CN111059802A - Condensing equipment and air conditioning system who has it - Google Patents
Condensing equipment and air conditioning system who has it Download PDFInfo
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- CN111059802A CN111059802A CN201911296504.1A CN201911296504A CN111059802A CN 111059802 A CN111059802 A CN 111059802A CN 201911296504 A CN201911296504 A CN 201911296504A CN 111059802 A CN111059802 A CN 111059802A
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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
- F25B39/00—Evaporators; Condensers
- F25B39/04—Condensers
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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
- F25B31/00—Compressor arrangements
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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
- F28D5/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, using the cooling effect of natural or forced evaporation
- F28D5/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, using the cooling effect of natural or forced evaporation in which the evaporating medium flows in a continuous film or trickles freely over the conduits
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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
- F25B2339/00—Details of evaporators; Details of condensers
- F25B2339/04—Details of condensers
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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
- F25B2339/00—Details of evaporators; Details of condensers
- F25B2339/04—Details of condensers
- F25B2339/041—Details of condensers of evaporative condensers
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
The invention provides a condensing device and an air conditioning system with the same, wherein the condensing device comprises a first heat exchanger and a second heat exchanger, the first heat exchanger is provided with a first inlet allowing a refrigerant to enter and a first outlet allowing the refrigerant to flow out after temperature reduction and heat exchange, and the second heat exchanger is provided with a second inlet allowing the refrigerant to enter and a second outlet allowing the refrigerant to flow out after temperature reduction and heat exchange; the supercooling section of the second heat exchanger is provided with a third inlet, a third inlet and a first outlet which can be communicated with the first outlet, and the third inlet and the first outlet are communicated through an intermediate pipe, so that fluid flows to the second heat exchanger from the first outlet, the intermediate pipe and the third inlet in sequence, and the pipe diameter of the first heat exchange pipe of the first heat exchanger is larger than that of the second heat exchange pipe of the second heat exchanger. The invention increases the flow velocity of the refrigerant in the supercooling section heat exchange tube, quickly takes away the liquid film refrigerant on the wall surface, effectively strengthens the condensation heat exchange effect, improves the heat exchange amount and also reduces the filling amount of the refrigerant in the condenser.
Description
Technical Field
The invention belongs to the technical field of air conditioners, and particularly relates to a condensing device and an air conditioning system with the condensing device.
Background
The condenser is one of the important components of the refrigeration system, and the quality of the heat exchange performance of the condenser has a crucial influence on the performance of the system. Generally, a condenser can be divided into a gas phase region, a two phase region, and a supercooling region according to a refrigerant state. In the gas phase area, the gas phase refrigerant in a high-temperature and high-pressure state is gradually cooled by low-temperature air forced to convect in a heat exchange tube of the condenser; in the two-phase area, the state of the refrigerant is a gas-liquid two-phase state, the refrigerant is gradually condensed into a liquid-phase refrigerant along with the two-phase state of the refrigerant, the thickness of the condensate on the inner wall surface of the heat exchange tube is gradually increased, the contact of steam and the wall surface is blocked, the main thermal resistance of condensation heat exchange is located, and the thickness phase change heat exchange effect of the condensate is also gradually reduced; when the gas-phase refrigerant is completely changed into the liquid-phase refrigerant and flows into the supercooling region, the heat exchange condition is changed from the condensation phase-change heat exchange into the single-phase convection heat exchange, and the single-phase convection heat exchange capacity is lower than the condensation phase-change heat exchange capacity under the same heat exchange condition. The heat exchange effect of the refrigerant in the supercooling section of the condenser is reduced, and the density of the liquid-phase refrigerant is higher than that of the gas phase, so that the filling amount of the refrigerant in the tail section of the condenser is large, and the heat exchange effect is poor. Therefore, the condenser without enhanced heat exchange is used in the double-condensation temperature system or the single-condensation temperature system, so that the system is low in energy efficiency, and the refrigerant charging amount in the system is large.
The invention researches and designs a condensing device and an air conditioning system with the condensing device, which are provided by the invention, because the heat exchange effect of a refrigerant in a supercooling section of a condenser is reduced and the density of a liquid-phase refrigerant is higher than that of a gas phase in the prior art, so that the refrigerant in the tail section of the condenser is more in filling amount and poor in heat exchange effect, the system energy efficiency of a double-condensation-temperature system or a single-condensation-temperature system is low, the filling amount of the refrigerant in the system is large, and the like.
Disclosure of Invention
Therefore, the technical problem to be solved by the invention is to overcome the defect that the supercooling section of the condenser in the prior art has poor heat exchange effect due to the increase of the thermal resistance of the inner wall of the heat exchange tube, so that the condensing device and the air conditioning system with the condensing device are provided.
The present invention provides a condensing unit, comprising:
the heat exchanger comprises a first heat exchanger and a second heat exchanger, wherein the first heat exchanger is provided with a first inlet allowing a refrigerant to enter and a first outlet allowing the refrigerant to flow out after temperature reduction and heat exchange, and the second heat exchanger is provided with a second inlet allowing the refrigerant to enter and a second outlet allowing the refrigerant to flow out after temperature reduction and heat exchange;
the supercooling section of the second heat exchanger is provided with a third inlet which can be communicated with the first outlet, the third inlet and the first outlet are communicated through an intermediate pipe, so that fluid flows to the second heat exchanger from the first outlet, the intermediate pipe and the third inlet in sequence, and the pipe diameter of a first heat exchange pipe of the first heat exchanger is larger than that of a second heat exchange pipe of the second heat exchanger.
