CN111141050B - Injection supercharging cascade supercooling transcritical CO 2 System and application - Google Patents
Injection supercharging cascade supercooling transcritical CO 2 System and application Download PDFInfo
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- CN111141050B CN111141050B CN202010069095.8A CN202010069095A CN111141050B CN 111141050 B CN111141050 B CN 111141050B CN 202010069095 A CN202010069095 A CN 202010069095A CN 111141050 B CN111141050 B CN 111141050B
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- 238000002347 injection Methods 0.000 title claims abstract description 19
- 239000007924 injection Substances 0.000 title claims abstract description 19
- 238000004781 supercooling Methods 0.000 title claims abstract description 19
- 239000003507 refrigerant Substances 0.000 claims abstract description 32
- 239000012530 fluid Substances 0.000 claims description 16
- 238000005057 refrigeration Methods 0.000 claims description 13
- 238000000034 method Methods 0.000 abstract description 10
- 230000008569 process Effects 0.000 abstract description 10
- 230000002427 irreversible effect Effects 0.000 abstract description 5
- 238000001816 cooling Methods 0.000 description 7
- 229920006395 saturated elastomer Polymers 0.000 description 5
- 238000007906 compression Methods 0.000 description 3
- 230000007613 environmental effect Effects 0.000 description 3
- 238000001704 evaporation Methods 0.000 description 3
- 231100000252 nontoxic Toxicity 0.000 description 3
- 230000003000 nontoxic effect Effects 0.000 description 3
- 239000003153 chemical reaction reagent Substances 0.000 description 2
- 239000002131 composite material Substances 0.000 description 2
- 230000006835 compression Effects 0.000 description 2
- 238000004378 air conditioning Methods 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 238000007796 conventional method Methods 0.000 description 1
- 125000004122 cyclic group Chemical group 0.000 description 1
- 235000013365 dairy product Nutrition 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 238000013461 design Methods 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 238000005265 energy consumption Methods 0.000 description 1
- 230000008020 evaporation Effects 0.000 description 1
- 238000002474 experimental method Methods 0.000 description 1
- 239000002360 explosive Substances 0.000 description 1
- 238000010438 heat treatment Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 239000013535 sea water Substances 0.000 description 1
- 238000006467 substitution reaction Methods 0.000 description 1
- 238000012360 testing method Methods 0.000 description 1
- 238000010792 warming Methods 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
- F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
- F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
-
- 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
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B40/00—Subcoolers, desuperheaters or superheaters
- F25B40/02—Subcoolers
-
- 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
-
- 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
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Chemical Kinetics & Catalysis (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
The invention discloses an injection supercharging cascade supercooling transcritical CO 2 Systems and applications. The invention includes CO 2 Evaporator, CO 2 A compressor; the CO 2 The outlet of the evaporator is sequentially communicated with CO 2 Main flow inlet and CO of compressor and high-pressure ejector 2 An inlet of the gas cooler; CO 2 The outlet of the gas cooler is divided into two paths, wherein one path is communicated with the refrigerant side of the primary subcooler, the main flow inlet of the medium-pressure ejector and the secondary flow inlet of the high-pressure ejector; the other path is divided into two paths after being communicated with the heat medium side of the primary subcooler, and is respectively communicated with the refrigerant side of the secondary subcooler, the secondary flow inlet of the medium-pressure ejector, the heat medium side of the secondary subcooler and CO 2 An inlet of the evaporator. The invention creates the injection supercharging cascade supercooling transcritical CO 2 The system can reduce irreversible loss in the heat exchange process and improve the energy efficiency ratio of the whole system.
Description
Technical Field
The invention belongs to the technical field of refrigeration and heat pumps, and particularly relates to injection supercharging cascade supercooling transcritical CO 2 Systems and applications.
Background
With the development of society, energy and environmental problems are receiving extensive attention from society. For the field of refrigeration and air conditioning, according to the regulations of the basic cali amendment, the existing widely applied refrigerants such as R134a, R410A and the like are gradually reduced due to the defect of higher GWP. Therefore, it is important to find efficient and environmentally friendly alternative refrigerants.
