CN210861850U - Double-stage throttling non-azeotropic working medium mechanical supercooling CO2Transcritical refrigeration cycle system - Google Patents
Double-stage throttling non-azeotropic working medium mechanical supercooling CO2Transcritical refrigeration cycle system Download PDFInfo
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- CN210861850U CN210861850U CN201921465727.1U CN201921465727U CN210861850U CN 210861850 U CN210861850 U CN 210861850U CN 201921465727 U CN201921465727 U CN 201921465727U CN 210861850 U CN210861850 U CN 210861850U
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Abstract
The utility model discloses a doublestage throttle non-azeotropic working medium machinery supercooling CO2A transcritical refrigeration cycle system. The utility model discloses CO2The transcritical refrigeration cycle system comprises a gas cooler, a medium-temperature-stage cooling evaporator, a low-temperature-stage cooling evaporator, an expansion valve, an evaporator and a compressor; the non-azeotropic working medium mechanical supercooling two-stage throttling circulation system comprises a medium temperatureThe system comprises a stage compressor, a condenser, a liquid storage device, a medium-temperature stage throttling valve, a low-temperature stage throttling valve and a low-temperature stage compressor. CO can be subjected to non-azeotropic working medium pressurization mechanical circulation2CO at the outlet of the recycle gas cooler2The fluid is subjected to primary and secondary cooling, so that throttling loss is reduced, and the overall energy efficiency of the system is improved. Through the mechanical auxiliary supercooling circulation of the double-stage throttling non-azeotropic working medium, the heat exchange forms better temperature matching, the heat transfer temperature difference is reduced, the irreversible loss in the process is reduced, the heat transfer irreversible loss of a condenser and an evaporator is further reduced, and the efficiency of the refrigeration circulation is improved.
Description
Technical Field
The utility model relates to the technical field of refrigeration, especially, relate to a doublestage throttle non-azeotropic working medium machinery supercooling CO2A transcritical refrigeration cycle system.
Background
With the increasingly prominent environmental problems of global warming, ozone layer destruction and the like, the search for novel and friendly natural refrigeration working media becomes the research focus in the field of refrigeration and air conditioning in order to replace working media such as CFCs, HCFCs, HFCs and the like which have the destruction effect on the ozone layer and generate the greenhouse effect. Wherein, CO2The advantages of no toxicity, no flammability, safety, environmental protection and the like cause common attention of people.
But due to CO2The lower critical temperature and the higher critical pressure cause large throttling loss and low refrigeration efficiency, and especially when the ambient temperature is higher, CO is generated2The cooling capacity of (2) is drastically reduced. If to CO at the outlet of the gas cooler2The fluid is supercooled, throttling loss is reduced along with the increase of the supercooling degree, circulating cold quantity is increased, and circulating COP is improved. CO 22Supercooling of the refrigeration cycle may be achieved by means of an internal heat exchanger, mechanical supercooling, thermoelectric supercooling, or the like. Some scholars use mechanical supercooling for CO2The transcritical refrigeration cycle was theoretically studied, namely, the main Cycle (CO) was subjected to vapor compression refrigeration cycle2Transcritical refrigeration cycle) gas cooler outlet CO2And cooling is carried out. The mechanical supercooling can not only increase the refrigerating capacity, but also reduce the running high pressure of the main circulation, reduce the exhaust pressure of the compressor and prolong the service life of the compressor
The conventional mechanical supercooling circulation adopts pure working medium, the temperature is kept unchanged in the evaporation phase change process, but the supercritical CO is adopted2The fluid cooling process is a temperature reduction process, and the temperature of the fluid cooling process are not matched, so that irreversible loss in the heat exchange process is large. And for application sites with higher ambient temperature and lower evaporation temperature, CO2The supercooling degree is up to more than 20 ℃. The condensing side of the mechanical supercooling refrigeration cycle exchanges heat with air, and the evaporating side exchanges heat with CO2The fluid exchanges heat, the temperature rise of the air side is generally not more than 8 ℃, and CO2The temperature drop of (A) is about 20 ℃.
