CN211060436U - Injection supercharging two-stage series connection supercooling double-temperature-zone refrigerating system - Google Patents
Injection supercharging two-stage series connection supercooling double-temperature-zone refrigerating system Download PDFInfo
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- CN211060436U CN211060436U CN201921842701.4U CN201921842701U CN211060436U CN 211060436 U CN211060436 U CN 211060436U CN 201921842701 U CN201921842701 U CN 201921842701U CN 211060436 U CN211060436 U CN 211060436U
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Abstract
The utility model provides an injection pressure boost doublestage series connection subcooling dual temperature area refrigerating system, including CO2A gas cooler; CO 22One path of pipeline of an outlet of the heat medium side of the gas cooler is sequentially communicated with the heat medium side of the intermediate-temperature stage cooling evaporator, the heat medium side of the low-temperature stage cooling evaporator, the first throttle valve and the first throttle valveThe liquid inlet of the gas-liquid separator, the second throttling valve and the liquid inlet of the second gas-liquid separator; the gas outlet of the second gas-liquid separator is sequentially communicated with low-temperature CO2Compressor, medium and low temperature CO2Compressor, medium-high temperature CO2Compressor, high temperature CO2Compressor and CO2An inlet on the heat medium side of the gas cooler. Injection pressure boost doublestage series connection subcooling dual-temperature-zone refrigerating system, adopt ejector pressure boost doublestage series connection cooling evaporator to realize the subcooling, make heat transfer process form better temperature matching, reduce the heat transfer difference in temperature, can show and reduce CO2Irreversible loss of heat exchange during subcooling.
Description
Technical Field
The utility model belongs to the technical field of refrigeration and heating, heat pump, especially, relate to an injection pressure boost doublestage series connection subcooling dual temperature area refrigerating system.
Background
Nowadays, energy is increasingly in short supply and environmental problems are more prominent, and a feasible energy-saving and environment-friendly mode is sought in the whole society. Meanwhile, new technologies and new products with excellent performance, low price and stable operation are continuously emerging. In the aspect of energy consumption, the refrigeration air-conditioning building has a large proportion, is a large user for electricity in the building, and needs to explore a novel energy-saving refrigeration heat pump technology. For civil and commercial applications, the demand for cooling and heating in multiple temperature zones is increasing dramatically. At present, the requirements of different temperature areas are mainly met through two or more refrigeration (heat pump) devices, so that energy waste and environmental damage are caused to a great extent. Meanwhile, most of the filled refrigerants of the equipment are HFCs high GWP working media.
CO2Compared with the traditional technology, the refrigeration technology is more efficient, more energy-saving and more environment-friendly. Carbon dioxide is known as a substitute with the most development potential of CFCs, HCFCs and HFCs by virtue of its excellent characteristics. Therefore, the green carbon dioxide refrigeration technology has wide development prospect. However, due to CO2The lower critical temperature (31.1 ℃) and the higher critical pressure (7.38MPa) cause the large throttle irreversible loss and the lower refrigeration efficiency, and the transcritical CO is treated2CO at the outlet of the gas cooler of the refrigeration cycle2The cooling method increases super-cooling degree to reduce throttling loss, increase circulating cold quantity and reduce CO2The high pressure of the circulation operation and the exhaust pressure of the compressor prolong the service life of the compressor and improve the COP of the circulation.
CO with an emitter2Refrigeration (heat pump) circulation is a research hotspot in recent years, and related researches show that CO with an ejector2Compared with the original heat pump set COP, the COP of the heat pump set is improved by more than 20 percent. The ejector is also called an injection pump and is mainly used for changing the pressure of fluid. The main high-pressure fluid expands in the nozzle at the constant entropy speed to increase the pressure and reduce the pressure, the secondary flow is ejected and sucked, and the two flows are mixed in the mixing chamberThe mixture is internally mixed to the intermediate pressure to form the intermediate pressure fluid at the outlet of the ejector. The invention uses the ejector to obtain two different evaporation pressures, completes two-stage series supercooling, increases the supercooling degree, reduces the throttle irreversible loss and improves the overall efficiency of the system.
Disclosure of Invention
In view of this, the utility model aims at providing an it penetrates pressure boost doublestage and establishes ties supercooling dual-temperature-zone refrigerating system to overcome prior art's defect, adopt ejector pressure boost doublestage to establish ties the cooling evaporator and realize the supercooling, two different heat transfer temperatures of medium temperature and high temperature of two series connection cooling evaporators make transcritical CO2CO at the outlet of the recycle gas cooler2The fluid is continuously supercooled twice in a stepped way, so that better temperature matching is formed in the heat exchange process, the heat transfer temperature difference is reduced, and the CO can be obviously reduced2Irreversible heat exchange loss in supercooling process and CO reduction2The outlet temperature of the gas cooler obtains larger super-cooling degree.
