I enters a nozzle of the ejector II; the gas obtained by the gas-liquid separator II passes through the evaporative condenser II, the heat regenerator, the throttle valve and the evaporator to realize refrigeration, and then enters a secondary inflow port of the ejector I; and the liquid obtained by the gas-liquid separator II enters a nozzle of the ejector I to be mixed with the secondary flow from the evaporator and is subjected to pressure boosting, then the mixture passes through the heat regenerator, enters the ejector II to be ejected by the saturated liquid from the gas-liquid separator I, then sequentially enters the evaporative condenser II and the evaporative condenser I, and finally returns to the compressor. The double-stage ejector fully recovers the expansion work in the liquid throttling process, gradually increases the suction pressure of the compressor, and improves the overall performance of the compressor and the system.
Description
Technical Field
The invention belongs to the technical field of refrigeration of refrigerators and freezers, and particularly relates to a two-stage auto-cascade low-temperature refrigeration system with synergy of a two-stage ejector and a circulation method.
Technical Field
In recent years, with the continuous improvement of the technological level, the low-temperature refrigeration technology is not only applied to the fields of traditional freezing and refrigeration and food transportation, but also increasingly widely applied to various fields such as bioengineering, medical treatment and the like, and particularly the requirement on ultra-low-temperature refrigeration equipment below minus 80 ℃ is increasingly increased; in addition, energy saving and environmental protection have also become the main development direction of low-temperature refrigeration technology. The technical means for realizing low-temperature refrigeration at present mainly comprise multi-stage compression circulation, mixed working medium throttling circulation and self-cascade refrigeration circulation.
Compared with other two technologies, the auto-cascade refrigeration technology utilizes the separation characteristic of non-azeotropic mixed working medium components, realizes automatic cascade through the evaporative condenser, can realize multi-stage cascade by utilizing a single compressor, thereby obtaining the low-temperature refrigeration effect, and has the advantages of low cost, high cooling speed and the like, thereby having great development potential in the field of low-temperature refrigeration. The method has the advantages that large irreversible loss exists in a traditional self-cascade system, firstly, irreversible loss caused by the application of a plurality of throttling components (capillary tubes or throttling valves) in the system is utilized, not only can the pressure of a high-pressure working medium be fully utilized, but also mechanical energy loss caused by pressure loss can be converted into heat and enters the system, and as the concentration of a low-boiling point working medium is high, the throttling pressure difference is increased and the throttling loss is more obvious when the refrigerating temperature is low; secondly, due to the low temperature performance requirement of the system, the suction pressure of the compressor is low, which leads to the increase of the pressure ratio of the compressor and the reduction of the volumetric efficiency of the compressor, which leads to the low performance of the system, and limits the development and application of the technology.
The ejector converts pressure energy into kinetic energy, ejects a low-pressure working medium, and then converts the kinetic energy into the pressure energy again to improve the pressure of the low-pressure working medium, so that the device has the advantages of simple structure, low processing cost, no moving part in the ejector, capability of better recovering expansion work, high reliability and suitability for the working condition of gas-liquid two-phase fluid; in addition, the ejector can improve the suction pressure of the compressor, reduce the pressure ratio of the compressor and effectively improve the system performance. At present, the application of the ejector applied to an ultralow temperature refrigeration system below-80 ℃ is still in the primary stage, and the method is relatively lacked. The ejector is used for a two-stage self-cascade low-temperature refrigerator, has great energy-saving potential, and is a new development direction for realizing an ultralow-temperature refrigeration system below 80 ℃.
Disclosure of Invention
The invention provides a two-stage self-cascade low-temperature refrigeration circulating system and a circulating method for enhancing the efficiency of a two-stage ejector, aiming at the defects in the prior art.
