CN110513926A - Twin-stage throttling non-azeotropic working medium mechanical super cooling CO2Trans-critical cycle cooling cycle system - Google Patents
Twin-stage throttling non-azeotropic working medium mechanical super cooling CO2Trans-critical cycle cooling cycle system Download PDFInfo
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- CN110513926A CN110513926A CN201910834769.6A CN201910834769A CN110513926A CN 110513926 A CN110513926 A CN 110513926A CN 201910834769 A CN201910834769 A CN 201910834769A CN 110513926 A CN110513926 A CN 110513926A
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- 238000004781 supercooling Methods 0.000 title claims abstract description 42
- 238000001816 cooling Methods 0.000 title claims abstract description 39
- 238000005057 refrigeration Methods 0.000 claims abstract description 21
- 239000007788 liquid Substances 0.000 claims abstract description 11
- 239000003507 refrigerant Substances 0.000 claims description 20
- 238000007906 compression Methods 0.000 claims description 3
- 230000006835 compression Effects 0.000 claims description 2
- 238000009833 condensation Methods 0.000 claims description 2
- 230000005494 condensation Effects 0.000 claims description 2
- 230000008878 coupling Effects 0.000 claims description 2
- 238000010168 coupling process Methods 0.000 claims description 2
- 238000005859 coupling reaction Methods 0.000 claims description 2
- 238000000034 method Methods 0.000 abstract description 16
- 239000012530 fluid Substances 0.000 abstract description 10
- 230000002427 irreversible effect Effects 0.000 abstract description 5
- 238000001704 evaporation Methods 0.000 description 12
- 230000008020 evaporation Effects 0.000 description 10
- 235000009508 confectionery Nutrition 0.000 description 3
- 230000007423 decrease Effects 0.000 description 3
- 229920006395 saturated elastomer Polymers 0.000 description 3
- CBENFWSGALASAD-UHFFFAOYSA-N Ozone Chemical compound [O-][O+]=O CBENFWSGALASAD-UHFFFAOYSA-N 0.000 description 2
- 230000006378 damage Effects 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 230000007613 environmental effect Effects 0.000 description 2
- 231100000252 nontoxic Toxicity 0.000 description 2
- 230000003000 nontoxic effect Effects 0.000 description 2
- 230000004224 protection Effects 0.000 description 2
- 238000004378 air conditioning Methods 0.000 description 1
- 230000006837 decompression Effects 0.000 description 1
- 230000007812 deficiency Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000002156 mixing Methods 0.000 description 1
- 230000000505 pernicious effect Effects 0.000 description 1
- 230000008092 positive effect Effects 0.000 description 1
- 238000003825 pressing Methods 0.000 description 1
- 238000010025 steaming Methods 0.000 description 1
- 230000005619 thermoelectricity Effects 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
- 238000010792 warming Methods 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
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
- F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/30—Expansion means; Dispositions thereof
- F25B41/31—Expansion valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
- F25B43/006—Accumulators
-
- 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
- F25B9/10—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point with several cooling stages
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Power Engineering (AREA)
- Lubricants (AREA)
Abstract
The invention discloses a kind of twin-stage throttling non-azeotropic working medium mechanical super cooling CO2Trans-critical cycle cooling cycle system.CO of the present invention2Trans-critical cycle cooling cycle system includes gas cooler, medium temperature grade cooling evaporator, low-temperature level cooling evaporator, expansion valve, evaporator, compressor；Non-azeotropic working medium mechanical super cooling twin-stage circulating with choke system includes medium temperature grade compressor, condenser, liquid storage device, medium temperature grade throttle valve, low-temperature level throttle valve, low-temperature level compressor.It can be to CO by non-azeotropic working medium supercharging mechanical circulation2The CO of recyclegas cooler outlet2Fluid carries out primary and secondary cooling, reduces restriction loss, improves system entirety efficiency.SAPMAC method is crossed by twin-stage throttling non-azeotropic working medium mechanical-assisted, heat exchange is set to form more good Temperature Matching, it reduces heat transfer temperature difference, reduce the irreversible loss of process, and then reduce the heat transfer irreversible loss of condenser and evaporator, be improved the efficiency of refrigeration cycle.
