CN113154557B - Quasi-two-stage compression four-pipe air conditioning system - Google Patents
Quasi-two-stage compression four-pipe air conditioning system Download PDFInfo
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- CN113154557B CN113154557B CN202110293660.3A CN202110293660A CN113154557B CN 113154557 B CN113154557 B CN 113154557B CN 202110293660 A CN202110293660 A CN 202110293660A CN 113154557 B CN113154557 B CN 113154557B
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- 238000004378 air conditioning Methods 0.000 title claims abstract description 17
- 230000006835 compression Effects 0.000 title claims abstract description 17
- 238000007906 compression Methods 0.000 title claims abstract description 17
- 239000007788 liquid Substances 0.000 claims abstract description 43
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims abstract description 29
- 238000001816 cooling Methods 0.000 claims abstract description 21
- 238000006073 displacement reaction Methods 0.000 claims description 3
- 239000000725 suspension Substances 0.000 claims description 2
- 230000008676 import Effects 0.000 claims 1
- 238000011084 recovery Methods 0.000 description 8
- 238000010438 heat treatment Methods 0.000 description 6
- 239000003507 refrigerant Substances 0.000 description 6
- 238000005516 engineering process Methods 0.000 description 4
- 238000000034 method Methods 0.000 description 4
- 229920006395 saturated elastomer Polymers 0.000 description 4
- 238000000926 separation method Methods 0.000 description 3
- 238000013461 design Methods 0.000 description 2
- 238000011161 development Methods 0.000 description 2
- 238000005265 energy consumption Methods 0.000 description 2
- 238000005057 refrigeration Methods 0.000 description 2
- 238000011160 research Methods 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000005339 levitation Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 239000011555 saturated liquid Substances 0.000 description 1
- 239000013526 supercooled liquid Substances 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F5/00—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater
- F24F5/0007—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater cooling apparatus specially adapted for use in air-conditioning
- F24F5/001—Compression cycle type
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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
- 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
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Power Engineering (AREA)
- Life Sciences & Earth Sciences (AREA)
- Sustainable Development (AREA)
- Combustion & Propulsion (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
Abstract
The invention discloses a quasi-two-stage compression four-pipe air conditioning system which comprises a compressor, a four-way reversing valve, a condenser, a liquid storage device, a first valve, a water cooling device, a gas-liquid separator, a second valve, a third valve, an evaporator, a fourth valve, a fin heat exchanger and a fifth valve, wherein an exhaust port of the compressor is connected with a port D of the four-way reversing valve, a port C of the four-way reversing valve is connected with an inlet of the condenser, an outlet of the condenser is connected with an inlet of the liquid storage device, and an outlet of the liquid storage device is connected with an inlet of the first valve.
Description
Technical Field
The invention relates to the technical field of energy-saving air conditioning equipment, in particular to the technical field of a quasi-two-stage compression four-pipe air conditioning system.
Background
In recent years, with the development of economy, people have higher and higher requirements on the quality of indoor life, and the research on meeting sustainable development technology is particularly urgent. The heat pump technology is an efficient energy-saving mode, but the traditional air source heat pump has poor heating performance and low-temperature reliability in a low-temperature environment, so that more researches are carried out on quasi-two-stage compression cycle of a compressor. As a technical scheme which is feasible in technology and easy to realize, the method has obvious effects on insufficient heating (refrigerating) quantity and reduced compressor efficiency when the compressor with the improved fixed volume ratio deviates from the design working condition.
The double-pipe air conditioner can not simultaneously meet the operation of a room with heat supply and a refrigerating room system in a building in a transition season, and the cold and heat balance condition is easy to occur in a three-pipe system. The four-pipe air conditioning system has the advantages of strong load adaptability, flexible adjustment, capability of meeting the simultaneous use of rooms with different requirements on temperature and humidity, and capability of freely selecting a heat supply or cold supply operation mode at any time. All energy consumption in the system can be provided according to the end requirement. The air conditioner is particularly suitable for rooms such as operating rooms in hospitals, which have high sanitary requirements, strict standards for temperature, humidity and air quality, and requirements for cold and heat in the whole process.
Disclosure of Invention
The invention aims to solve the problems in the prior art, and provides a quasi-two-stage compression four-pipe air conditioning system, so that an energy-saving system can meet the requirement that rooms with different requirements on temperature and humidity are used simultaneously, the rooms are independently refrigerated or refrigerated all the year round, cold and hot water is provided simultaneously, the problem that the heating (refrigerating) quantity of a compressor is insufficient when the compressor deviates from the design working condition is solved, the efficiency of the compressor is improved, the adaptability to load is strong, the adjustment is flexible, the energy loss can be effectively reduced, and the popularization and the application are facilitated.