In order to achieve the above purpose, the technical scheme of the utility model is realized like this:
an injection supercharging two-stage series connection supercooling dual-temperature-zone refrigerating system comprises CO2A gas cooler;
CO2one pipeline of an outlet at the heat medium side of the gas cooler is sequentially communicated with the heat medium side of the medium-temperature stage cooling evaporator, the heat medium side of the low-temperature stage cooling evaporator, the first throttling valve, a liquid inlet of the first gas-liquid separator, the second throttling valve and a liquid inlet of the second gas-liquid separator; the gas outlet of the second gas-liquid separator is sequentially communicated with low-temperature CO2Compressor, medium and low temperature CO2Compressor, medium-high temperature CO2Compressor, high temperature CO2Compressor and CO2An inlet on the heat medium side of the gas cooler; the liquid outlet of the second gas-liquid separator is sequentially communicated with CO2The secondary inflow port of the second ejector is arranged on the refrigerant side of the low-temperature evaporator; the gas outlet of the first gas-liquid separator is communicated with the medium-low temperature CO2The inlet of the compressor and the liquid outlet of the first gas-liquid separator which is not communicated with the second throttle valve are sequentially communicated with CO2The secondary inflow port of the first ejector is arranged on the refrigerant side of the intermediate-temperature-stage evaporator;
CO2the other pipeline of the outlet of the heat medium side of the gas cooler is divided into two pipelines, and one pipeline is communicated with the main flow inlet of the first ejector, the refrigerant side of the medium-temperature stage cooling evaporator and the high-temperature CO in sequence2Compressor and CO2The inlet of the heat medium side of the gas cooler and the other pipeline are sequentially communicated with the main flow inlet of the second ejector, the refrigerant side of the low-temperature stage cooling evaporator and the medium-high temperature CO2An inlet of the compressor.
When in use, CO2Low temperature stage evaporator, CO2Intermediate temperature stage evaporator, low temperature CO2Compressor, medium and low temperature CO2Compressor, medium-high temperature CO2Compressor, high temperature CO2Compressor, CO2The gas cooler, the medium-temperature-stage cooling evaporator, the first ejector, the second ejector, the low-temperature-stage cooling evaporator, the first throttle valve, the first gas-liquid separator, the second throttle valve and the second gas-liquid separator form a transcritical CO2Double-temperature-zone refrigeration cycle; the first ejector, the second ejector, the medium-temperature-stage cooling evaporator and the low-temperature-stage cooling evaporator jointly form an ejector supercharging two-stage series supercooling device, and the ejector supercharging two-stage series supercooling double-temperature-region refrigeration cycle can be completed.
Further, the heat exchange working medium of the injection supercharging two-stage series connection supercooling double-temperature-zone refrigerating system is CO2。
Further, CO2The heat exchange fluid on the refrigerant side of the gas cooler is water or air.
Further, CO2Refrigerant side and CO of intermediate temperature stage evaporator2The heat exchange fluid on the refrigerant side of the low-temperature stage evaporator is air.
Further, CO2The gas cooler is a sleeve-type heat exchanger or a plate-type heat exchanger; intermediate temperature stage cooling evaporator, low temperature stage cooling evaporator, CO2Intermediate temperature stage evaporator, CO2The low-temperature evaporator respectively adopts a sleeve type evaporator, a finned tube type evaporator and a finned tube type evaporator.
Further, CO2The evaporation temperature range of the low-temperature stage evaporator is-56 to-20 ℃, and CO is evaporated2The temperature range of the medium-temperature-stage evaporator is-20-10 ℃, the temperature range of the medium-temperature-stage cooling evaporator is 10-30 ℃, and the temperature range of the low-temperature-stage cooling evaporator is-10-20 ℃.
Further, low temperature CO2The suction pressure range of the compressor is 0.53-1.97 MPa, and the exhaust pressure range is 1.97-4.50 MPa; medium and low temperature CO2The suction pressure range of the compressor is 1.97-4.50 MPa, and the exhaust pressure range is 2.65-5.73 MPa; medium and high temperature CO2The suction pressure range of the compressor is 2.65-5.73 MPa, and the exhaust pressure range is 4.50-7.21 MPa; high temperature CO2The air suction pressure range of the compressor is 4.50-7.21 MPa, and the exhaust pressure range is 7.50-14 MPa.