Description
Technical field
The present invention relates to refrigeration technology fields, more particularly to a kind of twin-stage throttling non-azeotropic working medium mechanical super cooling CO2Across
Critical refrigeration cycle system.
Background technique
As global warming, ozone layer such as are destroyed at the increasingly prominent of environmental problems, there is destruction to ozone layer to substitute
The working medium such as effect and CFCs, HCFCs, HFCs for generating greenhouse effects, the natural refrigerants for finding novel close friend become system
The research emphasis of cold field of air conditioning.Wherein, CO2By causing the universal of people in advantages such as its nontoxic non-combustible, safety and environmental protections
Concern.
But due to CO2Lower critical-temperature and higher critical pressure, make that its restriction loss is big, refrigerating efficiency is lower,
Especially when environment temperature is higher, CO2Refrigerating capacity sharply decline.If to the CO of gas cooler outlet2Fluid carries out
Supercooling, with the increase of degree of supercooling, restriction loss is reduced, and circulation cooling capacity increases, and circulation COP is promoted.CO2Refrigeration cycle
Supercooling can be realized by modes such as internal exchanger, mechanical super cooling, thermoelectricity supercoolings.Some scholars are used for CO to mechanical super cooling2Across
Critical refrigeration cycle has carried out theoretical research, i.e., by Vapor Compression Refrigeration Cycle to major cycle (CO2Trans-critical cycle refrigeration cycle)
The CO of gas cooler outlet2It is cooled down.Mechanical super cooling can not only increase refrigerating capacity, and can reduce the fortune of major cycle
Horizontal high voltage reduces Compressor Discharge Pressure, extends the service life of compressor
Conventional mechanical crosses SAPMAC method and is all made of pure refrigerant, and evaporative phase-change process temperature remains unchanged, but supercritical CO2Stream
Body cooling procedure is temperature-fall period, and the two heat transfer process temperature mismatches, and causes heat transfer process irreversible loss big.And for
Environment temperature is higher, the lower application places of evaporating temperature, CO2Degree of supercooling is up to 20 DEG C or more.Mechanical super cooling refrigeration cycle is cold
Solidifying side exchanges heat with air, evaporation side and CO2Fluid exchanges heat, and the temperature rise of air side is usually no more than 8 DEG C, and CO2Temperature
It is reduced to 20 DEG C or so.
If mechanical super cooling circulation uses non-azeotropic working medium, evaporation and the temperature glide for condensing phase transition process are close, cold
Solidifying side and evaporation side cannot simultaneously with air and CO2Good Temperature Matching is formed, so that biggish irreversible damage can be caused again
It loses.
Summary of the invention
Present invention aims to overcome above-mentioned the deficiencies in the prior art, and it is non-total to provide a kind of twin-stage throttling
Boil working medium mechanical super cooling CO2Trans-critical cycle cooling cycle system.
The present invention is by mechanical super cooling refrigeration cycle and CO2Trans-critical cycle refrigeration cycle forms, wherein mechanical super cooling refrigeration cycle
For the vapor-compression refrigerant cycle of two evaporating pressures, refrigerant is the reasonable mix refrigerant CO of temperature glide2/R1234ze、
CO2/ R1234yf, R41/R1234ze, R41/R1234yf, R32/R1234ze, R32/R1234yf or R32/R600a.
The circulatory system of the present invention is by non-azeotropic working medium mechanical super cooling twin-stage circulating with choke system and CO2Trans-critical cycle refrigeration cycle
System coupling composition；
The CO2Trans-critical cycle cooling cycle system includes gas cooler, medium temperature grade cooling evaporator, the cooling steaming of low-temperature level
Send out device, expansion valve, evaporator, compressor；The compressor outlet is connected with gas cooler entrance, gas cooler outlet with
Medium temperature grade cooling evaporator entrance is connected, and the medium temperature grade cooling evaporator outlet is connected with low-temperature level cooling evaporator entrance,
Low-temperature level cooling evaporator outlet connect with expansion valve inlet, expansion valve outlet is connected with evaporator inlet, evaporator inlet and
Compressor is connected；
The non-azeotropic working medium mechanical super cooling twin-stage circulating with choke system include medium temperature grade compressor, condenser, liquid storage device,
Medium temperature grade throttle valve, low-temperature level throttle valve, low-temperature level compressor；The medium temperature stage compressor outlet is connected with condenser inlet,
Condensator outlet with medium temperature throttle valve and cryogenic throttle valve first via being connected respectively after liquid storage device, medium temperature throttling valve outlet and medium temperature
Cooling evaporator entrance is connected, and the outlet of medium temperature cooling evaporator is connected with medium temperature suction port of compressor, constitutes the first circuit；It is described low
Temperature throttling valve outlet is connected with sub-cooled evaporator inlet, sub-cooled evaporator outlet and low-temperature level suction port of compressor phase
Even, low temperature stage compressor outlet is connected with medium temperature grade suction port of compressor, constitutes second servo loop.