In order to achieve the purpose, the invention provides a quasi-two-stage compression four-tube air conditioning system which comprises a compressor, a four-way reversing valve, a condenser, a liquid storage device, a first valve, a water cooling device, a gas-liquid separator, a second valve, a third valve, an evaporator, a fourth valve, a fin heat exchanger and a fifth valve, wherein an exhaust port of the compressor is connected with a port D of the four-way reversing valve, a port C of the four-way reversing valve is connected with an inlet of the condenser, an outlet of the condenser is connected with an inlet of the liquid storage device, an outlet of the liquid storage device is connected with an inlet of the first valve, an outlet of the first valve is connected with inlets of the second valve and the water cooling device respectively, an outlet of the water cooling device is connected with an auxiliary air inlet of the compressor, an outlet of the second valve is connected with inlets of the third valve and the fourth valve respectively, an outlet of the third valve is connected with an inlet of the evaporator, an outlet of the evaporator is connected with an inlet of the gas-liquid separator, an outlet of the gas-liquid separator is connected with an outlet of the compressor, an outlet of the fourth valve is connected with inlets of the fin and the heat exchanger, an outlet of the heat exchanger is connected with an inlet of the four-liquid separator, and a port of the four-liquid separator.
Preferably, a heat recovery device is arranged on a pipeline between the gas-liquid separator and the compressor.
Preferably, the heat recovery device is a positive displacement heat recovery device.
Preferably, the condenser, the evaporator and the water cooling device are all plate heat exchangers.
Preferably, the first valve and the second valve are both thermal expansion valves and are always opened, and the third valve, the fourth valve and the fifth valve are both check valves.
Preferably, the compressor is a magnetic levitation compressor with an auxiliary air inlet.
Preferably, the heat exchanger is a fin heat exchanger.
The invention has the beneficial effects that: the invention solves the requirement of simultaneously using rooms with different requirements on temperature and humidity by combining the quasi-two-stage compression refrigeration and the four-pipe system technology, can independently refrigerate and heat, also improves the efficiency of the compressor, solves the problem of insufficient heating cold quantity, and simultaneously reduces the energy consumption as much as possible by using the heat recovery device, thereby saving energy to the maximum extent.
The features and advantages of the present invention will be described in detail by embodiments in conjunction with the accompanying drawings.
Drawings
Fig. 1 is a schematic structural diagram of a quasi-two-stage compression four-pipe air conditioning system according to the present invention.
In the figure: the system comprises a compressor 1, a four-way reversing valve 2, a condenser 3, a liquid storage device 4, a first valve 5, a water cooling device 6, a gas-liquid separator 7, a heat recovery device 8, a second valve 9, a third valve 10, an evaporator 11, a fourth valve 12, a fin heat exchanger 13 and a fifth valve 14.
Detailed Description
Referring to fig. 1, the quasi-two-stage compression four-tube air conditioning system of the present invention includes a compressor 1, a four-way reversing valve 2, a condenser 3, a liquid reservoir 4, a first valve 5, a water cooling device 6, a gas-liquid separator 7, a second valve 9, a third valve 10, an evaporator 11, a fourth valve 12, a fin heat exchanger 13 and a fifth valve 14, an exhaust port of the compressor 1 is connected to a port D of the four-way reversing valve 2, a port C of the four-way reversing valve 2 is connected to an inlet of the condenser 3, an outlet of the condenser 3 is connected to an inlet of the liquid reservoir 4, an outlet of the liquid reservoir 4 is connected to an inlet of the first valve 5, an outlet of the first valve 5 is connected to inlets of the second valve 9 and the water cooling device 6, an outlet of the water cooling device 6 is connected to an auxiliary air inlet of the compressor 1, an outlet of the second valve 9 is connected to inlets of the third valve 10 and a fourth valve 12, an outlet of the third valve 10 is connected to an inlet of the evaporator 11, an outlet of the evaporator 11 is connected to an inlet of the gas-liquid separator 7, an outlet of the compressor 1 is connected to an outlet of the heat exchanger 7, an outlet of the heat exchanger 4, an evaporator 14, an outlet of the heat exchanger 7 is connected to an inlet of the fin heat exchanger 7, an inlet of the heat exchanger 4, an evaporator 7, an inlet of the heat exchanger 7 is connected to a fin heat exchanger 4, an evaporator 7, an inlet of the heat exchanger 7, an evaporator is connected to a fin heat exchanger 4, and the third valve 10, the fourth valve 12 and the fifth valve 14 are all check valves, the compressor 1 is a magnetic suspension compressor 1 with an auxiliary air inlet, and the heat exchanger 13 is a fin heat exchanger.
