CN111964188B - Thermosiphon-vapor compression composite refrigeration system - Google Patents
Thermosiphon-vapor compression composite refrigeration system Download PDFInfo
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- CN111964188B CN111964188B CN202010863997.9A CN202010863997A CN111964188B CN 111964188 B CN111964188 B CN 111964188B CN 202010863997 A CN202010863997 A CN 202010863997A CN 111964188 B CN111964188 B CN 111964188B
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D15/00—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies
- F28D15/02—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes
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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
- F24F5/0003—Exclusively-fluid systems
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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
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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
- F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
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- General Engineering & Computer Science (AREA)
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- Sustainable Development (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Analytical Chemistry (AREA)
- Power Engineering (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
Abstract
The invention discloses a thermosiphon-vapor compression composite refrigeration system, which can improve the refrigeration effect of the composite refrigeration system and effectively improve the operation stability of the system. The thermosiphon-vapor compression composite refrigeration system comprises an evaporator, a condenser, an air separator, a compressor, a throttling element, a first three-way electromagnetic valve and a second three-way electromagnetic valve. In the embodiment, when the thermosiphon mode is operated, the two-phase refrigerant output by the evaporator is subjected to gas-liquid separation in the gas separator, and the gaseous refrigerant enters the condenser, so that the refrigeration effect is improved; the gravity pressure drop generated by the gaseous refrigerant in the ascending pipe is reduced, so that the driving force required by the system starting is reduced, and the running stability of the system is improved. When the steam compression mode is operated, superheated steam input by the compressor and liquid output by the condenser exchange heat in the air separator, so that saturated steam enters the condenser, the flow of a refrigerant of the condenser is relatively increased, and the refrigeration effect is improved.
Description
Technical Field
The invention relates to the technical field of refrigeration air conditioners and heat pipes, in particular to a thermosiphon-vapor compression composite refrigeration system.
Background
Traditional base station refrigeration mostly relies on single vapor compression formula refrigeration air conditioner, and it can't directly utilize the nature cold source to cool off the air in the base station when outdoor air temperature is lower to lead to this refrigeration mode electric energy consumption very big. The natural cooling technology mainly includes direct or indirect air natural cooling, direct or indirect evaporative cooling, and natural cooling using a heat pipe. The thermosiphon as one of the heat pipes has the advantages of no moving parts, compact arrangement, difficult leakage, selection of a proper evaporation and condensation heat exchanger type according to an application background and the like, and is widely applied to cooling of electronic equipment. Researchers have proposed combining thermosiphons with vapor compression refrigeration systems to form composite refrigeration systems. Compared with a single vapor compression type refrigeration air conditioner, the composite refrigeration system can effectively reduce the electric energy utilization efficiency of the base station.
However, the existing thermosiphon/vapor compression composite refrigeration system has certain defects which limit the wide application. First, the flow characteristics, heat transfer characteristics, and optimal charge rate of the refrigerant in the thermosiphon mode and the vapor compression refrigeration mode are different, resulting in a composite refrigeration system structure and charge rate optimized for one mode that degrades system performance in the other mode. Secondly, when the thermosiphon mode is operated under variable working conditions, the development of the composite refrigeration system is still limited by system oscillation caused by insufficient driving force. Thirdly, the vapor compression refrigeration mode of the fixed-frequency compressor cannot realize good refrigeration capacity matching according to the base station variable load working condition, so that the compressor is frequently started and stopped when the base station load changes, and the energy consumption of the composite refrigeration system is increased.
Disclosure of Invention
The technical problem to be solved by the invention is as follows: the thermosiphon-vapor compression composite refrigeration system can improve the refrigeration effect of the composite refrigeration system and effectively improve the operation stability of the system.