Further, the secondary flow of the first ejector has the air suction temperature ranging from-20 ℃ to 10 ℃, the pressure ranging from 1.97MPa to 4.50MPa, the main flow temperature ranging from 20 ℃ to 45 ℃, the pressure ranging from 7.5 MPa to 14MPa, the outlet temperature ranging from 10 ℃ to 30 ℃ and the pressure ranging from 2.65 MPa to 5.73 MPa.
Furthermore, the secondary flow of the second ejector has the air suction temperature ranging from-56 ℃ to-20 ℃, the pressure ranging from 0.53 MPa to 1.97MPa, the main flow temperature ranging from 20 ℃ to 45 ℃, the pressure ranging from 7.5 MPa to 14MPa, the outlet temperature ranging from-10 ℃ to 20 ℃ and the pressure ranging from 2.65 MPa to 5.73 MPa.
The utility model discloses still relate to as above draw and penetrate pressure boost doublestage series connection subcooling dual temperature area refrigerating system in the application of food refrigeration field.
Compared with the prior art, an injection pressure boost doublestage series connection subcooling dual-temperature-zone refrigerating system have following advantage:
(1) conventional mechanical supercooling of CO2The optimum supercooling degree of the circulation is overlarge, and the supercooling process CO2The temperature of the refrigerant is not matched with that of the conventional refrigerant, and the irreversible loss of heat exchange is large. The utility model discloses an injection ware pressure boost doublestage is established ties supercooling device and is realized the subcooling, and two different heat transfer temperatures of medium temperature and high temperature of two series connection cooling evaporators make and stride critical CO2CO at the outlet of the recycle gas cooler2The fluid is supercooled twice continuously, so that better temperature matching is formed in the heat exchange process, the heat transfer temperature difference is reduced, and the appearance is obviousRemarkably reduce CO2Irreversible heat exchange loss in supercooling process and CO reduction2The outlet temperature of the gas cooler obtains larger super-cooling degree. With simultaneous reduction of CO entering the throttle valve2The temperature reduces irreversible throttling loss and improves the overall energy efficiency of the system.
(2) Injecting outlet gas of the low-temperature evaporator and the medium-temperature evaporator respectively through double injectors to form two different evaporation temperatures and to CO2The fluid is cooled, the pressure reduction effect can be achieved without a throttle valve in the process, throttling loss is reduced, the pressure of the outlet of the ejector is higher than the evaporating pressure of the corresponding evaporator, the suction pressure of the compressor is improved, the compression ratio and the exhaust temperature of the compressor are reduced, and the system performance is improved.
(3) Compared with the conventional supercooling technology, the utility model discloses do not fill the vapour compression system who fills and annotate other working mediums alone to dispose, but adopt CO2The refrigerant is only natural working medium CO after self throttling and evaporation supercooling2Without the use of other conventional synthetic refrigerants, CO2The ODP is 0, the GWP is 1, the decomposition is not generated under the high temperature condition, and the method is safe, non-toxic and environment-friendly.
(4) Compared with the conventional CO2The compression process, the injection pressurization two-stage series connection supercooling double-temperature area refrigeration cycle reduces CO2To reduce compressor discharge pressure, CO2The pressure ratio of the compressor is reduced, the isentropic efficiency is improved, and the service life of the compressor is prolonged.
(5) The first gas-liquid separator and the second gas-liquid separator are arranged so that inflow of CO is performed2Intermediate temperature stage evaporator and CO2The working medium of the low-temperature evaporator is saturated liquid, and compared with the traditional gas-liquid two-phase fluid, the refrigerant is uniformly distributed in each parallel pipeline of the evaporator, so that the heat exchange efficiency is greatly improved, the heat exchange area of the evaporator can be reduced, and the low-temperature evaporator has better economical efficiency.
(6) Transcritical CO2The dual temperature zone can meet the requirements of two different temperature levels, CO2The middle-temperature evaporator has slightly higher evaporation temperature and can store dairy products, vegetables, fruits, eggs and the like; and CO2Relative evaporation temperature of low-temperature evaporatorLow in cost, and can be used for storing meat, fish, etc. Compare traditional equipment, this system can adopt one set of system can realize the function of multiple warm area, and equipment integration, the system is compact, makes things convenient for the demand of different warm areas, reduces equipment and takes up an area of.