The working process of the invention is as follows:
in the working process of the quasi-two-stage compression four-pipe air conditioning system, when the system is in a heating and refrigerating working condition, the four-way reversing valve 2 is opened, the third valve 10 is opened, and the fourth valve 12 and the fifth valve 14 are closed. The refrigerant sequentially passes through the compressor 1, the port D of the four-way reversing valve 2, the port C of the four-way reversing valve 2, the condenser 3, the liquid storage device 4 and the first valve 5 and then is divided into two paths, wherein one path passes through the water cooling device 6, and the other path passes through the second valve 9. One path of the water passes through the water cooling device 6 and reaches the compressor 1 to form a loop, and one path of the water enters the second valve 9, passes through the third valve 10 and the evaporator 11, enters the gas-liquid separator 7, passes through the positive displacement heat recovery device 8 and reaches the compressor 1 to form a loop. When the air conditioner works, low-pressure superheated gas enters the compressor 1 to be compressed, heated and boosted, high-pressure superheated steam generates high-pressure saturated or supercooled liquid through the condenser 3, a refrigerant enters the liquid storage device 4, enters the expansion valve, is throttled to a certain pressure in the middle, then enters the water cooling device 6 in two ways for heat exchange, is evaporated and then is sucked by the auxiliary air inlet of the compressor 1, and the water cooling device 6 simultaneously generates cold water for supply. The other path of the gas enters a second valve 9, further low-pressure liquid is generated and enters an evaporator 11, low-pressure saturated or superheated steam is generated and enters a gas-liquid separator 7 to realize gas-liquid separation, and the gas enters a heat recovery device 8 to recover heat and then enters the compressor 1.
And under the independent heating working condition, the four-way reversing valve 2 is opened, the fourth valve 12 is opened, and the third valve 10 and the fifth valve 14 are closed. The refrigerant sequentially passes through the compressor 1, the port D of the four-way reversing valve 2, the port C of the four-way reversing valve 2, the condenser 3, the liquid storage device 4 and the first valve 5 and then is divided into two paths, one path passes through the water cooling device 6, and the other path passes through the second valve 9. One path of the water reaches the compressor 1 through the water cooling device 6 to form a loop, and the other path of the water enters the second valve 9, passes through the fourth valve 12, the fin heat exchanger 13, the port E of the four-way reversing valve 2 and the port S of the four-way reversing valve 2, enters the gas-liquid separator 7, passes through the heat recoverer 8, and reaches the compressor 1 to form a loop. During operation, a refrigerant enters the liquid storage device 4, enters the expansion valve, is throttled to a certain pressure in the middle, enters one path of the second valve 9, further generates low-pressure liquid, enters the finned heat exchanger 13 through the fourth valve 12, generates low-pressure saturated or superheated steam, and enters the gas-liquid separator 7 to realize gas-liquid separation.
And under the independent refrigeration working condition, the four-way reversing valve 2 is opened, the third valve 10 and the fifth valve 14 are opened, and the fourth valve 12 is closed. The refrigerant is divided into two paths after sequentially passing through the compressor 1, the four-way reversing valve 2 port D, the four-way reversing valve 2 port E, the finned heat exchanger 13, the fifth valve 14, the liquid reservoir 4 and the first valve 5, wherein one path passes through the water cooling device 6, and the other path passes through the second valve 9. One path of the water passes through the water cooling device 6 and reaches the compressor 1 to form a loop, and one path of the water enters the second valve 9, passes through the third valve 10 and the evaporator 11, enters the gas-liquid separator 7, passes through the heat recovery device 8 and reaches the compressor 1 to form a loop. During operation, a refrigerant enters the liquid storage device 4, enters the expansion valve, is throttled to a certain pressure in the middle, enters one path of the second valve 9, further generates low-pressure liquid, enters the evaporator 11 through the third valve 10, generates low-pressure saturated or superheated steam, and enters the gas-liquid separator 7 to realize gas-liquid separation.
The above embodiments are illustrative of the present invention, and are not intended to limit the present invention, and any simple modifications of the present invention are within the scope of the present invention.
Claims (6)
1. The utility model provides a four pipe system air conditioning system of accurate second grade compression which characterized in that: including compressor (1), four-way reversing valve (2), condenser (3), reservoir (4), first valve (5), water cooling plant (6), vapour and liquid separator (7), second valve (9), third valve (10), evaporimeter (11), fourth valve (12), fin heat exchanger (13) and fifth valve (14), the gas vent and four-way reversing valve (2) port D of compressor (1) link to each other, the entry of condenser (3) is connected to four-way reversing valve (2) port C, the entry of exit linkage reservoir (4) of condenser (3), the import of the exit linkage first valve (5) of reservoir (4), the export of first valve (5) respectively with the entry linkage of second valve (9) and water cooling plant (6), the auxiliary air inlet of exit linkage compressor (1) of water cooling plant (6), the exit linkage third valve (10) and the entry of fourth valve (12) of air inlet of second valve (9) respectively, the exit linkage of third valve (10) exit linkage vapour and liquid separator (7), the export of evaporimeter (7) connect the entry of compressor (11), the compressor (7) export of compressor (11), the outlet of the fourth valve (12) is connected with the inlets of a fin heat exchanger (13) and a fifth valve (14) respectively, the outlet of the fifth valve (14) is connected with the inlet of a liquid storage device (4), the outlet of the fin heat exchanger (13) is connected with a port E of a four-way reversing valve (2), a port S of the four-way reversing valve (2) is connected with the inlet of a gas-liquid separator (7), the first valve (5) and the second valve (9) are thermal expansion valves and are opened all the time, and the third valve (10), the fourth valve (12) and the fifth valve (14) are check valves.