In order to solve the above technical problems, an embodiment of the present invention provides a thermosiphon-vapor compression composite refrigeration system, which includes an evaporator, a condenser, a gas separator, a compressor, a throttling element, a first three-way electromagnetic valve and a second three-way electromagnetic valve, the outlet of the evaporator is connected with the inlet of the first three-way electromagnetic valve, the first outlet of the first three-way electromagnetic valve is connected with the inlet of the compressor, the second outlet of the first three-way electromagnetic valve and the outlet of the compressor are connected with the first inlet of the air separator through the first ascending pipe, the first outlet of the air separator is connected with the inlet of the condenser through the second ascending pipe, the outlet of the condenser is connected with the second inlet of the air separator, the second outlet of the air separator is connected with the inlet of the second three-way electromagnetic valve through the descending pipe, the first outlet of the second three-way electromagnetic valve is connected with the inlet of the throttling element, and the outlet of the throttling element and the second outlet of the second three-way electromagnetic valve are connected with the inlet of the evaporator.
As a further improvement of the embodiment of the present invention, in use, the two outlets of the first three-way solenoid valve and the two outlets of the second three-way solenoid valve are respectively adjusted to open and close, so as to realize the switching between the thermosiphon mode and the vapor compression mode.
As a further improvement of the embodiment of the present invention, when the mode is switched to the thermosiphon mode, the first outlet of the first three-way electromagnetic valve is closed, and the second outlet of the first three-way electromagnetic valve is opened; and closing the first outlet of the second three-way electromagnetic valve and opening the second outlet of the second three-way electromagnetic valve.
As a further improvement of the embodiment of the present invention, when the compression mode is switched to the vapor compression mode, the first outlet of the first three-way electromagnetic valve is opened, and the second outlet of the first three-way electromagnetic valve is closed; and opening a first outlet of the second three-way electromagnetic valve, and closing a second outlet of the second three-way electromagnetic valve.
As a further improvement of the embodiment of the present invention, the compressor is an inverter compressor.
As a further improvement of the embodiment of the present invention, the throttling element is an electronic expansion valve.
As a further improvement of the embodiment of the invention, the evaporator and the condenser are both fin-tube heat exchangers.
Compared with the prior art, the technical scheme of the invention has the following beneficial effects: the embodiment of the invention provides a thermosiphon-vapor compression composite refrigeration system, which can improve the refrigeration effect of the composite refrigeration system and effectively improve the operation stability of the system. In this embodiment, a gas separator is provided in the hybrid refrigeration system to store the refrigerant and achieve gas-liquid separation. When the thermosiphon mode is operated, the two-phase refrigerant output by the evaporator is subjected to gas-liquid separation in the gas separator, and the gaseous refrigerant enters the condenser, so that the heat exchange efficiency of the condenser is improved, and the refrigerating performance of the composite refrigerating system is improved; after gas-liquid separation, the gaseous refrigerant enters the condenser through the second ascending pipe, and compared with a two-phase refrigerant, the gravity pressure drop generated by the gaseous refrigerant in the second ascending pipe is greatly reduced, so that the driving force required by starting the system is reduced, and the running stability of the system is improved. When the vapor compression mode is operated, superheated vapor input by the compressor and liquid output by the condenser exchange heat in the air separator, so that saturated vapor enters the condenser, meanwhile, the flow of a refrigerant of the condenser is relatively increased, the heat exchange efficiency of the condenser is improved, and the refrigeration performance of the composite refrigeration system is improved. The liquid storage function of the air separator can realize that the refrigerant circulation flow in the refrigerating system can be adjusted and supplemented to the variable working condition respectively under two running modes, and the running performance of the system is effectively improved.
Drawings
FIG. 1 is a schematic structural view of a thermosiphon-vapor compression composite refrigeration system according to an embodiment of the present invention;
fig. 2 is a schematic structural view of the gas separator of fig. 1.
The figure shows that: the system comprises an evaporator 101, a first three-way electromagnetic valve 102, a first ascending pipe 103, a gas separator 104, a second ascending pipe 105, a condenser 106, a descending pipe 107, a second three-way electromagnetic valve 108, a throttling element 109 and a compressor 110.
Detailed Description
The technical solution of the present invention will be described in detail below with reference to the accompanying drawings.