If the mechanical supercooling circulation adopts a non-azeotropic working medium, the temperature slippage of the evaporation and condensation phase change process is close, and the condensation side and the evaporation side can not be simultaneously contacted with air and CO2A good temperature match is formed, which in turn causes large irreversible losses.
SUMMERY OF THE UTILITY MODEL
The utility model aims to overcome the defects in the prior art and provide a double-stage throttling non-azeotropic working medium mechanical supercooling CO2A transcritical refrigeration cycle system.
The utility model adopts mechanical supercooling refrigeration cycle and CO2A transcritical refrigeration cycle, wherein the mechanical supercooling refrigeration cycle is a vapor compression refrigeration cycle with two evaporation pressures, and the refrigerant is a mixed refrigerant CO with reasonable temperature slippage2/R1234ze、CO2R1234yf, R41/R1234ze, R41/R1234yf, R32/R1234ze, R32/R1234yf or R32/R600 a.
The utility model discloses circulation system is by non-azeotropic working medium machinery subcooling doublestage throttle circulation system and CO2A transcritical refrigeration cycle system;
the CO is2The transcritical refrigeration cycle system comprises a gas cooler, a medium-temperature-stage cooling evaporator, a low-temperature-stage cooling evaporator, an expansion valve, an evaporator and a compressor; the outlet of the compressor and the inlet of the gas coolerThe outlet of the gas cooler is connected with the inlet of the intermediate-temperature stage cooling evaporator, the outlet of the intermediate-temperature stage cooling evaporator is connected with the inlet of the low-temperature stage cooling evaporator, the outlet of the low-temperature stage cooling evaporator is connected with the inlet of the expansion valve, the outlet of the expansion valve is connected with the inlet of the evaporator, and the inlet of the evaporator is connected with the compressor;
the non-azeotropic working medium mechanical supercooling two-stage throttling circulation system comprises a medium-temperature-stage compressor, a condenser, a liquid storage device, a medium-temperature-stage throttling valve, a low-temperature-stage throttling valve and a low-temperature-stage compressor; the outlet of the medium-temperature stage compressor is connected with the inlet of the condenser, the outlet of the condenser is connected with the medium-temperature throttling valve and the low-temperature throttling valve respectively after passing through the liquid storage device, the outlet of the medium-temperature throttling valve is connected with the inlet of the medium-temperature cooling evaporator, and the outlet of the medium-temperature cooling evaporator is connected with the inlet of the medium-temperature compressor to form a first loop; and the outlet of the low-temperature throttling valve is connected with the inlet of the low-temperature cooling evaporator, the outlet of the low-temperature cooling evaporator is connected with the inlet of the low-temperature stage compressor, and the outlet of the low-temperature stage compressor is connected with the inlet of the medium-temperature stage compressor to form a second loop.
The medium-temperature cooling evaporator and the low-temperature cooling evaporator are both counterflow heat exchangers.
CO2Natural working medium CO is adopted as transcritical refrigeration cycle refrigerant2The non-azeotropic working medium mechanical supercooling two-stage throttling circulating refrigerant is CO2/R1234ze、CO2R1234yf, R41/R1234ze, R41/R1234yf, R32/R1234ze, R32/R1234yf or R32/R600 a.
The utility model has the advantages and positive effects that:
(1)CO2the refrigerant of the refrigerating system is natural working medium CO2。CO2The GWP of the refrigerant is 1, the ODP is 0, the refrigerant is safe, nontoxic, nonflammable, cheap and easily obtained, does not decompose to generate harmful gas under the high-temperature condition, and mechanical supercooling cycle working medium CO2/R1234ze、CO2The GWP of the refrigerant/R1234 yf, R41/R1234ze, R41/R1234yf, R32/R1234ze, R32/R1234yf or R32/R600a is low, and all the refrigerants used in the system are environment-friendly refrigerants.