In order to realize the purpose, the invention adopts the technical scheme that:
a two-stage self-cascade low-temperature refrigeration cycle system adopting double ejectors for synergism comprises a compressor 101, a condenser 102, a gas-liquid separator I103, a gas-liquid separator II 105, an evaporative condenser I104, an evaporative condenser II 106, a heat regenerator 107, a throttle valve 108, an evaporator 109, an ejector I110 and an ejector II 111;
an outlet of the compressor 101 is connected with an inlet of a condenser 102, and an outlet of the condenser 102 is connected with an inlet of a gas-liquid separator I103; a saturated liquid outlet of the gas-liquid separator I103 is connected with a nozzle inlet of the ejector II 111, and a gas outlet of the gas-liquid separator I103 is sequentially connected with inlets of the evaporative condenser I104 and the gas-liquid separator II 105; the gas outlet of the gas-liquid separator II 105 is sequentially connected with the secondary inlets of the evaporative condenser II 106, the heat regenerator 107, the throttle valve 108, the evaporator 109 and the ejector I110; a liquid outlet of the gas-liquid separator II 105 is connected with a nozzle inlet of the ejector I110, and is mixed with the secondary fluid of the ejector I110 and subjected to a diffusion process to realize pressure increase; an outlet of the ejector I110 is sequentially connected with secondary flow inlets of the heat regenerator 107 and the ejector II 111, saturated liquid from the gas-liquid separator I103 is mixed with the secondary flow of the ejector II 111, and the pressure is increased again; the outlet of the ejector II 111 is connected with the evaporative condenser II 106, the evaporative condenser I104 and the compressor 101 in sequence to form a complete refrigeration cycle.
Liquid at the liquid outlet of the gas-liquid separator II 105 enters an ejector I110 to inject refrigerant from an evaporator 109; liquid at the liquid outlet of the gas-liquid separator I103 enters an ejector II 111 to inject refrigerant from the outlet of the ejector I110; the system can recover the expansion work twice and obtain higher pressure lifting ratio, and the pressure ratio of the compressor is reduced, so that the system performance is improved.
The evaporative condenser I104 and the evaporative condenser II 106 are arranged, and the refrigerant at the outlet of the ejector II 111 exchanges heat with the gas refrigerant discharged from the gas outlets of the evaporative condenser I104 and the evaporative condenser II 106 respectively, so that the concentration of a low-boiling-point working medium in a gas phase can be improved, the reduction of the refrigeration temperature is facilitated, the suction process of the compressor is ensured to be in an overheat state, the liquid impact of the compressor is avoided, and the reliability of the system is improved; the heat regenerator 107 is arranged, the refrigerant regenerates heat with the fluid from the outlet of the ejector I110 before throttling refrigeration is realized, the supercooling degree before the throttle valve is reduced, the reduction of the inlet temperature of the evaporator 109 is facilitated, meanwhile, the refrigerant of the secondary inflow port of the ejector II 111 is ensured to be in a single-phase gas state, and the reliability of the ejector II 111 is improved.
According to the circulation method of the two-stage self-cascade low-temperature refrigeration circulation system with the synergy of the two-stage ejector, a mixed working medium is changed into high-temperature high-pressure gas through the compressor 101, then the high-temperature high-pressure gas enters the condenser 102 to be condensed into a two-phase state, the two-phase state enters the gas-liquid separator I103, the obtained saturated gas rich in the working medium with the middle and low boiling points enters the evaporation condenser I104 to be changed into a gas-liquid two-phase state, then the gas enters the gas-liquid separator II 105 to be further subjected to component separation, the concentration of the working medium with the low boiling point in the obtained gas-phase refrigerant is further increased, the gas is changed into subcooled liquid through the evaporation condenser II 106 and the; then the liquid enters a secondary inflow port of the ejector I110, the liquid of the gas-liquid separator II 105 enters a nozzle of the ejector I110 and is mixed and diffused with secondary fluid to be changed into two-phase fluid, then the two-phase fluid is changed into single-phase gas through a heat regenerator 107 and enters a secondary inflow port of the ejector II 111, the liquid of the gas-liquid separator I103 enters a nozzle of the ejector II 111 and is mixed and diffused with the secondary fluid to be changed into two-phase fluid, then the two-phase fluid is absorbed by an evaporative condenser II 106 and an evaporative condenser I104 to be changed into superheated gas, and finally the superheated gas returns to the compressor 101, so that the complete two-stage self-cascade low-temperature refrigeration cycle with.