Drawings
Fig. 1 is a schematic diagram of a simple structure of an injection supercharging two-stage series connection supercooling dual-temperature-zone refrigeration system according to the present invention;
fig. 2 is a pressure-enthalpy diagram of the injection supercharging two-stage series connection supercooling dual-temperature-zone refrigerating system in working.
Reference numerals:
1-low temperature CO2A compressor; 2-medium and low temperature CO2A compressor; 3-medium-high temperature CO2A compressor; 4-high temperature CO2A compressor; 5-CO2A gas cooler; 6-intermediate temperature stage cooling evaporator; 7-a first ejector; 8-a second ejector; 9-low temperature stage cooling evaporator; 10-a first throttle valve; 11-CO2A medium temperature stage evaporator; 12-a first gas-liquid separator; 13-a second throttle valve; 14-CO2A low temperature stage evaporator; 15-second gas-liquid separator.
Detailed Description
Unless defined otherwise, technical terms used in the following examples have the same meanings as commonly understood by one of ordinary skill in the art to which this invention belongs. The test reagents used in the following examples, unless otherwise specified, are all conventional biochemical reagents; the experimental methods are conventional methods unless otherwise specified.
The present invention will be described in detail with reference to the following embodiments and accompanying drawings.
An injection supercharging two-stage series connection supercooling dual-temperature-region refrigerating system comprises an injector supercharging two-stage series connection supercooling device and a transcritical CO, wherein the injector supercharging two-stage series connection supercooling device can realize mutual heat exchange2Double temperature zone refrigeration cycle. The ejector supercharging two-stage series supercooling device comprises a first ejector, a second ejector, a medium-temperature-stage cooling evaporator and a low-temperature-stage cooling evaporator; the first ejector and the second ejector are arranged in parallel, the outlet of the first ejector is communicated with the refrigerant side of the medium-temperature-stage cooling evaporator 6, andthe outlets of the two ejectors are communicated with the refrigerant side of the low-temperature-stage cooling evaporator 9; the heat medium side of the intermediate stage cooling evaporator 6 and the heat medium side of the low stage cooling evaporator 9 are connected in series. The utility model discloses an injection ware pressure boost doublestage is established ties supercooling device and is realized the subcooling, and two different heat transfer temperatures of medium temperature and high temperature of two series connection cooling evaporators make and stride critical CO2CO at the outlet of the recycle gas cooler2The fluid is continuously supercooled twice in a stepped way, so that better temperature matching is formed in the heat exchange process, the heat transfer temperature difference is reduced, and the CO can be obviously reduced2Irreversible heat exchange loss in supercooling process and CO reduction2The outlet temperature of the gas cooler obtains larger super-cooling degree. With simultaneous reduction of CO entering the throttle valve2The temperature reduces irreversible throttling loss and improves the overall energy efficiency of the system.
Transcritical CO2The dual temperature zone refrigeration cycle includes CO2A gas cooler 5; CO 22An outlet at the heat medium side of the gas cooler 5 is communicated with a first pipeline and a second pipeline, and the first pipeline is sequentially communicated with the heat medium side of the intermediate-temperature-stage cooling evaporator 6, the heat medium side of the low-temperature-stage cooling evaporator 9, a first throttle valve 10, a liquid inlet of a first gas-liquid separator 12, a second throttle valve 13 and a liquid inlet of a second gas-liquid separator 15; the gas outlet of the second gas-liquid separator 15 is sequentially communicated with low-temperature CO2Compressor 1, medium and low temperature CO2Compressor 2, medium-high temperature CO2Compressor 3, high temperature CO2Compressor 4 and CO2An inlet on the heat medium side of the gas cooler 5; the liquid outlet of the second gas-liquid separator 15 is communicated with CO in sequence2A secondary inflow port of the second ejector 8 and a refrigerant side of the low-temperature evaporator 14; the gas outlet of the first gas-liquid separator 12 is communicated with the medium-low temperature CO2The inlet of the compressor 2 and the liquid outlet of the first gas-liquid separator 12 which is not communicated with the second throttling valve 13 are sequentially communicated with CO2A secondary inflow port of the first ejector 7 and the refrigerant side of the intermediate-temperature-stage evaporator 11; the second pipeline is divided into two paths, one path of pipeline is communicated with the main flow inlet of the first ejector 7, and the other path of pipeline is communicated with the main flow inlet of the second ejector 8; CO 22The inlet of the gas cooler 5 is communicated with high-temperature CO2Outlet of compressor 4, high temperature CO2Inlet of compressor 4 and intermediate temperature stage cooling evaporator6, the outlet of the low-temperature stage cooling evaporator 9 and the outlet of the high-temperature CO side are communicated with each other2A medium-high temperature CO is arranged on a communication pipeline between the inlet of the compressor 4 and the outlet of the refrigerant side of the low-temperature stage cooling evaporator 92 A compressor 3.