The medium temperature cooling evaporator and sub-cooled evaporator are counter-flow heat exchanger.
CO2Trans-critical cycle refrigeration cycle refrigerant uses natural refrigerant CO2, non-azeotropic working medium mechanical super cooling twin-stage circulating with choke
Refrigerant is CO2/R1234ze、CO2/R1234yf、R41/R1234ze、R41/R1234yf、 R32/R1234ze、R32/
R1234yf or R32/R600a.
The advantages and positive effects of the present invention are:
(1)CO2The refrigerant of refrigeration system is natural refrigerant CO2。CO2GWP be 1, ODP 0, it is safe and non-toxic it is non-combustible,
It is cheap easily to obtain, do not decompose generation pernicious gas, mechanical super cooling cycle fluid CO under the high temperature conditions yet2/R1234ze、CO2/
The GWP of R1234yf, R41/R1234ze, R41/R1234yf, R32/R1234ze, R32/R1234yf or R32/R600a are lower,
Refrigerant used in system is environmental-friendly refrigerant.
(2) mechanical super cooling circulation uses mixed non-azeotropic refrigerant CO2/R1234ze、CO2/R1234yf、 R41/
R1234ze, R41/R1234yf, R32/R1234ze, R32/R1234yf or R32/R600a are as working medium, and refrigerant is in condenser
In with air form good Temperature Matching.Refrigerant throttles twice, recycles the twice evaporation process different there are high/low temperature,
The evaporation process and CO of middle higher temperature2Level-one is subcooled to form good Temperature Matching, the evaporation process and CO of lower temperature2Two
Grade supercooling carries out preferable Temperature Matching, finally further reduced CO2The outlet temperature of gas cooler.Mechanical super cooling circulation
Evaporation side and the heat exchange irreversible loss of condensation side reduce, circulation overall performance improves.
(3) by mechanical super cooling system to CO2The CO of system gas cooler outlet2It is subcooled, is lowered into expansion valve
Preceding CO2Temperature reduces expansion-loss, and further decreases CO2Run high pressure.
Detailed description of the invention
Fig. 1 is twin-stage of the present invention throttling non-azeotropic working medium mechanical super cooling CO2The CO of Trans-critical cycle cooling cycle system2Trans-critical cycle
The Sweet service of refrigeration cycle；
Fig. 2 is twin-stage of the present invention throttling non-azeotropic working medium mechanical super cooling CO2The twin-stage of Trans-critical cycle cooling cycle system throttles
The Sweet service of non-azeotropic working medium mechanical super cooling；
Fig. 3 is twin-stage of the present invention throttling non-azeotropic working medium mechanical super cooling CO2The schematic diagram of Trans-critical cycle cooling cycle system.
Specific embodiment
The present invention will be further described with reference to the accompanying drawing.
As shown in Figure 1, the present invention includes the twin-stage throttling non-azeotropic working medium mechanical super cooling circulatory system and CO2Trans-critical cycle refrigeration
The circulatory system, heavy line CO2Trans critical cycle (1 ' -2 ' -3 ' -4 ' -5 ' -6 ' -1 '), fine line are twin-stage throttling non-azeotrope work
The low-temperature evaporation process (8-1) and high temperature evaporation process (7-3) of matter mechanical super cooling circulation.Fig. 2 is non-azeotropic working medium of the present invention increasing
CO is subcooled in press mechanical pressing2The Sweet service of the auxiliary supercooling refrigeration cycle of Trans-critical cycle cooling cycle system, wherein 3 ' -4 ' be CO2Level-one
Subcooling process, 4 ' -5 ' be CO2Second level subcooling process.