Among the numerous refrigerants, CO 2 The environment-friendly composite material is nontoxic, nonflammable, ODP=0 and GWP=1, has obvious environmental protection advantages, and can be applied to the fields of automobile air conditioners, supermarket refrigeration, dairy plants, chilled seawater coolers, residential air conditioners and the like. However, the critical temperature is lower (31.1 ℃), the critical pressure is higher (7.38 MPa), the irreversible loss of throttling is large, and the cyclic COP is lower. For refrigeration CO with higher ambient temperature 2 CO with higher system or backwater temperature 2 System, gas cooler temperature is higher, resulting in CO 2 The system throttling loss is large, and the system performance is poor.
CO to gas cooler outlet by subcooling 2 The fluid is cooled, so that the COP of the whole system can be greatly improved. Conventional subcooling systems require a single vapor compression refrigeration system with a small amount of refrigeration to be configured to supply CO 2 Other synthetic refrigerants (R134 a, R290, R1234yf, etc.) are introduced into the system, so that the environment-friendly performance of the system is reduced, and the system is flammable and explosive or is high in price. Thus, can pass through CO 2 Self-evaporating phase change for CO at outlet of gas cooler 2 The fluid cools itself, and the whole system only needs to be filled with CO 2 A refrigerant having an improved energy efficiency ratio.
However CO 2 The optimal supercooling degree of the system is larger, if single-stage evaporative cooling is adopted, CO is generated 2 Supercritical fluid cooling process and CO 2 The evaporation process temperature of the fluid is not matched, resulting in a large irreversible loss.
Disclosure of Invention
The invention aims to provide an injection supercharging cascade supercooling transcritical CO 2 A system to overcome the shortcomings of the prior art.
The invention relates to injection supercharging cascade supercooling transcritical CO 2 System, CO 2 The outlet of the evaporator is sequentially communicated with CO 2 Main flow inlet and CO of compressor and high-pressure ejector 2 An inlet of the gas cooler;
the CO 2 The outlet of the gas cooler is divided into two paths, one path is sequentially communicated with the refrigerant side of the primary subcooler and the main inflow of the medium-pressure ejectorThe other path is sequentially communicated with the heat medium side of the primary subcooler and then is divided into two paths, one path is communicated with the refrigerant side of the secondary subcooler and the secondary flow inlet of the medium-pressure ejector, and the other path is communicated with the heat medium side of the secondary subcooler and CO 2 An inlet of the evaporator.
Further, CO 2 The high-temperature-stage throttle valve is arranged on a pipeline of the outlet of the gas cooler, which is communicated with the refrigerant side of the primary subcooler, the medium-temperature-stage throttle valve is arranged on a pipeline of the primary subcooler, which is communicated with the refrigerant side of the secondary subcooler, and the heat medium side of the secondary subcooler is communicated with CO 2 The pipeline for communicating the inlet of the evaporator is provided with a low-temperature-stage throttle valve.
Further, the heat exchange working media of the refrigerant side of the primary subcooler and the refrigerant side of the secondary subcooler adopt pure refrigerant CO 2 。
Further, CO 2 Evaporator, CO 2 Compressor, high-pressure ejector and CO 2 The heat exchange fluid of the gas cooler, the medium-pressure ejector, the heat medium side of the primary subcooler and the heat medium side of the secondary subcooler is CO 2 ；
Preferably, the main flow of the high-pressure ejector (3) has an air suction pressure range of 7.5-12.5 MPa, an air suction temperature range of 105-135 ℃, an air suction pressure range of 2.5-7.5 MPa, an air suction temperature range of 0-30 ℃, an outlet pressure range of 5.5-10.5 MPa and a temperature range of 85-115 ℃; the main flow of the medium pressure ejector (7) has an air suction pressure range of 3.5-8.5 MPa, an air suction temperature range of 5-35 ℃, an air suction pressure range of 1.5-6.5 MPa, an air suction temperature range of-10-20 ℃, an outlet pressure range of 2.5-7.4 MPa and a temperature range of 0-30 ℃.