Injecting outlet gas of the low-temperature evaporator and the medium-temperature evaporator respectively through double injectors to form two different evaporation temperatures and to CO2The fluid is cooled, the pressure reduction effect can be achieved without a throttle valve in the process, throttling loss is reduced, the pressure of the outlet of the ejector is higher than the evaporating pressure of the corresponding evaporator, the suction pressure of the compressor is improved, the compression ratio and the exhaust temperature of the compressor are reduced, and the system performance is improved. Further, the first gas-liquid separator 12 and the second gas-liquid separator 15 are provided so that inflow CO is introduced2Intermediate temperature stage evaporator and CO2The working medium of the low-temperature evaporator is saturated liquid, and compared with the traditional gas-liquid two-phase fluid, the refrigerant is uniformly distributed in each parallel pipeline of the evaporator, so that the heat exchange efficiency is greatly improved, the heat exchange area of the evaporator can be reduced, and the low-temperature evaporator has better economical efficiency.
As an optional implementation mode, the heat exchange working medium of the injection supercharging two-stage series connection supercooling double-temperature-zone refrigerating system is CO2。CO2The ODP is 0, the GWP is 1, the decomposition is not generated under the high temperature condition, and the method is safe, non-toxic and environment-friendly.
As an alternative embodiment of the present invention, CO2The heat exchange fluid on the refrigerant side of the gas cooler 5 can be water or gas according to the process requirements, and high-temperature hot water or high-temperature steam can be obtained through heat exchange. CO 22Refrigerant side and CO of intermediate temperature stage evaporator 112The heat exchange fluid on the refrigerant side of the low temperature stage evaporator 14 is air.
As an alternative embodiment of the present invention, CO2The gas cooler 5 is a double pipe heat exchanger or a plate heat exchanger, preferably a double pipe heat exchanger; medium temperature stage cooling evaporator 6, low temperature stage cooling evaporator 9, CO2Intermediate temperature stage evaporator 11, CO2The low-temperature evaporator 14 adopts a sleeve type evaporator and a sleeve type evaporator respectivelyEvaporator, finned tube evaporator.
As an alternative embodiment of the present invention, CO2The evaporation temperature range of the low-temperature stage evaporator 14 is-56 to-20 ℃, and CO is2The temperature range of the medium-temperature-stage evaporator 11 is-20-10 ℃, the temperature range of the medium-temperature-stage cooling evaporator 6 is 10-30 ℃, and the temperature range of the low-temperature-stage cooling evaporator 9 is-10-20 ℃. Low temperature CO2The suction pressure range of the compressor 1 is 0.53-1.97 MPa, and the exhaust pressure range is 1.97-4.50 MPa; medium and low temperature CO2The suction pressure range of the compressor 2 is 1.97-4.50 MPa, and the exhaust pressure range is 2.65-5.73 MPa; medium and high temperature CO2The suction pressure range of the compressor 3 is 2.65-5.73 MPa, and the exhaust pressure range is 4.50-7.21 MPa; high temperature CO2The suction pressure of the compressor 4 is 4.50-7.21 MPa, and the discharge pressure is 7.50-14 MPa. The secondary flow of the first ejector 7 has the air suction temperature ranging from-20 ℃ to 10 ℃, the pressure ranging from 1.97MPa to 4.50MPa, the main flow temperature ranging from 20 ℃ to 45 ℃, the pressure ranging from 7.5 MPa to 14MPa, the outlet temperature ranging from 10 ℃ to 30 ℃ and the pressure ranging from 2.65 MPa to 5.73 MPa. The secondary flow of the second ejector 8 has the air suction temperature ranging from-56 ℃ to-20 ℃, the pressure ranging from 0.53 MPa to 1.97MPa, the main flow temperature ranging from 20 ℃ to 45 ℃, the pressure ranging from 7.5 MPa to 14MPa, the outlet temperature ranging from-10 ℃ to 20 ℃ and the pressure ranging from 2.65 MPa to 5.73 MPa.