2. A quasi-two-stage compression four-pipe air conditioning system as claimed in claim 1, wherein: and a heat recoverer (8) is arranged on a pipeline between the gas-liquid separator (7) and the compressor (1).
3. A quasi-two-stage compression four-pipe air conditioning system as claimed in claim 2, wherein: the heat recoverer (8) is a positive displacement heat recoverer.
4. A quasi-two-stage compression four-pipe air conditioning system as claimed in claim 1, wherein: the condenser (3), the evaporator (11) and the water cooling device (6) are all plate heat exchangers.
5. A quasi-two-stage compression four-pipe air conditioning system as claimed in claim 1, wherein: the compressor (1) is a magnetic suspension compressor (1) with an auxiliary air inlet.
6. A quasi-two-stage compression four-pipe air conditioning system as claimed in any one of claims 1 to 5, wherein: the heat exchanger (13) is a fin heat exchanger.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110293660.3A CN113154557B (en) | 2021-03-19 | 2021-03-19 | Quasi-two-stage compression four-pipe air conditioning system |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110293660.3A CN113154557B (en) | 2021-03-19 | 2021-03-19 | Quasi-two-stage compression four-pipe air conditioning system |
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| CN113154557A CN113154557A (en) | 2021-07-23 |
| CN113154557B true CN113154557B (en) | 2022-12-20 |
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| CN114353358B (en) * | 2021-12-16 | 2024-07-23 | 臣功(北京)科技有限公司 | Temperature and humidity independent control constant temperature and humidity unit based on solution dehumidification |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE10029662A1 (en) * | 2000-06-23 | 2002-01-03 | Uwe Zeiler | System of refrigeration machines, heat exchangers for air conditioning has bivalent mode with plate heat exchangers, refrigeration machines producing refrigeration power simultaneously |
| CN101294754A (en) * | 2008-05-26 | 2008-10-29 | 刘雄 | Multifunctional air conditioner heat pump |
| CN102937347A (en) * | 2012-12-10 | 2013-02-20 | 广州柯兰特热能科技有限公司 | Enhanced vapor injection type triple co-generation machine |
| CN111288679A (en) * | 2020-03-09 | 2020-06-16 | 中国轻工业武汉设计工程有限责任公司 | Single-stage and double-stage switching evaporation supercooling ejector refrigeration heat pump circulation system |
| CN211119734U (en) * | 2019-12-05 | 2020-07-28 | 孚莱美科(江苏)环境科技有限公司 | Four-pipe system central air-conditioning system |
-
2021
- 2021-03-19 CN CN202110293660.3A patent/CN113154557B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE10029662A1 (en) * | 2000-06-23 | 2002-01-03 | Uwe Zeiler | System of refrigeration machines, heat exchangers for air conditioning has bivalent mode with plate heat exchangers, refrigeration machines producing refrigeration power simultaneously |
| CN101294754A (en) * | 2008-05-26 | 2008-10-29 | 刘雄 | Multifunctional air conditioner heat pump |
| CN102937347A (en) * | 2012-12-10 | 2013-02-20 | 广州柯兰特热能科技有限公司 | Enhanced vapor injection type triple co-generation machine |
| CN211119734U (en) * | 2019-12-05 | 2020-07-28 | 孚莱美科(江苏)环境科技有限公司 | Four-pipe system central air-conditioning system |
| CN111288679A (en) * | 2020-03-09 | 2020-06-16 | 中国轻工业武汉设计工程有限责任公司 | Single-stage and double-stage switching evaporation supercooling ejector refrigeration heat pump circulation system |
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Effective date of registration: 20240704 Address after: 230000 Woye Garden Commercial Building B-1017, 81 Ganquan Road, Shushan District, Hefei City, Anhui Province Patentee after: HEFEI JINGLONG ENVIRONMENTAL PROTECTION TECHNOLOGY Co.,Ltd. Country or region after: China Address before: 310018 No. 2 street, Baiyang street, Hangzhou economic and Technological Development Zone, Zhejiang 928 Patentee before: ZHEJIANG SCI-TECH University Country or region before: China |