(2) Mechanical supercooling circulation by using non-azeotropic mixed refrigerant CO2/R1234ze、CO2The refrigerant is used as working media of/R1234 yf, R41/R1234ze, R41/R1234yf, R32/R1234ze, R32/R1234yf or R32/R600a, and the refrigerant and air form good temperature matching in the condenser. The refrigerant is throttled twice, and two evaporation processes with different high and low temperatures exist in a cycle, wherein the evaporation process with higher temperature and CO2The first stage supercooling forms good temperature matching, and the evaporation process at lower temperature is matched with CO2The secondary supercooling performs better temperature matching, and finally further reduces CO2Outlet temperature of the gas cooler. The irreversible loss of heat exchange of the evaporation side and the condensation side of the mechanical supercooling cycle is reduced, and the overall cycle performance is improved.
(3) CO pairs by mechanical subcooling systems2CO at the outlet of the system gas cooler2Supercooling to reduce CO before entering the expansion valve2Temperature, reduced expansion loss, and further reduced CO2High pressure is run.
Drawings
FIG. 1 shows that the utility model discloses two-stage throttle non-azeotropic working medium machinery supercooling CO2CO of transcritical refrigeration cycle system2A temperature enthalpy diagram of the transcritical refrigeration cycle;
FIG. 2 shows the utility model discloses a two-stage throttling non-azeotropic working medium mechanical supercooling CO2A temperature-enthalpy diagram of mechanical supercooling of a two-stage throttling non-azeotropic working medium of a transcritical refrigeration cycle system;
FIG. 3 shows the utility model discloses a two-stage throttling non-azeotropic working medium mechanical supercooling CO2Schematic diagram of a transcritical refrigeration cycle system.
Detailed Description
The present invention will be further explained with reference to the accompanying drawings.
As shown in figure 1, the utility model comprises a two-stage throttling non-azeotropic working medium mechanical supercooling circulation system and CO2A transcritical refrigeration cycle system, and CO as a thick solid line2The transcritical cycle (1 ' -2 ' -3 ' -4 ' -5 ' -6 ' -1 ') and the thin solid lines are the low-temperature evaporation process (8-1) and the high-temperature evaporation process (7-3) of the double-stage throttling non-azeotropic working medium mechanical supercooling cycle. FIG. 2 shows that the utility model discloses super-cooled CO of non-azeotropic medium supercharging machinery2Auxiliary process of transcritical refrigeration cycle systemTemperature-enthalpy diagram of cold refrigeration cycle, in which 3 '-4' is CO24 '-5' to CO2The secondary subcooling process of (1).
The utility model discloses the system is shown in figure 3:
the first step is as follows: the compressor 1 sucks in low-temperature and low-pressure saturated CO at the outlet of the evaporator 62The gas is compressed into high-temperature and high-pressure gas, the temperature of the gas is reduced after the gas exchanges heat with the air in the gas cooler 2, and then the gas respectively flows through the medium-temperature cooling evaporator 3 and the low-temperature cooling evaporator 4 to exchange heat with the non-azeotropic mixed refrigerant, so that CO is realized2The fluid is subcooled and enters the throttle valve 5 for throttling and pressure reduction to become a gas-liquid two-phase state. Then the gas is evaporated by the evaporator 6 to absorb heat and becomes superheated gas which enters the compressor to complete CO2And (4) trans-critical circulation.
The second step is that: the mechanical supercooling circulation low-temperature stage compressor 12 absorbs the low-temperature low-pressure refrigerant at the outlet of the low-temperature cooling evaporator 4, compresses the refrigerant into medium-temperature medium-pressure superheated gas, mixes the superheated gas with saturated gas at the outlet of the medium-temperature cooling evaporator 3, then enters the medium-temperature stage compressor 7, compresses the gas into high-temperature high-pressure gas, and enters the condenser 8 to exchange heat with air. Then the refrigerant enters the liquid storage device 9, one path of the refrigerant is expanded and throttled by the medium-temperature-level throttling valve 10 to become medium-temperature and medium-pressure gas-liquid two-phase fluid, and the other path of the refrigerant is expanded and throttled by the low-temperature-level throttling valve 11 to become low-temperature and low-pressure gas-liquid two-phase fluid.