When in use, the catalyst is prepared from CO2Low temperature stage evaporator 14, CO2Intermediate temperature stage evaporator 11, low temperature CO2Compressor 1, medium and low temperature CO2Compressor 2, medium-high temperature CO2Compressor 3, high temperature CO2Compressor 4, CO2The transcritical CO is composed of a gas cooler 5, a medium-temperature stage cooling evaporator 6 (specifically a heat medium side), a first ejector 7, a second ejector 8, a low-temperature stage cooling evaporator 9 (specifically a heat medium side), a first throttle valve 10, a first gas-liquid separator 12, a second throttle valve 13 and a second gas-liquid separator 152The double-temperature-zone refrigeration cycle is completed by a first ejector 7, a second ejector 8, a medium-temperature-stage cooling evaporator 6 (specifically a refrigerant side), a low-temperature-stage cooling evaporator 9 (specifically a refrigerant side) and the likeThe specific working principle of the two-stage series supercooling method for supercharging by the ejector is as follows (see a pressure-enthalpy diagram of fig. 2):
the first step is as follows: low temperature and low pressure CO at gas outlet of second gas-liquid separator 152Gas a is low-temperature CO2The compressor 1 sucks in CO compressed to medium temperature and pressure2Fluid b is then mixed with CO from the gas outlet of the first gas-liquid separator 122Mixing the fluid d to a state c, flowing through a section of pipeline, and then being subjected to medium-low temperature CO2The compressor 2 sucks in the CO which is continuously compressed and compressed2Fluid e and CO at the outlet of the low temperature side (i.e. refrigerant side) of the low temperature stage cooling evaporator 92Mixing the fluid g, flowing through a section of pipeline, and then being subjected to medium-high temperature CO2The compressor 3 sucks in the CO to continue compression, and the compressed CO2Fluid h and CO at the outlet of the low-temperature side (i.e. refrigerant side) of the intermediate-temperature stage cooling evaporator 62Mixing the fluid j to a state i, flowing through a section of pipeline and then being subjected to high-temperature CO2The compressor 4 sucks in the CO to continue to compress the CO to high-temperature and high-pressure CO2Fluid k, then into CO2Gas cooler 5 exchanges heat with a heat exchange fluid, CO2Gas cooler 5 outlet CO2The fluid l is divided into two paths, one path flows into the high-temperature side (namely the heat medium side) of the medium-temperature-stage cooling evaporator 6; the other path of the mixed gas flows through a section of pipeline and then flows into main flow inlets of a first ejector 7 and a second ejector 8 respectively, and CO flows into the main flow inlets2The fluid is supercooled to a state m in the intermediate temperature stage cooling evaporator 6, flows into the low temperature stage cooling evaporator 9, is continuously cooled to a state n, and then CO2The fluid flows through the first throttle valve 10, throttled and cooled to the state q and then flows into the first gas-liquid separator 12, the liquid in the first gas-liquid separator 12 is divided into two paths, one path of CO2The fluid flows through the second throttle valve 13, is throttled and cooled to the state t, and then flows into the second gas-liquid separator 15; another CO path2Fluid flow through CO2The intermediate-temperature stage evaporator 11 performs evaporation and heat absorption to a state d, and then CO2The fluid flows into the secondary inlet of the first ejector 7 and CO in the second gas-liquid separator 152Liquid flow through CO2The low temperature stage evaporator 14 performs evaporation heat absorption to a state a, and then CO2The fluid flows into the secondary inlet of the second ejector 8, and the outlet CO of the first ejector 72Fluid flows into the intermediate temperature stage cooling evaporator 6The low temperature side (i.e., the refrigerant side); outlet CO of the second ejector 82The fluid flows into the low-temperature side of the low-temperature stage cooling evaporator 9, and the steps are repeated in this way, so that the trans-critical CO is completed2Double temperature zone refrigeration cycle.
The second step is that: CO 22The high-temperature high-pressure fluid at the outlet of the gas cooler 5 is divided into two paths, wherein one path enters the main flow inlet of the first ejector 7 and the main flow inlet of the second ejector 8 for isentropic expansion, the flow rate is increased, and the pressure is reduced; flow through CO2Low temperature stage evaporator 14 and CO2CO of the intermediate-temperature stage evaporator 112The fluid is the secondary flow of the second ejector 8 and the first ejector 7 respectively, the secondary flow is continuously sucked into the suction chambers of the first ejector 7 and the second ejector 8 by the low-pressure main flow and is mixed with the low-pressure main flow in the corresponding mixing chamber, the mixed fluid enters the corresponding diffusion chamber, the fluid speed is reduced, the pressure is increased to be between the main flow and the secondary fluid, high evaporation pressure is realized, the states of the mixed fluid at the outlets of the first ejector 7 and the second ejector 8 are o and p respectively, and the mixed fluid respectively flows into CO at the low-temperature side (namely the refrigerant side) of the medium-temperature-stage cooling evaporator 6, at the low-temperature side (namely the refrigerant side) of the low-temperature-stage cooling evaporator 9, at the high-temperature side (namely the heat medium side) of the medium-temperature-stage cooling evaporator 6 and at the high-temperature side (namely the heat medium side) of the low2Fluid heat exchange to saturated gas state g and j, high temperature side CO2The temperature of the fluid is lowered by cooling. High temperature side CO2The fluid is cooled twice at different temperature levels, and CO is generated in each supercooling process2The temperature drop is not high, good temperature matching is formed, the irreversible loss of heat exchange is reduced, a large supercooling degree is obtained, and the supercharging two-stage series supercooling of the ejector is completed.