Compared with the traditional ejector synergy self-cascade refrigeration cycle, the cycle utilizes the ejector to recover the expansion work in the liquid throttling process of the gas-liquid separator I103 and the gas-liquid separator II 105, and enhances the injection capacity of the ejector, thereby obtaining higher pressure lift ratio, reducing the pressure ratio of a compressor and improving the overall performance of the system. Secondly, the evaporative condenser I104 and the evaporative condenser II 106 are arranged, so that component separation of refrigerants with different boiling points is facilitated, the concentration of a working medium with a low boiling point in a gas phase is improved, the reduction of the refrigeration temperature is facilitated, meanwhile, the suction and heat regeneration process can ensure that the suction of the compressor is in an overheat state, the liquid impact of the compressor is avoided, and the reliability of the system is improved; the heat regenerator 107 is arranged, the refrigerant regenerates heat with the fluid from the outlet of the ejector I110 before throttling refrigeration is realized, the supercooling degree before the throttle valve is reduced, the reduction of the inlet temperature of the evaporator 109 is facilitated, meanwhile, the refrigerant of the secondary inflow port of the ejector II 111 is ensured to be in a single-phase gas state, and the reliability of the ejector II 111 is improved.
Drawings
Fig. 1 is a schematic view of a cycle of a refrigeration cycle system according to the present invention.
Fig. 2 is a pressure-enthalpy diagram (p-h diagram) of the operation of the refrigeration cycle system of the present invention.
Detailed Description
In order to make the objects, technical solutions and advantages of the present invention more clear and concise, the present invention will be further described in detail with reference to the accompanying drawings and two embodiments. It should be understood that the specific embodiments described herein are merely illustrative of the invention and are not intended to limit the invention.
Examples
As shown in fig. 1, in this embodiment, a two-stage self-cascade low-temperature refrigeration cycle system with two-stage ejector synergy is provided, an outlet of a compressor 101 is connected with an inlet of a condenser 102, and an outlet of the condenser 102 is connected with an inlet of a gas-liquid separator i 103; a saturated liquid outlet of the gas-liquid separator I103 is connected with a nozzle inlet of the ejector II 111, and a gas outlet of the gas-liquid separator I103 is sequentially connected with inlets of the evaporative condenser I104 and the gas-liquid separator II 105; the gas outlet of the gas-liquid separator II 105 is sequentially connected with the secondary inlets of the evaporative condenser II 106, the heat regenerator 107, the throttle valve 108, the evaporator 109 and the ejector I110; a liquid outlet of the gas-liquid separator II 105 is connected with a nozzle inlet of the ejector I110, and is mixed with the secondary fluid of the ejector I110 and subjected to a diffusion process to realize pressure increase; an outlet of the ejector I110 is sequentially connected with secondary flow inlets of the heat regenerator 107 and the ejector II 111, saturated liquid from the gas-liquid separator I103 is mixed with the secondary flow of the ejector II 111, and the pressure is increased again; the outlet of the ejector II 111 is connected with the evaporative condenser II 106, the evaporative condenser I104 and the compressor 101 in sequence to form a complete refrigeration cycle.