Further, the CO 2 The gas cooler adopts a double-pipe heat exchanger; the CO 2 The evaporator adopts a fin-tube heat exchanger or a double-tube heat exchanger;
preferably, CO 2 Gas cooler, CO 2 The working temperature ranges of the evaporator are 30-140 ℃ and-35-10 ℃ respectively;
preferably, CO 2 The suction pressure of the compressor ranges from 1.97 MPa to 4.50MPa, and the discharge pressure ranges from 7.5MPa to 14MPa.
The invention also relates to the injection supercharging cascade supercooling transcritical CO 2 The system is applied to the field of refrigeration and heat pumps.
Compared with the prior art, the injection supercharging cascade supercooling transcritical CO 2 The system has the following advantages:
(1) Through the injection of the high-pressure injector, the CO entering after compression is reduced 2 The pressure of the gas cooler can obviously reduce CO 2 The design pressure of the gas cooler reduces the system cost.
(2) The use of the circulating medium-high pressure ejector and the medium-pressure ejector realizes the step pressure ejection in the circulating process, so that the CO with relatively low pressure is obtained 2 After the gas is boosted by the ejector, the gas directly enters the gas cooler for cooling, so that the compression process of the compressor is omitted, the energy consumption of the compressor is reduced, and the system COP is improved.
(3) CO to gas cooler outlet through twice supercooling cooling process 2 The fluid is subjected to gradient cooling, so that the temperature in the subcooler is more matched, gradient utilization of cold energy is realized, irreversible loss of the subcooler caused by heat exchange is obviously reduced, and CO is improved 2 Refrigeration efficiency of the refrigeration system.
(4) CO entering throttle valve through cooling process 2 The temperature of the fluid is obviously reduced, and CO can be greatly reduced 2 Irreversible loss in throttling process, increase CO 2 Refrigeration efficiency of the refrigeration system.
(5) The primary subcooler and the secondary subcooler are both connected through CO 2 Supercritical CO self-evaporation to gas cooler outlet 2 The fluid is cooled, other types of refrigerants are not introduced, and the system is ensured to only contain one natural working medium CO 2 The environment-friendly composite material is nonflammable, nontoxic, ODP=0, GWP=1, environment-friendly, and beneficial to relieving environmental problems such as global warming and the like at present.
Drawings
Fig. 1 is a simple structure schematic of the present invention.
Detailed Description
Unless defined otherwise, technical terms used in the following examples have the same meaning as commonly understood by one of ordinary skill in the art to which the inventive concepts pertain. 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 invention will be described in detail with reference to the following examples and drawings.
As shown in figure 1, an injection supercharging cascade supercooling transcritical CO 2 The system comprises a high-pressure ejector 3 and CO 2 High-pressure injection CO consisting of gas cooler 4, high-temperature-stage throttle valve 5 and primary subcooler 6 2 Primary supercooling; medium pressure injection CO composed of medium pressure injector 7, medium temperature level throttle valve 8 and secondary subcooler 9 2 Second-stage supercooling; high pressure injection CO 2 Primary supercooling, medium pressure injection CO 2 The secondary subcooling may form a cyclical heat exchange.
The concrete structure is as follows:
the CO 2 The outlet of the evaporator 1 is sequentially communicated with CO 2 Main flow inlet of compressor 2, high pressure ejector 3, and CO 2 An inlet of the gas cooler 4; the CO 2 The outlet of the gas cooler 4 is divided into two paths, one path is sequentially communicated with the refrigerant side of the primary subcooler 6, the main flow inlet of the medium-pressure ejector 7 and the secondary flow inlet of the high-pressure ejector 3, the other path is sequentially communicated with the heat medium side of the primary subcooler 6 and then divided into two paths, one path is communicated with the refrigerant side of the secondary subcooler 9 and the secondary flow inlet of the medium-pressure ejector 7, and the other path is communicated with the heat medium side of the secondary subcooler 9 and CO 2 An inlet of the evaporator 1.