The third step: heat transfer fluid inflow CO2The heat exchange fluid side of the gas cooler 5 is heated to the temperature required by the process to obtain the required medium-high temperature hot water or high-temperature steam, and the heating process of the heat exchange fluid is completed. Air flow through CO2Intermediate temperature stage evaporator 11 and CO2The low temperature stage evaporator 14 side cools the heat exchange fluid to complete the refrigeration process.
In the above process, one of the preferable process conditions that can be adopted is: CO 22The evaporation temperature of the low-temperature stage evaporator 14 is-30 ℃, and CO is2The temperature of the medium-temperature stage evaporator 11 is-5 ℃, the temperature of the medium-temperature stage cooling evaporator 6 is 18 ℃, and the temperature of the low-temperature stage cooling evaporator 9 is 5 ℃. Low temperature CO2The suction pressure of the compressor 1 is 1MPa, and the exhaust pressure is 3 MPa; medium and low temperature CO2The suction pressure of the compressor 2 is 2.5MPa, and the exhaust pressure is 4 MPa; medium and high temperature CO2The suction pressure of the compressor 3 is 4MPa, and the exhaust pressure is 6 MPa; high temperature CO2The suction pressure of the compressor 4 was 6MPa, and the discharge pressure was 12 MPa. The air suction temperature of the secondary flow of the first ejector 7 is 0 ℃, the pressure range is 3MPa, the main flow temperature range is 30 ℃, the pressure range is 11MPa, the outlet temperature of the first ejector 7 is 20 ℃, and the pressure is 4 MPa. The secondary flow of the second ejector 8 has the air suction temperature of-40 ℃, the pressure range of 1.2MPa, the main flow temperature of 30 ℃, the pressure of 10MPa, the outlet temperature range of 5 ℃ and the pressure of 4 MPa.
It should be noted that the suction chamber, the mixing chamber and the diffusion chamber are all components of the ejector, and the first ejector and the second ejector are conventional existing ejectors.
Injection pressure boost doublestage series connection subcooling dual-temperature-zone refrigerating system, can extensively be used for the food refrigeration field, particularly: its transcritical CO2The dual temperature zone can meet the requirements of two different temperature levels, CO2The middle-temperature evaporator has slightly higher evaporation temperature and can store dairy products, vegetables, fruits, eggs and the like; and CO2The low-temperature evaporator has relatively low evaporation temperature and can store meat, fish and other food.
The above description is only a preferred embodiment of the present invention, and should not be taken as limiting the invention, and any modifications, equivalent replacements, improvements, etc. made within the spirit and principle of the present invention should be included in the protection scope of the present invention.
Claims (9)
1. The utility model provides an injection pressure boost doublestage series connection subcooling dual temperature area refrigerating system which characterized in that: comprising CO2A gas cooler (5);
CO2one way of outlet of heat medium side of gas cooler (5)The pipeline is communicated with a heat medium side of the middle-temperature stage cooling evaporator (6), a heat medium side of the low-temperature stage cooling evaporator (9), a first throttling valve (10), a liquid inlet of a first gas-liquid separator (12), a second throttling valve (13) and a liquid inlet of a second gas-liquid separator (15) in sequence; the gas outlet of the second gas-liquid separator (15) is sequentially communicated with low-temperature CO2Compressor (1), medium and low temperature CO2Compressor (2), medium-high temperature CO2Compressor (3), high temperature CO2Compressor (4) and CO2An inlet on the heat medium side of the gas cooler (5); the liquid outlet of the second gas-liquid separator (15) is communicated with CO in sequence2A secondary inflow port of the second ejector (8) and on the refrigerant side of the low-temperature evaporator (14); the gas outlet of the first gas-liquid separator (12) is communicated with the medium-low temperature CO2The inlet of the compressor (2) and the liquid outlet of the first gas-liquid separator (12) which is not communicated with the second throttling valve (13) are sequentially communicated with CO2The refrigerant side of the intermediate-temperature-stage evaporator (11) and the secondary inflow port of the first ejector (7);
CO2the other pipeline of the outlet of the heat medium side of the gas cooler (5) is divided into two pipelines, and one pipeline is sequentially communicated with the main flow inlet of the first ejector (7), the refrigerant side of the medium-temperature stage cooling evaporator (6) and high-temperature CO2Compressor (4) and CO2The inlet of the heat medium side of the gas cooler (5) and the other pipeline are sequentially communicated with the main flow inlet of the second ejector (8), the refrigerant side of the low-temperature stage cooling evaporator (9) and medium-high temperature CO2An inlet of the compressor (3).
