CN114674090A - Low-ambient-temperature heating air-conditioning system - Google Patents
Low-ambient-temperature heating air-conditioning system Download PDFInfo
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- CN114674090A CN114674090A CN202210378298.4A CN202210378298A CN114674090A CN 114674090 A CN114674090 A CN 114674090A CN 202210378298 A CN202210378298 A CN 202210378298A CN 114674090 A CN114674090 A CN 114674090A
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- 238000010438 heat treatment Methods 0.000 title claims abstract description 36
- 238000004378 air conditioning Methods 0.000 title claims abstract description 22
- 238000005057 refrigeration Methods 0.000 claims abstract description 37
- 239000003507 refrigerant Substances 0.000 claims description 94
- 238000002347 injection Methods 0.000 claims description 76
- 239000007924 injection Substances 0.000 claims description 76
- RYGMFSIKBFXOCR-UHFFFAOYSA-N Copper Chemical compound [Cu] RYGMFSIKBFXOCR-UHFFFAOYSA-N 0.000 claims description 27
- 229910052802 copper Inorganic materials 0.000 claims description 27
- 239000010949 copper Substances 0.000 claims description 27
- 239000007788 liquid Substances 0.000 claims description 24
- 230000008020 evaporation Effects 0.000 claims description 15
- 238000001704 evaporation Methods 0.000 claims description 15
- 238000000034 method Methods 0.000 claims description 6
- 230000006835 compression Effects 0.000 claims description 5
- 238000007906 compression Methods 0.000 claims description 5
- 229910001220 stainless steel Inorganic materials 0.000 claims description 5
- 239000010935 stainless steel Substances 0.000 claims description 5
- 239000013589 supplement Substances 0.000 claims description 5
- COCAUCFPFHUGAA-MGNBDDOMSA-N n-[3-[(1s,7s)-5-amino-4-thia-6-azabicyclo[5.1.0]oct-5-en-7-yl]-4-fluorophenyl]-5-chloropyridine-2-carboxamide Chemical compound C=1C=C(F)C([C@@]23N=C(SCC[C@@H]2C3)N)=CC=1NC(=O)C1=CC=C(Cl)C=N1 COCAUCFPFHUGAA-MGNBDDOMSA-N 0.000 claims description 2
- 230000000694 effects Effects 0.000 abstract description 7
- 230000001502 supplementing effect Effects 0.000 description 3
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 description 2
- 229910052782 aluminium Inorganic materials 0.000 description 2
- 230000007613 environmental effect Effects 0.000 description 2
- 239000011888 foil Substances 0.000 description 2
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000005219 brazing Methods 0.000 description 1
- 239000003245 coal Substances 0.000 description 1
- 230000006837 decompression Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000005485 electric heating Methods 0.000 description 1
- 238000005265 energy consumption Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
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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
- F25B7/00—Compression machines, plants or systems, with cascade operation, i.e. with two or more circuits, the heat from the condenser of one circuit being absorbed by the evaporator of the next circuit
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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
- F25B41/00—Fluid-circulation arrangements
- F25B41/30—Expansion means; Dispositions thereof
- F25B41/31—Expansion valves
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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
- F25B41/00—Fluid-circulation arrangements
- F25B41/40—Fluid line arrangements
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Other Air-Conditioning Systems (AREA)
Abstract
The invention relates to the technical field of ultra-low temperature environment temperature heating air-conditioning systems, in particular to a low environment temperature heating air-conditioning system which comprises four refrigeration cycles, wherein the refrigeration cycle system can effectively improve the heating capacity at low environment temperature, has obvious improvement effect on high temperature hot air at low environment temperature, can still produce hot air by a load side air conditioner when the environment temperature is below 50 ℃ below zero, has obvious heating effect, and is energy-saving and practical.
Description
Technical Field
The invention relates to the technical field of heating air-conditioning systems at ultralow ambient temperature, in particular to a heating air-conditioning system at low ambient temperature.
Background
The general heat pump air conditioning unit has low working efficiency and poor heating capacity when the environmental temperature is low, and can not meet the heating requirement of severe cold areas in winter. Especially when the environmental temperature is lower than minus 50 ℃, the air-conditioning heating effect is poor, the heating requirement in the northeast, Xinjiang, inner Mongolia and other severe cold areas of China is higher at present, but the pure electric heating hot water heating has higher energy consumption and poor economical and practical properties, and the coal or gas hot water heating wastes resources and pollutes the environment.