An embodiment of the present invention provides a thermosiphon-vapor compression composite refrigeration system, as shown in fig. 1, including an evaporator 101, a condenser 106, a gas separator 104, a compressor 110, a throttling element 109, a first three-way solenoid valve 102, and a second three-way solenoid valve 108. An outlet of the evaporator 101 is connected with an inlet of a first three-way solenoid valve 102, a first outlet of the first three-way solenoid valve 102 is connected with an inlet of a compressor 110, and an outlet of the compressor 110 and a second outlet of the first three-way solenoid valve 102 are both connected with a first inlet of an air separator 104 through a first riser 103. As shown in fig. 2, a first outlet of the air separator 104 is connected to an inlet of the condenser 106 through the second rising pipe 105, and an outlet of the condenser 106 is connected to a second inlet of the air separator 104. The second outlet of the gas separator 104 is connected to the inlet of a second three-way solenoid valve 108 via a down pipe 107, the first outlet of the second three-way solenoid valve 108 is connected to the inlet of a throttling element 109, and both the outlet of the throttling element 109 and the second outlet of the second three-way solenoid valve 108 are connected to the inlet of the evaporator 101.
In the above embodiment, the air separator 104 is provided in the composite refrigeration system to store the refrigerant and achieve the gas-liquid separation. When the thermosiphon mode is operated, the two-phase refrigerant output by the evaporator 101 is subjected to gas-liquid separation in the gas separator 104, the gaseous refrigerant enters the condenser 106 and releases heat from a gaseous state to a liquid state, and the pure gaseous refrigerant has higher heat exchange efficiency compared with the two-phase refrigerant, so that the heat exchange efficiency of the condenser 106 is improved, and the refrigeration performance of the composite refrigeration system is improved; after gas-liquid separation, the gaseous refrigerant enters the condenser 106 through the second ascending pipe 105, and compared with a two-phase refrigerant, the gravity pressure drop generated by the gaseous refrigerant is greatly reduced, so that the driving force required by starting the system is reduced, and the running stability of the system is improved. When the vapor compression mode is operated, superheated vapor output by the compressor 110 and liquid refrigerant output by the condenser 106 exchange heat in the air separator 104, so that saturated vapor enters the condenser 106, the saturated vapor releases heat from a gaseous state to a liquid state, and the saturated vapor refrigerant has higher heat exchange efficiency compared with the superheated refrigerant; the two streams of fluid entering the air separator 104 are superheated vapor and saturated liquid respectively, the two streams of fluid flowing out of the air separator 104 are saturated vapor and saturated liquid respectively, in order to achieve heat balance in the air separator 104, part of liquid refrigerant input into the air separator 104 by the condenser 106 absorbs heat in the superheated vapor, and the refrigerant flow entering the condenser 106 and 106 after being changed into saturated gaseous refrigerant is relatively increased, so that the heat exchange efficiency of the condenser is improved, and the refrigerating performance of the composite refrigerating system is improved. The air separator 104 is used for storing the refrigerant, and is communicated with the evaporator 101, the compressor 110 and the condenser 106, so that the refrigerant circulating flow in the refrigeration system can be adjusted and supplemented respectively according to the variable working conditions in two operation modes, and the operation performance of the system is effectively improved.
In the thermosiphon-vapor compression composite refrigeration system of the present embodiment, the opening and closing of the two outlets of the first three-way solenoid valve 102 and the opening and closing of the two outlets of the second three-way solenoid valve 108 are respectively adjusted to realize the switching between the thermosiphon mode and the vapor compression mode of the composite refrigeration system. Specifically, the first outlet of the first three-way solenoid valve 102 is closed, and the second outlet of the first three-way solenoid valve 102 is opened, so that the outlet of the evaporator 101 is directly communicated with the first riser 103. The first outlet of the second three-way solenoid valve 108 is closed and the second outlet of the second three-way solenoid valve 108 is opened, so that the downcomer 107 is in direct communication with the inlet of the evaporator, switching to the thermosiphon mode. The first outlet of the first three-way solenoid valve 102 is opened and the second outlet of the first three-way solenoid valve 102 is closed, so that the outlet of the evaporator 101 communicates with the inlet of the compressor 110. The first outlet of the second three-way solenoid valve 108 is opened and the second outlet of the second three-way solenoid valve 108 is closed, so that the downcomer 107 is connected to the throttling element 109, and the throttling element 109 communicates with the inlet of the evaporator, switching to the vapor compression mode.