2. The injection supercharging two-stage series connection supercooling double-temperature-zone refrigeration system according to claim 1, wherein: the heat exchange working medium of the injection supercharging two-stage series connection supercooling double-temperature-zone refrigerating system is CO2。
3. The injection supercharging two-stage series connection supercooling double-temperature-zone refrigeration system according to claim 1, wherein: CO 22The heat exchange fluid on the refrigerant side of the gas cooler (5) is water or air.
4. The injection supercharging two-stage series connection supercooling two-temperature-zone refrigeration system according to claim 1, wherein the injection supercharging two-stage series connection supercooling two-temperature-zone refrigeration systemIs characterized in that: CO 22Refrigerant side and CO of intermediate temperature stage evaporator (11)2The heat exchange fluid on the refrigerant side of the low-temperature stage evaporator (14) is air.
5. The injection supercharging two-stage series connection supercooling double-temperature-zone refrigeration system according to claim 1, wherein: CO 22The gas cooler (5) is a double-pipe heat exchanger or a plate heat exchanger; a medium temperature stage cooling evaporator (6), a low temperature stage cooling evaporator (9), CO2Medium temperature stage evaporator (11), CO2The low-temperature evaporator (14) respectively adopts a sleeve type evaporator, a finned tube evaporator and a finned tube evaporator.
6. The injection supercharging two-stage series connection supercooling double-temperature-zone refrigeration system according to claim 1, wherein: CO 22The evaporation temperature range of the low-temperature stage evaporator (14) is-56 to-20 ℃, and CO is2The temperature range of the medium-temperature stage evaporator (11) is-20-10 ℃, the temperature range of the medium-temperature stage cooling evaporator (6) is 10-30 ℃, and the temperature range of the low-temperature stage cooling evaporator (9) is-10-20 ℃.
7. The injection supercharging two-stage series connection supercooling double-temperature-zone refrigeration system according to claim 1, wherein: low temperature CO2The suction pressure range of the compressor (1) is 0.53-1.97 MPa, and the exhaust pressure range is 1.97-4.50 MPa; medium and low temperature CO2The suction pressure range of the compressor (2) is 1.97-4.50 MPa, and the exhaust pressure range is 2.65-5.73 MPa; medium and high temperature CO2The suction pressure range of the compressor (3) is 2.65-5.73 MPa, and the exhaust pressure range is 4.50-7.21 MPa; high temperature CO2The air suction pressure range of the compressor (4) is 4.50-7.21 MPa, and the exhaust pressure range is 7.50-14 MPa.
8. The injection supercharging two-stage series connection supercooling double-temperature-zone refrigeration system according to claim 1, wherein: the secondary flow of the first ejector (7) has the air suction temperature ranging from-20 ℃ to 10 ℃, the pressure ranging from 1.97MPa to 4.50MPa, the main flow temperature ranging from 20 ℃ to 45 ℃, the pressure ranging from 7.5 MPa to 14MPa, the outlet temperature ranging from 10 ℃ to 30 ℃ and the pressure ranging from 2.65 MPa to 5.73 MPa.
9. The injection supercharging two-stage series connection supercooling double-temperature-zone refrigeration system according to claim 1, wherein: the secondary flow of the second ejector (8) has the air suction temperature ranging from-56 ℃ to-20 ℃, the pressure ranging from 0.53 MPa to 1.97MPa, the main flow temperature ranging from 20 ℃ to 45 ℃, the pressure ranging from 7.5 MPa to 14MPa, the outlet temperature ranging from-10 ℃ to 20 ℃ and the pressure ranging from 2.65 MPa to 5.73 MPa.
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| CN110701810A (en) * | 2019-10-29 | 2020-01-17 | 中机国能炼化工程有限公司 | Injection supercharging two-stage series connection supercooling double-temperature-zone refrigerating system and application |
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