Disclosure of Invention
The technical problem to be solved by the invention is as follows: in order to solve the problems that the heating is difficult, the heating attenuation is serious, the heating capacity is poor and even an air conditioning unit cannot be started to normally operate when the ambient temperature is lower than minus 50 ℃, the invention provides a low-ambient-temperature heating air conditioning system which comprises four refrigeration cycles, wherein the refrigeration cycle system can effectively improve the heating capacity at the low ambient temperature and obviously improve the high-temperature hot air at the low ambient temperature, particularly, the load-side air conditioner can still produce the hot air when the ambient temperature is lower than minus 50 ℃, the heating effect is obvious, the energy is saved, the material is low, and the problems in the prior art are effectively solved.
The technical scheme adopted by the invention for solving the technical problems is as follows:
a low-ambient-temperature heating air-conditioning system comprises four refrigeration cycles,
the first refrigeration cycle is a cycle of driving a refrigerant medium R23 by a low-temperature enhanced vapor injection compressor, namely a cycle of the refrigerant medium R23 among the low-temperature enhanced vapor injection compressor, an evaporative condenser, a first economizer, a second throttling expansion valve, a low-temperature evaporator and the low-temperature enhanced vapor injection compressor;
the second refrigeration cycle is a cycle of driving refrigerant medium R23 by the low-temperature enhanced vapor injection compressor, namely, the refrigerant medium R23 circulates between the low-temperature enhanced vapor injection compressor, the evaporative condenser, the first economizer, the first throttling expansion valve, the first economizer and the low-temperature enhanced vapor injection compressor;
the third refrigeration cycle is that the high-temperature enhanced vapor injection compressor drives the refrigerant medium R32 to circulate, namely the refrigerant medium R32 circulates among the high-temperature enhanced vapor injection compressor, the high-temperature condenser, the second economizer, the fourth throttle expansion valve, the evaporative condenser and the high-temperature enhanced vapor injection compressor;
the fourth refrigeration cycle high-temperature enhanced vapor injection compressor drives the refrigerant R32 to circulate, namely the refrigerant R32 circulates between the high-temperature enhanced vapor injection compressor, the high-temperature condenser, the second economizer, the third throttling expansion valve, the second economizer and the high-temperature enhanced vapor injection compressor.
Specifically, high-temperature and high-pressure R23 refrigerant gas compressed by the low-temperature enhanced vapor injection compressor is discharged through an outlet o, the refrigerant gas enters the evaporative condenser inlet c after passing through the plurality of connecting copper pipes to release heat in the evaporative condenser, the refrigerant liquid after releasing heat enters the first economizer inlet 1 through an outlet d to be subcooled, the refrigerant liquid after being subcooled flows out of the first economizer outlet 1 and is throttled and depressurized through the first throttle expansion valve, then enters the first economizer through an inlet 2 to be subjected to heat exchange and evaporation, the refrigerant gas after being vaporized flows out of the outlet 2 and enters the low-temperature enhanced vapor injection compressor air supplement port b after passing through the plurality of connecting copper pipes to be compressed by the compressor, namely, the enhanced vapor injection process is performed, and the refrigerant liquid after being subcooled flows out of the first economizer outlet 1 and is throttled and is evaporated through an inlet g after being depressurized through the second throttle expansion valve, refrigerant gas after the evaporator flows out through the outlet h, then passes through the connecting copper pipes and is sucked and compressed by the low-temperature enhanced vapor injection compressor through the inlet a, and a low-temperature stage refrigeration cycle is completed.
Specifically, high-temperature high-pressure R32 refrigerant gas after the compression of the high-temperature enhanced vapor injection compressor is discharged through an outlet n, the refrigerant gas enters through a plurality of connecting copper pipes and enters into a high-temperature condenser inlet p to be condensed and released heat in the high-temperature condenser, the refrigerant liquid after the heat release enters into a second economizer through an outlet q to be recooled, the recooled refrigerant liquid enters into the second economizer through an inlet 4 after being throttled and depressurized through a third throttle expansion valve and enters into the second economizer to be heat-exchanged and evaporated through an inlet 4, the evaporated refrigerant gas flows out through an outlet 4 and enters into a high-temperature enhanced vapor injection compressor air supplement port s to be compressed by the compressor after being throttled and depressurized through a fourth throttle expansion valve and then enters into the evaporation condenser through an inlet e to be evaporated, and the recooled refrigerant liquid flows out of an outlet 3 of the second economizer and enters into the evaporation condenser through an outlet e after being throttled and depressurized through a fourth throttle expansion valve, the evaporated refrigerant gas flows out through the outlet f, then passes through the connecting copper pipes and is sucked and compressed by the high-temperature enhanced vapor injection compressor through the inlet m, and a high-temperature stage refrigeration cycle is completed.