Fig. 2 is a pressure-enthalpy diagram (p-h diagram) of the operation of the refrigeration cycle system of the embodiment. The specific working process of the invention is as follows: the mixed working medium is changed into high-temperature high-pressure gas (point 2 in figure 2) through a compressor 101, then the mixed working medium enters a condenser 102 to be partially condensed into a two-phase state (point 3 in figure 2), the mixed working medium enters a gas-liquid separator I103 in the two-phase state, saturated gas (point 5 in figure 2) rich in medium and low boiling point working media is obtained, the saturated gas enters an evaporative condenser I104 to be changed into a gas-liquid two-phase state (point 6 in figure 2), then the saturated gas enters a gas-liquid separator II 105 to be further subjected to component separation, the concentration of the medium and low boiling point working media in the obtained gas-phase refrigerant is further increased (point 10 in figure 2), the gas is changed into supercooled liquid (point 11 in figure 2) through an evaporative condenser II 106 and a heat regenerator 107, and then the gas is changed into low-temperature two-phase fluid (point 12 in figure; then enters a secondary flow inlet (8 points in figure 2) of the ejector I110, the liquid (7 points in figure 2) of the gas-liquid separator II 105 enters a nozzle (9 points in figure 2) of the ejector I110, then expands into a two-phase high-speed fluid (7 'points in figure 2) and passes through mixing and diffusion processes with the secondary fluid to become a two-phase fluid (14 points in figure 2), then passes through a heat regenerator 107 to become a single-phase gas and enters a secondary flow inlet of the ejector II 111, the liquid (4 points in figure 2) of the gas-liquid separator I103 expands into a high-speed two-phase fluid (4' points in figure 2) through a nozzle of the ejector II 111 and passes through mixing and diffusion processes with the secondary fluid to become a two-phase fluid (17 points in figure 2), then passes through an evaporative condenser II 106 to absorb heat (18 points in figure 2) and an evaporative condenser I104 to become superheated gas (1 point in figure 2), and finally returns to the compressor 101, and a complete two-stage self-cascade low-temperature refrigeration cycle with double-stage ejector synergy is realized.
Claims (4)
1. A two-stage auto-cascade low-temperature refrigeration cycle system with double-stage ejector synergy is characterized in that: the system comprises a compressor (101), a condenser (102), a gas-liquid separator I (103), an evaporative condenser I (104), a gas-liquid separator II (105), an evaporative condenser II (106), a heat regenerator (107), a throttle valve (108), an evaporator (109), an ejector I (110) and an ejector II (111);
an outlet of the compressor (101) is connected with an inlet of a condenser (102), and an outlet of the condenser (102) is connected with an inlet of a gas-liquid separator I (103); a saturated liquid outlet of the gas-liquid separator I (103) is connected with a nozzle inlet of the ejector II (111), and a gas outlet of the gas-liquid separator I (103) is sequentially connected with inlets of the evaporative condenser I (104) and the gas-liquid separator II (105); a gas outlet of the gas-liquid separator II (105) is sequentially connected with a secondary inflow port of the evaporative condenser II (106), the heat regenerator (107), the throttle valve (108), the evaporator (109) and the ejector I (110); a liquid outlet of the gas-liquid separator II (105) is connected with a nozzle inlet of the ejector I (110), and is mixed with the secondary fluid of the ejector I (110) and subjected to a pressure expansion process to realize pressure increase; an outlet of the ejector I (110) is sequentially connected with a heat regenerator (107) and a secondary flow inlet of the ejector II (111), saturated liquid from the gas-liquid separator I (103) is mixed with the secondary flow of the ejector II (111), and the pressure is increased again; and the outlet of the ejector II (111) is sequentially connected with the evaporative condenser II (106), the evaporative condenser I (104) and the compressor (101) to form a complete refrigeration cycle.
2. The dual stage ejector enhanced two stage self-cascade cryogenic refrigeration cycle system of claim 1, wherein: liquid at the liquid outlet of the gas-liquid separator II (105) enters an ejector I (110) to inject refrigerant from an evaporator (109); liquid at the liquid outlet of the gas-liquid separator I (103) enters an ejector II (111) to inject refrigerant from the outlet of the ejector I (110); the system utilizes the principle of a two-stage ejector to recover the expansion work of two paths of liquid, gradually increases the pressure increase ratio higher than the suction pressure of the compressor, and reduces the pressure ratio of the compressor, thereby improving the system performance.