Present system is as shown in Figure 3:
Step 1: compressor 1 sucks the saturation CO of the low-temp low-pressure in 6 exit of evaporator2Gas compresses it into high temperature
The gas of high pressure, temperature reduces after being exchanged heat in gas cooler 2 with air, flows separately through medium temperature cooling evaporator later
3 exchange heat with sub-cooled evaporator 4 with mixed non-azeotropic refrigerant, realize CO2Fluid supercooling, enters back into 5 section of throttle valve
Stream decompression, becomes gas-liquid two-phase state.Become overheated gas after 6 evaporation endothermic of evaporator again and enter compressor, completes CO2Across
Critical cycle.
Step 2: mechanical super cooling circulation low-temperature level compressor 12 absorbs the low-temp low-pressure in 4 exit of sub-cooled evaporator
Refrigerant compresses it into the overheated gas of medium temperature and medium pressure, enters after mixing with the saturated gas that medium temperature cooling evaporator 3 exports
Medium temperature grade compressor 7, is compressed into high temperature and high pressure gas, into condenser 8 and air heat-exchange.Refrigerant enters liquid storage device 9 later,
Become the gas-liquid two-phase fluid of medium temperature and medium pressure after 10 expansion throttling of medium temperature grade throttle valve all the way, another way passes through low-temperature level section
Become the gas-liquid two-phase fluid of low-temp low-pressure after stream 11 expansion throttling of valve.
Step 3: the non-azeotropic working medium gas-liquid two-phase fluid of mechanical super cooling circulation medium temperature and medium pressure passes through medium temperature cooling evaporator
3 and CO2It carries out primary heat exchange and becomes saturated gas, the gas-liquid two-phase fluid of low-temp low-pressure passes through sub-cooled evaporator 4 and CO2
It exchanges heat, further decreases CO2The temperature of fluid, non-azeotropic working medium ultimately become saturated gas.
Although the preferred embodiment of the present invention is described above in conjunction with attached drawing, the invention is not limited to upper
The specific embodiment stated, the above mentioned embodiment is only schematical, be not it is restrictive, this field it is common
Technical staff under the inspiration of the present invention, without breaking away from the scope protected by the purposes and claims of the present invention, may be used also
By make it is many in the form of, within these are all belonged to the scope of protection of the present invention.
Claims (3)
- The non-azeotropic working medium mechanical super cooling CO 1. a kind of twin-stage throttles2Trans critical cycle refrigeration system, which is characterized in that the circulatory system By non-azeotropic working medium mechanical super cooling twin-stage circulating with choke system and CO2Trans-critical cycle cooling cycle system coupling composition；The CO2Trans-critical cycle cooling cycle system include gas cooler, medium temperature grade cooling evaporator, low-temperature level cooling evaporator, Expansion valve, evaporator, compressor；The compressor outlet is connected with gas cooler entrance, gas cooler outlet and medium temperature Grade cooling evaporator entrance is connected, and the medium temperature grade cooling evaporator outlet is connected with low-temperature level cooling evaporator entrance, low temperature The outlet of grade cooling evaporator is connect with expansion valve inlet, and expansion valve outlet is connected with evaporator inlet, evaporator inlet and compression Machine is connected；The non-azeotropic working medium mechanical super cooling twin-stage circulating with choke system includes medium temperature grade compressor, condenser, liquid storage device, medium temperature Grade throttle valve, low-temperature level throttle valve, low-temperature level compressor；The medium temperature stage compressor outlet is connected with condenser inlet, condensation First via being connected respectively with medium temperature throttle valve and cryogenic throttle valve after liquid storage device, medium temperature throttling valve outlet and medium temperature are cooling for device outlet Evaporator inlet is connected, and the outlet of medium temperature cooling evaporator is connected with medium temperature suction port of compressor；Cryogenic throttle valve outlet with it is low Warm cooling evaporator entrance is connected, and sub-cooled evaporator outlet is connected with low-temperature level suction port of compressor, and low-temperature level compressor goes out Mouth is connected with medium temperature grade suction port of compressor.