Specifically, the economizer adopts a stainless steel brazed plate heat exchanger.
Specifically, the low-ambient-temperature heating air-conditioning system is a cascade refrigeration cycle system with two different enhanced vapor injection refrigerant compressors.
The beneficial effects of the invention are: the invention provides a low-environment-temperature heating air-conditioning system, which comprises four refrigeration cycles, wherein the refrigeration cycle system can effectively improve the heating capacity at low environment temperature, has obvious improvement effect on high-temperature hot air at low environment temperature, and particularly can still produce hot air when the environment temperature is below 50 ℃ below zero, so the heating effect is obvious, and the energy is saved and the practicability is realized.
Drawings
The invention is further illustrated with reference to the following figures and examples.
Fig. 1 is a schematic structural view of the present invention.
In the figure, 1 low-temperature enhanced vapor injection compressor, 2 a plurality of connecting copper pipes, 3 evaporative condenser, 4 first throttle expansion valve, 5 first economizer, 6 second throttle expansion valve, 7 low-temperature evaporator, 8 low-temperature fan, 9 high-temperature enhanced vapor injection compressor, 10 high-temperature condenser, 11 high-temperature fan, 12 second economizer, 13 third throttle expansion valve, 14 fourth throttle expansion valve.
Detailed Description
The present invention will now be described in further detail with reference to the accompanying drawings. The figures are simplified schematic diagrams illustrating the basic structure of the invention only in a schematic way, and thus are only shown in connection with the invention.
A low-ambient-temperature heating air-conditioning system comprises four refrigeration cycles,
the first refrigeration cycle is a cycle of driving a refrigerant medium R23 by a low-temperature enhanced vapor injection compressor, namely a cycle of the refrigerant medium R23 among the low-temperature enhanced vapor injection compressor, an evaporative condenser, a first economizer, a second throttling expansion valve, a low-temperature evaporator and the low-temperature enhanced vapor injection compressor;
the second refrigeration cycle is a cycle of driving refrigerant medium R23 by the low-temperature enhanced vapor injection compressor, namely, the refrigerant medium R23 circulates between the low-temperature enhanced vapor injection compressor, the evaporative condenser, the first economizer, the first throttling expansion valve, the first economizer and the low-temperature enhanced vapor injection compressor;
the third refrigeration cycle is that the high-temperature enhanced vapor injection compressor drives the refrigerant medium R32 to circulate, namely the refrigerant medium R32 circulates among the high-temperature enhanced vapor injection compressor, the high-temperature condenser, the second economizer, the fourth throttle expansion valve, the evaporative condenser and the high-temperature enhanced vapor injection compressor;
the fourth refrigeration cycle high-temperature enhanced vapor injection compressor drives the refrigerant R32 to circulate, namely the refrigerant R32 circulates between the high-temperature enhanced vapor injection compressor, the high-temperature condenser, the second economizer, the third throttling expansion valve, the second economizer and the high-temperature enhanced vapor injection compressor.
Specifically, the high-temperature and high-pressure R23 refrigerant gas compressed by the low-temperature enhanced vapor injection compressor is discharged through an outlet o, the refrigerant gas enters an inlet c of the evaporation condenser through the plurality of connecting copper pipes to release heat in the evaporation condenser, the refrigerant liquid after releasing heat enters an inlet 1 of the first economizer through an outlet d to be subcooled, the refrigerant liquid after being subcooled flows out of the outlet 1 of the first economizer to be throttled and depressurized through the first throttling expansion valve, then enters the first economizer through an inlet 2 to be subjected to heat exchange and evaporation, the refrigerant gas after being vaporized flows out of the outlet 2 to enter a gas supplementing port b of the low-temperature enhanced vapor injection compressor through the plurality of connecting copper pipes to be compressed by the compressor, namely, the enhanced vapor injection process, and the refrigerant liquid after being subcooled flows out of the outlet 1 of the first economizer to be throttled and depressurized through the second throttling expansion valve to enter the low-temperature evaporator through an inlet g to be evaporated, refrigerant gas after the evaporator flows out through the outlet h, then passes through the connecting copper pipes and is sucked and compressed by the low-temperature enhanced vapor injection compressor through the inlet a, and a low-temperature stage refrigeration cycle is completed.