As an alternative embodiment of the invention, in order to control the heat exchange fluid flow of the corresponding pipeline, the heat exchange fluid flow control device comprises a control unit for controlling the heat exchange fluid flow of the corresponding pipeline in the CO 2 The high-temperature-stage throttle valve 5 is arranged on a pipeline of which the outlet of the gas cooler 4 is communicated with the refrigerant side of the primary subcooler 6, the medium-temperature-stage throttle valve 8 is arranged on a pipeline of which the heat medium side of the primary subcooler 6 is communicated with the refrigerant side of the secondary subcooler 9, and the heat medium side of the secondary subcooler 9 is communicated with CO 2 A low-temperature-stage throttle valve is arranged on a pipeline communicated with the inlet of the evaporator 110。
Due to CO 2 Is the only nonflammable, nontoxic, refrigerant with odp=0 and gwp=1, classified as A1, and can operate below 0 without damaging the environment. Therefore, the heat exchange working media of the refrigerant side of the primary subcooler 6 and the refrigerant side of the secondary subcooler 9 of the invention adopt pure refrigerant CO 2 。
CO 2 Evaporator 1, CO 2 Compressor 2, high pressure ejector 3, CO 2 The heat exchange fluid of the gas cooler 4, the medium-pressure ejector 7, the heat medium side of the primary subcooler 6 and the heat medium side of the secondary subcooler 9 is CO 2 。
As an embodiment of the invention, the CO 2 The gas cooler 4 adopts a double pipe heat exchanger; the CO 2 The evaporator 1 adopts a fin-tube heat exchanger or a double-tube heat exchanger;
one preferred process condition is: the main flow of the high-pressure ejector 3 has an air suction pressure of 10MPa, an air suction temperature of 120 ℃, an air suction pressure of 5MPa for the secondary flow, an air suction temperature of 15 ℃, an outlet pressure of the high-pressure ejector of 8MPa and a temperature of 100 ℃; the main flow of the medium pressure ejector 7 has an air suction pressure of 6MPa, an air suction temperature of 20 ℃, an air suction pressure of 4MPa for the secondary flow, an air suction temperature of 5 ℃, an outlet pressure of 5MPa and a temperature of 15 ℃. CO 2 Gas cooler 4, CO 2 The working temperature of the evaporator 1 is 35 ℃ and minus 5 ℃ respectively; CO 2 The suction pressure of the compressor 2 was 3MPa and the discharge pressure was 10MPa.
When in use, injection pressurizing step supercooling transcritical CO is adopted 2 The refrigerating and heat exchanging process of the system comprises the following steps:
from CO 2 The fluid of the evaporator 1 enters the CO 2 The compressor 2 compresses the high-temperature high-pressure superheated steam into a main flow inlet of the high-pressure ejector 3, and ejects CO at an outlet of the medium-pressure ejector 7 2 Gas, enter CO 2 The gas cooler 4 exchanges heat with the heat exchange fluid, and the temperature is reduced; from CO 2 The outlet of the gas cooler 4 is divided into two paths, one path enters a high-temperature-stage throttle valve 5 for cooling and depressurization, then enters the refrigerant side of a primary subcooler 6, and the other path enters a primary bypassCO on the heat medium side of the cooler 6 2 Saturated gas flows into the main flow inlet of the medium-pressure ejector 7, and the other path of saturated gas enters the CO cooled on the heat medium side of the primary subcooler 6 2 Saturated gas is divided into two paths, one path flows into a medium-temperature-stage throttle valve 8 for throttling and depressurization, then flows into a refrigerant side of a second-stage subcooler 9, and cools CO of the other path flowing into a heating medium side of the second-stage subcooler 9 2 Saturated gas, then enters the inlet of secondary flow of the medium-pressure ejector 7, and the other flow enters the low-temperature-stage throttle valve 10 for throttling and reducing pressure and flows into CO 2 The inlet of the evaporator 1 releases low-temperature cold energy to the refrigerating space, and the evaporated saturated gas continues to circulate.