3. The dual stage ejector enhanced two stage self-cascade cryogenic refrigeration cycle system of claim 1, wherein: the evaporative condenser I (104) and the evaporative condenser II (106) are arranged, and the refrigerant at the outlet of the ejector II (111) exchanges heat with the gas refrigerant discharged from the gas outlets of the evaporative condenser I (104) and the evaporative condenser II (106) respectively, so that the concentration of a medium-low boiling point working medium in a gas phase is improved, the reduction of the refrigeration temperature is facilitated, the suction process of the compressor is ensured to be in an overheat state, the liquid impact of the compressor is avoided, and the reliability of the system is improved; the heat regenerator (107) is arranged, the refrigerant is subjected to heat regeneration with fluid from the outlet of the ejector I (110) before throttling refrigeration is realized, the supercooling degree of the refrigerant before the throttle valve (108) is reduced, the reduction of the inlet temperature of the evaporator (109) is facilitated, meanwhile, the refrigerant of a secondary inflow port of the ejector II (111) is ensured to be in a single-phase gas state, and the reliability of the ejector II (111) is improved.
4. A method of cycling a two-stage self-cascade cryogenic refrigeration cycle system with two-stage ejector synergy as claimed in any one of claims 1 to 3, characterized in that: the mixed working medium is changed into high-temperature high-pressure gas through a compressor (101), then enters a condenser (102) to be condensed into a two-phase state, enters a gas-liquid separator I (103) in the two-phase state to obtain saturated gas rich in medium and low boiling point working mediums, enters an evaporative condenser I (104) to be changed into a gas-liquid two-phase state, then enters a gas-liquid separator II (105) to further carry out component separation, the concentration of the low boiling point working medium in the obtained gas-phase refrigerant is further increased, the gas is changed into supercooled liquid through an evaporative condenser II (106) and a heat regenerator (107), then is changed into low-temperature two-phase fluid through a throttle valve (108), enters an evaporator (109) to realize low-temperature refrigeration, and then enters a secondary inflow port of; the liquid of the gas-liquid separator II (105) enters a nozzle of the ejector I (110) and is mixed and diffused with the secondary fluid to be changed into two-phase fluid, then the two-phase fluid is changed into single-phase gas through a heat regenerator (107) and enters a secondary inflow port of the ejector II (111), the liquid of the gas-liquid separator I (103) enters the nozzle of the ejector II (111) and is mixed and diffused with the secondary fluid to be changed into two-phase fluid, then the two-phase fluid is absorbed by an evaporative condenser II (106) and an evaporative condenser I (104) to be changed into superheated gas, and finally the superheated gas returns to a compressor (101), so that the complete two-stage self-cascade low-temperature refrigeration cycle with synergy of the two-.
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| CN114623620B (en) * | 2022-02-28 | 2024-03-08 | 河南科技大学 | Double-temperature-position injection compression refrigeration cycle device with expander |
| CN115235135B (en) * | 2022-07-20 | 2023-05-23 | 北京航空航天大学 | Gas classification cooling liquefaction system based on vortex tube and injector |
| CN116538699B (en) * | 2023-04-18 | 2024-05-03 | 西安交通大学 | CO (carbon monoxide)2Two-stage compression double-temperature refrigerating system |
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| US6389818B2 (en) * | 2000-03-03 | 2002-05-21 | Vortex Aircon, Inc. | Method and apparatus for increasing the efficiency of a refrigeration system |
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| JP2007057156A (en) * | 2005-08-24 | 2007-03-08 | Calsonic Kansei Corp | Refrigeration cycle |
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| US6389818B2 (en) * | 2000-03-03 | 2002-05-21 | Vortex Aircon, Inc. | Method and apparatus for increasing the efficiency of a refrigeration system |
| CN101952670A (en) * | 2008-04-18 | 2011-01-19 | 株式会社电装 | Ejector-type refrigeration cycle device |
| CN101603745A (en) * | 2009-07-07 | 2009-12-16 | 河南科技大学 | A kind of pressure-boosting absorptive-type auto-cascade absorption refrigeration circulating system |
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