Specifically, high-temperature high-pressure R32 refrigerant gas after the compression of the high-temperature enhanced vapor injection compressor is discharged through an outlet n, the refrigerant gas enters through a plurality of connecting copper pipes and enters into a high-temperature condenser inlet p to be condensed and released heat in the high-temperature condenser, the refrigerant liquid after the heat release enters into a second economizer through an outlet q to be recooled, the recooled refrigerant liquid enters into the second economizer through an inlet 4 after being throttled and depressurized through a third throttle expansion valve and enters into the second economizer to be heat-exchanged and evaporated through an inlet 4, the evaporated refrigerant gas flows out through an outlet 4 and enters into a high-temperature enhanced vapor injection compressor air supplement port s to be compressed by the compressor after being throttled and depressurized through a fourth throttle expansion valve and then enters into the evaporation condenser through an inlet e to be evaporated, and the recooled refrigerant liquid flows out of an outlet 3 of the second economizer and enters into the evaporation condenser through an outlet e after being throttled and depressurized through a fourth throttle expansion valve, the evaporated refrigerant gas flows out through the outlet f, then passes through the connecting copper pipes and is sucked and compressed by the high-temperature enhanced vapor injection compressor through the inlet m, and a high-temperature stage refrigeration cycle is completed.
The low-temperature enhanced vapor injection compressor is provided with an inlet a, an air supplementing port b and an outlet o, the evaporative condenser is provided with an inlet c, an outlet d, an inlet e and an outlet f, (wherein c-d is a flow channel, e-f is a flow channel), the first economizer is provided with an inlet 1, an outlet 1 and an inlet 2, and the low-temperature evaporator is provided with an inlet g and an outlet h, the high-temperature enhanced vapor injection compressor is provided with an outlet n, an inlet m and a gas supplementing port s, the high-temperature condenser is provided with an inlet p and an outlet q, the economizer is provided with an inlet 3, an outlet 3, an inlet 4 and an outlet 4, the inlet 3-the outlet 3 is a 12 economizer 3 channel, and the inlet 4-the outlet 4 is a 12 economizer 4 channel, and all connecting copper pipes and refrigeration fittings are connected by brazing.
Generally, the refrigerant medium of the low-temperature enhanced vapor injection compressor 1 is R23, the R23 refrigerant medium can still absorb heat and evaporate at the ambient temperature of-50 ℃, and the low-temperature enhanced vapor injection compressor has low working pressure, and is safe, stable and reliable. A refrigerant medium flows in the connecting copper pipes 2. The evaporative condenser 3 is a brazed plate heat exchanger which is formed by pressing stainless steel and has double channels, and two refrigerant media of R23 and R32 with different cold and hot temperatures exchange heat in the refrigerant media. The evaporative condenser 3 is used as a condenser of a low-temperature-level refrigeration cycle and also as an evaporator of a high-temperature-level refrigerant cycle, so that a carrier for transferring energy from a low-temperature heat source to a high-temperature heat source is realized. The brazed plate heat exchangers in the first economizer 5 and the second economizer 12 are press-formed from stainless steel, double pass. The first throttle expansion valve 4, the second throttle expansion valve 6, the third throttle expansion valve 13, and the fourth throttle expansion valve 14 perform a throttling and pressure reducing function during a refrigeration cycle. The low-temperature evaporator 7 is formed by expanding and processing a copper pipe (an aluminum foil fin). The low-temperature fan 8 and the low-temperature evaporator 7 conduct forced convection heat exchange to promote the refrigerant medium in the low-temperature evaporator to conduct heat exchange with low-temperature air, and the low-temperature evaporator is enabled to absorb heat in the low-temperature air. The refrigerant medium of the high-temperature stage compressor 9 is R32, the condenser temperature of the R32 refrigerant medium is above 65 ℃, the refrigerant medium can exchange heat with the load side (room air) to increase the air temperature, and R32 is an environment-friendly refrigerant medium. The high-temperature condenser 10 is formed by expanding and processing a copper pipe (an aluminum foil fin). The high-temperature fan 11, the low-temperature fan 8 and the high-temperature condenser 10 perform forced convection heat exchange to promote the refrigerant medium in the high-temperature condenser to exchange heat with the load side (room air), so that the room air absorbs heat in the high-temperature condenser, and finally hot air is heated and discharged.