In the above embodiment, the evaporator 101, the first riser 103, the air separator 104, the second riser 105, the condenser 106, and the downcomer 107 can be reused in both the thermosiphon mode and the vapor compression mode, and the two modes can be switched by only adjusting the opening and closing of the two outlets of the first three-way electromagnetic valve and the second three-way electromagnetic valve, so that the whole system has a simple structure and is convenient to switch.
In the thermosiphon mode, the two-phase refrigerant output from the evaporator 101 passes through the second outlet of the first three-way solenoid valve 102 and then enters the air separator 104 through the first rising pipe 103, as shown in fig. 2, the two-phase refrigerant is subjected to gas-liquid separation in the air separator 104, the gas refrigerant enters the condenser 106 through the second rising pipe 105, the gas refrigerant is changed into liquid refrigerant after heat exchange in the condenser 106 and then enters the air separator 104, and the liquid refrigerant enters the evaporator 101 from the second outlet of the air separator 104 through the second outlet of the downcomer 107 and the second outlet of the second three-way solenoid valve 108 in sequence.
During the vapor compression mode, the superheated vapor output by the evaporator 101 enters the compressor 110 through the first outlet of the first three-way solenoid valve 102, and enters the air separator 104 through the first rising pipe 103 after being boosted, as shown in fig. 2, the superheated vapor exchanges heat with the liquid vapor in the air separator 104, so that the saturated vapor enters the condenser 106 through the second rising pipe 105, the refrigerant which becomes liquid after exchanging heat in the condenser 106 enters the air separator 104 again, the liquid refrigerant enters the throttling element 109 from the second outlet of the air separator 104 through the descending pipe 107 and the first outlet of the second three-way solenoid valve 108 in sequence, and the liquid refrigerant after being throttled and depressurized enters the evaporator 101.
As a preferable example, the compressor 110 is an inverter compressor. By adopting the variable-frequency compressor, good refrigerating capacity matching can be realized aiming at the variable-load working condition of the base station, the compressor is prevented from being started and stopped frequently when the load of the base station changes, and the energy consumption of a load refrigerating system is reduced.
Preferably, the throttling element 109 is an electronic expansion valve. Compared with the traditional throttling device, the electronic expansion valve is suitable for occasions with severe load change or wider working condition range, and is particularly suitable for the compressor 110 which is a variable-frequency compressor.
As a preferable example, the evaporator 101 and the condenser 106 are both fin-tube heat exchangers, and the refrigerant flows through the evaporator 101 and the condenser 106 to exchange heat with indoor and outdoor air, thereby achieving a refrigeration effect.
The foregoing illustrates and describes the principles, general features, and advantages of the present invention. It will be understood by those skilled in the art that the present invention is not limited to the embodiments described above, which are intended to further illustrate the principles of the invention, and that various changes and modifications may be made without departing from the spirit and scope of the invention, which is also intended to be covered by the appended claims. The scope of the invention is defined by the claims and their equivalents.