In the refrigerating and heat exchanging process, CO 2 The heat exchange fluid of the gas cooler is water.
The injection supercharging cascade supercooling transcritical CO 2 The system can improve the utilization rate of equipment, improve the energy efficiency ratio and save space, and can be applied to a plurality of refrigeration heat exchange fields.
The above embodiments are merely preferred embodiments of the present invention and are not intended to limit the present invention, and any modifications, equivalent substitutions, improvements, etc. within the spirit and principle of the present invention should be included in the protection scope of the present invention.
Claims (2)
1. Injection supercharging cascade supercooling transcritical CO 2 The system is characterized in that: comprising CO 2 An evaporator (1);
the CO 2 The outlet of the evaporator (1) is sequentially communicated with CO 2 Main flow inlet of compressor (2) and high pressure ejector (3), CO 2 An inlet of a gas cooler (4); the CO 2 The outlet of the gas cooler (4) is divided into two paths, one path is sequentially communicated with the refrigerant side of the primary subcooler (6), the main flow inlet of the medium-pressure ejector (7) and the secondary flow inlet of the high-pressure ejector (3), the other path is communicated with the heat medium side of the primary subcooler (6) and then divided into two paths, one path is communicated with the refrigerant side of the secondary subcooler (9) and the secondary flow inlet of the medium-pressure ejector (7), and the other path is communicated with the heat medium side of the secondary subcooler (9) and CO 2 An inlet of the evaporator (1);
CO 2 the high-temperature-stage throttle valve (5) is arranged on a pipeline of the outlet of the gas cooler (4) communicated with the refrigerant side of the primary subcooler (6), the medium-temperature-stage throttle valve (8) is arranged on a pipeline of the heat medium side of the primary subcooler (6) communicated with the refrigerant side of the secondary subcooler (9), and the heat medium side of the secondary subcooler (9) is communicated with CO 2 A low-temperature-stage throttle valve (10) is arranged on a pipeline communicated with the inlet of the evaporator (1);
the heat exchange working media of the refrigerant side of the primary subcooler (6) and the refrigerant side of the secondary subcooler (9) adopt pure refrigerant CO 2；
CO 2 Evaporator (1), CO 2 Compressor (2), high-pressure ejector (3), and CO 2 The heat exchange fluid of the heat medium side of the gas cooler (4), the medium pressure ejector (7), the primary subcooler (6) and the secondary subcooler (9) is CO 2 ;
The CO 2 The gas cooler (4) adopts a double-pipe heat exchanger; the CO 2 The evaporator (1) adopts a fin-tube heat exchanger or a double-tube heat exchanger.
2. The injection pressurized cascade supercooling transcritical CO of claim 1 2 The system is applied to the field of refrigeration and heat pumps.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010069095.8A CN111141050B (en) | 2020-01-21 | 2020-01-21 | Injection supercharging cascade supercooling transcritical CO 2 System and application |
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| Application Number | Priority Date | Filing Date | Title |
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| CN202010069095.8A CN111141050B (en) | 2020-01-21 | 2020-01-21 | Injection supercharging cascade supercooling transcritical CO 2 System and application |
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| CN111141050A CN111141050A (en) | 2020-05-12 |
| CN111141050B true CN111141050B (en) | 2024-03-26 |
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2020
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Patent Citations (11)
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|---|---|---|---|---|
| CN1910410A (en) * | 2004-09-22 | 2007-02-07 | 株式会社电装 | Ejector type refrigeration cycle |
| CN2916521Y (en) * | 2006-06-23 | 2007-06-27 | 中南大学 | Ejector type refrigerating machine |
| JP2008241192A (en) * | 2007-03-28 | 2008-10-09 | Mitsubishi Electric Corp | Refrigerating cycle device |
| JP2011185580A (en) * | 2010-03-11 | 2011-09-22 | Denso Corp | Ejector unit, heat exchanger unit, and refrigerant short-circuit detecting method of the ejector unit |
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| CN111141050A (en) | 2020-05-12 |
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