Specifically, high-temperature high-pressure R23 refrigerant gas after low-temperature enhanced vapor injection compressor 1 compression is discharged through export o, refrigerant gas enters into evaporative condenser 3 entry c after a plurality of connecting copper pipes 2 and releases heat in evaporative condenser 3, refrigerant liquid after releasing heat enters into first economic device 5 entry 1 after export d and carries out the subcooling (subcooling), refrigerant liquid after the subcooling (subcooling) flows out from first economic device 5 export 1 and after the first throttle expansion valve 4 throttle decompression, enter into first economic device 5 through entry 2 and exchange heat evaporation, refrigerant gas after the evaporation enters into low-temperature enhanced vapor injection compressor 1 tonifying qi mouth b after a plurality of connecting copper pipes 2 through export 2 and is compressed by the compressor, namely the enhanced vapor injection process. The recooled refrigerant liquid flows out from the outlet 1 of the first economizer 5, is throttled and decompressed by the second throttle expansion valve 6, enters the low-temperature evaporator 7 through the inlet g for evaporation, flows out through the outlet h, passes through the plurality of connecting copper pipes 2, is sucked and compressed by the low-temperature air-injection enthalpy-increasing compressor 1 through the inlet a, and completes a low-temperature stage refrigeration cycle.
Specifically, high-temperature high-pressure R32 refrigerant gas compressed by the high-temperature enhanced vapor injection compressor 9 is discharged through an outlet n, the refrigerant gas enters an inlet p of the high-temperature condenser 10 through a plurality of connecting copper pipes 2 and is condensed and released heat in the high-temperature condenser 10, the refrigerant liquid after the heat release enters the second economizer 12 through an outlet q to be recooled (supercooled), the recooled (supercooled) refrigerant liquid is throttled and depressurized through a third throttle expansion valve 13 and enters the second economizer 12 through an inlet 4 to be subjected to heat exchange and evaporation, the evaporated refrigerant gas flows out through an outlet 4 and enters an air supplement port s of the high-temperature enhanced vapor injection compressor 9 through a plurality of connecting copper pipes 2 and is compressed by the compressor, namely, the enhanced vapor injection process. The recooled refrigerant liquid flows out of the outlet 3 of the second economizer 12, is throttled and decompressed by the fourth throttle expansion valve 14, enters the evaporative condenser 3 through the inlet e, is evaporated, flows out of the outlet f, passes through the plurality of connecting copper pipes 2, is sucked and compressed by the high-temperature enhanced vapor injection compressor 9 through the inlet m, and completes a high-temperature stage refrigeration cycle.
In one embodiment, the economizer employs a stainless steel brazed plate heat exchanger.
In another embodiment, the low ambient temperature heating air conditioning system is a cascade refrigeration cycle system with two different enhanced vapor injection refrigerant compressors.
According to the refrigeration principle and the refrigerant characteristics, the enhanced vapor injection cascade compression refrigeration cycle system can effectively improve the heating capacity at low ambient temperature, particularly improve the air outlet temperature of heating air-conditioning equipment in an ultralow temperature environment below 50 ℃ below zero, and has obvious improvement effect on the heating at low ambient temperature.
In light of the foregoing description of the preferred embodiment of the present invention, many modifications and variations will be apparent to those skilled in the art without departing from the spirit and scope of the invention. The technical scope of the present invention is not limited to the content of the specification, and must be determined according to the scope of the claims.