Claims (7)
1. A thermosiphon-vapor compression composite refrigeration system is characterized by comprising an evaporator (101), a condenser (106), an air separator (104), a compressor (110), a throttling element (109), a first three-way electromagnetic valve (102) and a second three-way electromagnetic valve (108), wherein an outlet of the evaporator (101) is connected with an inlet of the first three-way electromagnetic valve (102), a first outlet of the first three-way electromagnetic valve (102) is connected with an inlet of the compressor (110), a second outlet of the first three-way electromagnetic valve (102) and an outlet of the compressor (110) are connected with a first inlet of the air separator (104) through a first ascending pipe (103), a first outlet of the air separator (104) is connected with an inlet of the condenser (106) through a second ascending pipe (105), an outlet of the condenser (106) is connected with a second inlet of the air separator (104), and a second outlet of the air separator (104) is connected with an inlet of the second three-way electromagnetic valve (108) through a descending pipe (107), a first outlet of the second three-way electromagnetic valve (108) is connected with an inlet of the throttling element (109), and an outlet of the throttling element (109) and a second outlet of the second three-way electromagnetic valve (108) are both connected with an inlet of the evaporator (101);
when the thermosiphon mode is operated, the two-phase refrigerant output by the evaporator (101) is subjected to gas-liquid separation in the gas separator (104), the gaseous refrigerant enters the condenser (106) through the second ascending pipe (105), and the gaseous refrigerant releases heat from the gaseous state to be in a liquid state; compared with a two-phase refrigerant, the pure gaseous refrigerant has higher heat exchange efficiency, so that the heat exchange efficiency of the condenser (106) is improved, and the refrigeration performance of the composite refrigeration system is improved; the gravity pressure drop generated by the gaseous refrigerant in the second ascending pipe (105) is greatly reduced, so that the driving force required by the system starting is reduced, and the running stability of the system is improved;
when the vapor compression mode is operated, superheated vapor output by the compressor (110) exchanges heat with liquid refrigerant output by the condenser (106) in the gas separator (104), so that saturated vapor enters the condenser (106), and the saturated vapor refrigerant has higher heat exchange efficiency compared with the superheated refrigerant; the part of liquid refrigerant input into the gas separator (104) by the condenser (106) absorbs the heat in the superheated steam, and enters the condenser (106) after becoming saturated gaseous refrigerant, and the refrigerant flow of the condenser (106) is relatively increased, so that the heat exchange efficiency of the condenser is improved, and the refrigeration performance of the composite refrigeration system is improved.
2. A thermosiphon-vapor compression composite refrigeration system according to claim 1, characterized in that, in use, the switching between thermosiphon mode and vapor compression mode is achieved by adjusting the opening and closing of the two outlets of the first three-way solenoid valve (102) and the two outlets of the second three-way solenoid valve (108), respectively.
3. A thermosiphon-vapor compression composite refrigeration system according to claim 2, characterized in that when switched to thermosiphon mode, the first outlet of the first three-way solenoid valve (102) is closed and the second outlet of the first three-way solenoid valve (102) is opened; the first outlet of the second three-way solenoid valve (108) is closed, and the second outlet of the second three-way solenoid valve (108) is opened.
4. A thermosiphon-vapor compression composite refrigeration system according to claim 2, characterized in that when switching to the vapor compression mode, the first outlet opening the first three-way solenoid valve (102) is opened and the second outlet of the first three-way solenoid valve (102) is closed; and opening a first outlet of the second three-way electromagnetic valve (108), and closing a second outlet of the second three-way electromagnetic valve (108).
5. Thermosiphon-vapor compression composite refrigeration system according to claim 1, characterized in that the compressor (110) is a variable frequency compressor.
6. A thermosiphon-vapor compression composite refrigeration system according to claim 1, characterized in that the throttling element (109) is an electronic expansion valve.
7. A thermosiphon-vapor compression composite refrigeration system according to claim 1, characterized in that both the evaporator (101) and the condenser (106) are finned tube heat exchangers.
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| CN105180693A (en) * | 2015-09-30 | 2015-12-23 | 华南理工大学 | Heat pipe and circulation method for working liquid in heat pipe |
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2020
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| JPH09273876A (en) * | 1996-04-08 | 1997-10-21 | Mitsubishi Denki Bill Techno Service Kk | Cooler with natural circulation loop |
| JP2004349551A (en) * | 2003-05-23 | 2004-12-09 | Denso Corp | Boiling cooling system |
| JP2005055079A (en) * | 2003-08-05 | 2005-03-03 | Hachiyo Engneering Kk | Thermosiphon cycle system |
| CN2821493Y (en) * | 2005-08-17 | 2006-09-27 | 江苏科技大学 | Overheat steam saturator in refrigerating system |
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