- The non-azeotropic working medium mechanical super cooling CO 2. twin-stage according to claim 1 throttles2Trans critical cycle refrigeration system, it is special Sign is that the medium temperature cooling evaporator and sub-cooled evaporator are counter-flow heat exchanger.
- The non-azeotropic working medium mechanical super cooling CO 3. twin-stage according to claim 1 throttles2Trans critical cycle refrigeration system, it is special Sign is, CO2Trans-critical cycle refrigeration cycle refrigerant uses natural refrigerant CO2, non-azeotropic working medium mechanical super cooling twin-stage circulating with choke system Cryogen is CO2/R1234ze、CO2/R1234yf、R41/R1234ze、R41/R1234yf、R32/R1234ze、R32/R1234yf Or R32/R600a.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910834769.6A CN110513926A (en) | 2019-09-05 | 2019-09-05 | Twin-stage throttling non-azeotropic working medium mechanical super cooling CO2Trans-critical cycle cooling cycle system |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910834769.6A CN110513926A (en) | 2019-09-05 | 2019-09-05 | Twin-stage throttling non-azeotropic working medium mechanical super cooling CO2Trans-critical cycle cooling cycle system |
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Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113776215A (en) * | 2021-09-18 | 2021-12-10 | 青岛科技大学 | Circulating system applied to cascade refrigeration or heat pump system and supercooling method |
| CN113956850A (en) * | 2021-10-18 | 2022-01-21 | 珠海格力电器股份有限公司 | Environment-friendly mixed refrigerant, preparation method thereof and refrigeration system |
| CN114992897A (en) * | 2022-05-07 | 2022-09-02 | 松下压缩机(大连)有限公司 | CO 2 Transcritical two-stage compression type air source heat pump system |
| US11796238B2 (en) * | 2020-08-28 | 2023-10-24 | Daikin Industries, Ltd. | Heat source unit and refrigeration apparatus |
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| JP2000161805A (en) * | 1998-11-27 | 2000-06-16 | Daikin Ind Ltd | Refrigerating apparatus |
| WO2008019689A2 (en) * | 2006-08-18 | 2008-02-21 | Knudsen Køling A/S | A transcritical refrigeration system with a booster |
| CN106828032A (en) * | 2017-01-24 | 2017-06-13 | 天津商业大学 | A kind of carbon dioxide automobile air conditioner system of both vapor compression auxiliary supercooling |
| CN210861850U (en) * | 2019-09-05 | 2020-06-26 | 天津商业大学 | Double-stage throttling non-azeotropic working medium mechanical supercooling CO2Transcritical refrigeration cycle system |
-
2019
- 2019-09-05 CN CN201910834769.6A patent/CN110513926A/en active Pending
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2000161805A (en) * | 1998-11-27 | 2000-06-16 | Daikin Ind Ltd | Refrigerating apparatus |
| WO2008019689A2 (en) * | 2006-08-18 | 2008-02-21 | Knudsen Køling A/S | A transcritical refrigeration system with a booster |
| CN106828032A (en) * | 2017-01-24 | 2017-06-13 | 天津商业大学 | A kind of carbon dioxide automobile air conditioner system of both vapor compression auxiliary supercooling |
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Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US11796238B2 (en) * | 2020-08-28 | 2023-10-24 | Daikin Industries, Ltd. | Heat source unit and refrigeration apparatus |
| CN113776215A (en) * | 2021-09-18 | 2021-12-10 | 青岛科技大学 | Circulating system applied to cascade refrigeration or heat pump system and supercooling method |
| CN113956850A (en) * | 2021-10-18 | 2022-01-21 | 珠海格力电器股份有限公司 | Environment-friendly mixed refrigerant, preparation method thereof and refrigeration system |
| CN114992897A (en) * | 2022-05-07 | 2022-09-02 | 松下压缩机(大连)有限公司 | CO 2 Transcritical two-stage compression type air source heat pump system |
| CN114992897B (en) * | 2022-05-07 | 2024-03-26 | 冰山松洋压缩机(大连)有限公司 | CO 2 Transcritical two-stage compression type air source heat pump system |
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