Claims (5)
1. A low ambient temperature heating air conditioning system is characterized by comprising four refrigeration cycles,
the first refrigeration cycle is a cycle of driving a refrigerant medium R23 by a low-temperature enhanced vapor injection compressor, namely a cycle of the refrigerant medium R23 among the low-temperature enhanced vapor injection compressor, an evaporative condenser, a first economizer, a second throttling expansion valve, a low-temperature evaporator and the low-temperature enhanced vapor injection compressor;
the second refrigeration cycle is a cycle of driving refrigerant medium R23 by the low-temperature enhanced vapor injection compressor, namely, the refrigerant medium R23 circulates between the low-temperature enhanced vapor injection compressor, the evaporative condenser, the first economizer, the first throttling expansion valve, the first economizer and the low-temperature enhanced vapor injection compressor;
the third refrigeration cycle is that the high-temperature enhanced vapor injection compressor drives the refrigerant medium R32 to circulate, namely the refrigerant medium R32 circulates among the high-temperature enhanced vapor injection compressor, the high-temperature condenser, the second economizer, the fourth throttle expansion valve, the evaporative condenser and the high-temperature enhanced vapor injection compressor;
the fourth refrigeration cycle high-temperature enhanced vapor injection compressor drives the refrigerant R32 to circulate, namely the refrigerant R32 circulates between the high-temperature enhanced vapor injection compressor, the high-temperature condenser, the second economizer, the third throttling expansion valve, the second economizer and the high-temperature enhanced vapor injection compressor.
2. The low ambient temperature heating air conditioning system of claim 1,
high-temperature high-pressure R23 refrigerant gas after the low temperature enhanced vapor injection compressor compression is discharged through export o, refrigerant gas gets into behind a plurality of connection copper pipes evaporative condenser entry c is exothermic in the evaporative condenser, refrigerant liquid after the heat release gets into behind export d first economizer entry 1 carries out the subcooling, refrigerant liquid after the subcooling flows out from first economizer export 1 after the first throttle expansion valve throttle step-down, gets into through entry 2 heat transfer evaporation in the first economizer, refrigerant gas after the evaporation flows out through export 2 and gets into behind a plurality of connection copper pipes low temperature enhanced vapor injection compressor air supplement port b is compressed by the compressor, and the enhanced vapor injection process, and refrigerant liquid after the subcooling flows out from first economizer export 1 and gets into after the second throttle expansion valve throttle step-down in the low temperature evaporator through entry g and evaporates, refrigerant gas after the evaporator flows out through the outlet h, then passes through the connecting copper pipes and is sucked and compressed by the low-temperature enhanced vapor injection compressor through the inlet a, and a low-temperature stage refrigeration cycle is completed.
3. The low-ambient-temperature heating air-conditioning system according to claim 2, wherein the high-temperature and high-pressure R32 refrigerant gas compressed by the high-temperature enhanced vapor injection compressor is discharged through an outlet n, the refrigerant gas enters the high-temperature condenser inlet p through the connecting copper pipes to condense and release heat in the high-temperature condenser, the refrigerant liquid after releasing heat enters the second economizer through an outlet q to be re-cooled, the re-cooled refrigerant liquid is throttled and depressurized by the third throttle expansion valve and then enters the second economizer through an inlet 4 to exchange heat and evaporate, the evaporated refrigerant gas flows out through an outlet 4, passes through the connecting copper pipes, enters the high-temperature enhanced vapor injection compressor air-supplementing inlet s to be compressed by the compressor, namely, the enhanced vapor injection process, and the re-cooled refrigerant liquid flows out from an outlet 3 of the second economizer, is throttled and depressurized by the fourth throttle expansion valve, enters the evaporation condenser through an inlet e to evaporate, the evaporated refrigerant gas flows out through the outlet f, then passes through the connecting copper pipes and is sucked and compressed by the high-temperature enhanced vapor injection compressor through the inlet m, and a high-temperature stage refrigeration cycle is completed.
4. The low ambient temperature heating air conditioning system of claim 3, wherein the economizer employs a stainless steel brazed plate heat exchanger.
5. The low-ambient-temperature heating air-conditioning system as claimed in claim 4, wherein the low-ambient-temperature heating air-conditioning system is a cascade refrigeration cycle system with two different types of enhanced vapor injection refrigerant compressors.