The third step: mechanically supercooled circulation medium-temperature medium-pressure non-azeotropic working medium gas-liquid two-phase fluid passes through the medium-temperature cooling evaporator 3 and CO2The primary heat exchange is carried out to change the fluid into saturated gas, and the low-temperature low-pressure gas-liquid two-phase fluid passes through the low-temperature cooling evaporator 4 and CO2Heat exchange is carried out to further reduce CO2The temperature of the fluid and the non-azeotropic working medium finally become saturated gas.
Although the preferred embodiments of the present invention have been described with reference to the accompanying drawings, the present invention is not limited to the above-mentioned embodiments, which are only illustrative and not restrictive, and those skilled in the art can make many forms without departing from the spirit and scope of the present invention, which is within the protection scope of the present invention.
Claims (3)
1. Double-stage throttling non-azeotropic working medium mechanical supercooling CO2The transcritical circulation refrigeration system is characterized in that the circulation system consists of a non-azeotropic working medium mechanical supercooling two-stage throttling circulation system and CO2A transcritical refrigeration cycle system;
the CO is2The transcritical refrigeration cycle system comprises a gas cooler, a medium-temperature-stage cooling evaporator, a low-temperature-stage cooling evaporator, an expansion valve, an evaporator and a compressor; the outlet of the compressor is connected with the inlet of the gas cooler, the outlet of the gas cooler is connected with the inlet of the medium-temperature-stage cooling evaporator, the outlet of the medium-temperature-stage cooling evaporator is connected with the inlet of the low-temperature-stage cooling evaporator, the outlet of the low-temperature-stage cooling evaporator is connected with the inlet of the expansion valve, the outlet of the expansion valve is connected with the inlet of the evaporator, and the inlet of the evaporator is connected with the compressor;
the non-azeotropic working medium mechanical supercooling two-stage throttling circulation system comprises a medium-temperature-stage compressor, a condenser, a liquid storage device, a medium-temperature-stage throttling valve, a low-temperature-stage throttling valve and a low-temperature-stage compressor; the outlet of the medium-temperature stage compressor is connected with the inlet of the condenser, the outlet of the condenser is connected with the medium-temperature throttling valve and the low-temperature throttling valve respectively after passing through the liquid storage device, the outlet of the medium-temperature throttling valve is connected with the inlet of the medium-temperature cooling evaporator, and the outlet of the medium-temperature cooling evaporator is connected with the inlet of the medium-temperature compressor; the outlet of the low-temperature throttling valve is connected with the inlet of a low-temperature cooling evaporator, the outlet of the low-temperature cooling evaporator is connected with the inlet of a low-temperature stage compressor, and the outlet of the low-temperature stage compressor is connected with the inlet of a medium-temperature stage compressor.
2. The dual stage throttling non-azeotropic working medium mechanical subcooling CO according to claim 12The transcritical circulation refrigeration system is characterized in that the medium-temperature cooling evaporator and the low-temperature cooling evaporator are both counterflow heat exchangers.
3. The dual stage throttle of claim 1Mechanical super-cooling CO of non-azeotropic working medium2Transcritical cycle refrigeration system, characterized by CO2Natural working medium CO is adopted as transcritical refrigeration cycle refrigerant2The non-azeotropic working medium mechanical supercooling two-stage throttling circulating refrigerant is CO2/R1234ze、CO2R1234yf, R41/R1234ze, R41/R1234yf, R32/R1234ze, R32/R1234yf or R32/R600 a.
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| CN201921465727.1U CN210861850U (en) | 2019-09-05 | 2019-09-05 | Double-stage throttling non-azeotropic working medium mechanical supercooling CO2Transcritical refrigeration cycle system |
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| CN201921465727.1U CN210861850U (en) | 2019-09-05 | 2019-09-05 | Double-stage throttling non-azeotropic working medium mechanical supercooling CO2Transcritical refrigeration cycle system |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN113587469A (en) * | 2021-08-02 | 2021-11-02 | 珠海格力节能环保制冷技术研究中心有限公司 | Control device and method of temperature control system and temperature control system |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN113587469A (en) * | 2021-08-02 | 2021-11-02 | 珠海格力节能环保制冷技术研究中心有限公司 | Control device and method of temperature control system and temperature control system |
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