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| CN202210378298.4A CN114674090A (en) | 2022-04-12 | 2022-04-12 | Low-ambient-temperature heating air-conditioning system |
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Citations (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1357338A1 (en) * | 2002-04-03 | 2003-10-29 | Jean-Paul Arpin | Low temperature freezing system, in particular for freezing, deep freezing and storing of food products |
| CN105509358A (en) * | 2015-12-21 | 2016-04-20 | 重庆美的通用制冷设备有限公司 | Refrigeration unit |
| CN206905292U (en) * | 2017-06-06 | 2018-01-19 | 广州泉能智能科技股份有限公司 | A kind of cold ambient air temperature source two level carries hot type heat pump high-temperature hot-air unit |
| CN108759143A (en) * | 2018-07-02 | 2018-11-06 | 江苏奥斯康新能源有限公司 | A kind of special cascade superhigh temperature hot water air source heat pump system |
| CN208254010U (en) * | 2018-04-19 | 2018-12-18 | 董建 | A kind of full working scope air-source superposition type high-temperature-hot-water heat pump unit |
| CN208871896U (en) * | 2018-08-28 | 2019-05-17 | 福建雪人股份有限公司 | A kind of dual system salt water unit |
| CN210425663U (en) * | 2019-07-12 | 2020-04-28 | 克莱门特捷联制冷设备(上海)有限公司 | Cold and hot water air conditioning system with enhanced vapor injection |
| CN111076421A (en) * | 2019-12-31 | 2020-04-28 | 江苏奥斯康新能源有限公司 | Direct current frequency conversion overlapping hot water unit |
| CN210569369U (en) * | 2019-10-18 | 2020-05-19 | 大连冰山空调设备有限公司 | Low-temperature frequency conversion overlapping high-temperature air source heat pump unit |
| CN212538345U (en) * | 2020-06-23 | 2021-02-12 | 武汉斯诺制冷设备有限公司 | Double-temperature-zone overlapping refrigerating unit |
| CN217685885U (en) * | 2022-04-12 | 2022-10-28 | 新科环保科技有限公司 | Low ambient temperature air source heat pump air heater system |
| CN116123744A (en) * | 2023-03-24 | 2023-05-16 | 哈尔滨工业大学 | Ultralow-temperature single-stage and double-stage hybrid air source heat pump unit |
-
2022
- 2022-04-12 CN CN202210378298.4A patent/CN114674090A/en active Pending
Patent Citations (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP1357338A1 (en) * | 2002-04-03 | 2003-10-29 | Jean-Paul Arpin | Low temperature freezing system, in particular for freezing, deep freezing and storing of food products |
| CN105509358A (en) * | 2015-12-21 | 2016-04-20 | 重庆美的通用制冷设备有限公司 | Refrigeration unit |
| CN206905292U (en) * | 2017-06-06 | 2018-01-19 | 广州泉能智能科技股份有限公司 | A kind of cold ambient air temperature source two level carries hot type heat pump high-temperature hot-air unit |
| CN208254010U (en) * | 2018-04-19 | 2018-12-18 | 董建 | A kind of full working scope air-source superposition type high-temperature-hot-water heat pump unit |
| CN108759143A (en) * | 2018-07-02 | 2018-11-06 | 江苏奥斯康新能源有限公司 | A kind of special cascade superhigh temperature hot water air source heat pump system |
| CN208871896U (en) * | 2018-08-28 | 2019-05-17 | 福建雪人股份有限公司 | A kind of dual system salt water unit |
| CN210425663U (en) * | 2019-07-12 | 2020-04-28 | 克莱门特捷联制冷设备(上海)有限公司 | Cold and hot water air conditioning system with enhanced vapor injection |
| CN210569369U (en) * | 2019-10-18 | 2020-05-19 | 大连冰山空调设备有限公司 | Low-temperature frequency conversion overlapping high-temperature air source heat pump unit |
| CN111076421A (en) * | 2019-12-31 | 2020-04-28 | 江苏奥斯康新能源有限公司 | Direct current frequency conversion overlapping hot water unit |
| CN212538345U (en) * | 2020-06-23 | 2021-02-12 | 武汉斯诺制冷设备有限公司 | Double-temperature-zone overlapping refrigerating unit |
| CN217685885U (en) * | 2022-04-12 | 2022-10-28 | 新科环保科技有限公司 | Low ambient temperature air source heat pump air heater system |
| CN116123744A (en) * | 2023-03-24 | 2023-05-16 | 哈尔滨工业大学 | Ultralow-temperature single-stage and double-stage hybrid air source heat pump unit |
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