Preferably, the first and second electrodes are formed of a metal,
the supercooling section of the second heat exchanger is a partial pipe section of the second heat exchange pipe relatively close to the second outlet; and/or the middle pipe is also provided with a pressure regulating device.
Preferably, the first and second electrodes are formed of a metal,
the first heat exchanger is a fin type heat exchanger, the first heat exchange tube is a serpentine bent tube, and a plurality of heat exchange fins are arranged on the first heat exchange tube; and/or the second heat exchanger is a microchannel heat exchanger, the second heat exchange tube comprises heat exchange flat tubes and a collecting tube, the supercooling section comprises at least one heat exchange flat tube close to the second outlet, the middle tube is communicated to the collecting tube and communicated with the heat exchange flat tubes in the supercooling section, and the cross-sectional area of the first heat exchange tube is larger than that of the heat exchange flat tubes.
Preferably, the first and second electrodes are formed of a metal,
the first heat exchanger is a fin heat exchanger, the second heat exchanger is also a fin heat exchanger, and the cross-sectional area of the first heat exchange tube is larger than that of the second heat exchange tube; or the first heat exchanger is a micro-channel heat exchanger, the second heat exchanger is also a micro-channel heat exchanger, and the cross-sectional area of the heat exchange flat tube of the first heat exchanger is larger than that of the heat exchange flat tube of the second heat exchanger.
Preferably, the first and second electrodes are formed of a metal,
the heat exchanger further comprises an evaporative cooling device, and the evaporative cooling device can spray water or spray cooling on the first heat exchanger and/or the second heat exchanger.
Preferably, the first and second electrodes are formed of a metal,
the evaporative cooling apparatus includes a spray device positioned above the first heat exchanger to enable water to be sprayed onto the first heat exchanger.
Preferably, the first and second electrodes are formed of a metal,
the evaporative cooling device further comprises a water pump and a water receiving disc, the water pump is communicated with the spraying device through a first water pipe, the water receiving disc is communicated with the water pump through a second water pipe, and the water receiving disc is located at the lower end of the first heat exchanger and used for receiving water falling from the first heat exchanger.
Preferably, the first and second electrodes are formed of a metal,
the evaporative cooling device further comprises a spraying device, the spraying device is communicated with the water pump through a third water pipe, and the spraying device can spray the second heat exchanger.
Preferably, the first and second electrodes are formed of a metal,
the first heat exchanger and the second heat exchanger are arranged up and down, the first heat exchanger is located above the second heat exchanger, the water receiving tray is arranged below the first heat exchanger and above the second heat exchanger, and the spraying device is arranged above the second heat exchanger and below the water receiving tray.
The invention also provides an air conditioning system, which comprises a compression device, a throttling device, an evaporator and the condensing device.
Preferably, the first and second electrodes are formed of a metal,
the compression device comprises a low-pressure compressor and a high-pressure compressor, an exhaust port of the low-pressure compressor is communicated with the second inlet of the second heat exchanger, an exhaust port of the high-pressure compressor is communicated with the first inlet of the first heat exchanger, a second outlet of the second heat exchanger is communicated with one end of the evaporator after passing through the throttling device, and the other end of the evaporator is divided into two paths and is respectively communicated to an air suction port of the low-pressure compressor and an air suction port of the high-pressure compressor.
Preferably, the first and second electrodes are formed of a metal,
the compression device comprises a single compressor, an exhaust port of the single compressor is divided into two paths and is respectively communicated to the first inlet of the first heat exchanger and the second inlet of the second heat exchanger, a second outlet of the second heat exchanger is communicated with one end of the evaporator after passing through the throttling device, and the other end of the evaporator is communicated to an air suction port of the single compressor.
The condensing device and the air conditioning system with the condensing device have the following beneficial effects:
according to the invention, the two heat exchangers are arranged, the heat exchange pipes of the two heat exchangers have different pipe diameters, the outlet of the heat exchanger with the large pipe diameter of the heat exchange pipe is communicated to the supercooling section of the heat exchanger with the small pipe diameter of the heat exchange pipe, and the mixture is discharged together after being mixed by the supercooling section with the small pipe diameter of the heat exchange pipe, so that the pipe diameter of the heat exchange pipe is suddenly reduced, the flow velocity of the refrigerant in the supercooling section heat exchange pipe is effectively increased, the retention time in the pipe is reduced, the liquid film refrigerant on the wall surface is quickly taken away, and the thickness of thick condensate on the inner wall of the heat exchange pipe is reduced, therefore, the condensation heat exchange effect is effectively enhanced, the heat exchange amount is increased, the refrigerant can be more and more quickly discharged from the supercooling section heat exchange pipe, the.
Drawings
FIG. 1 is a schematic diagram of the construction of a condensing unit according to the present invention;
FIG. 2 is a schematic diagram of a first embodiment of the air conditioning system (dual condensing temperature system) of the present invention;
fig. 3 is a schematic structural diagram of a second embodiment (single condensing temperature system) of the air conditioning system of the present invention.
The reference numbers in the figures denote:
1. a first heat exchanger; 11. a first inlet; 12. a first outlet; 13. a first heat exchange tube; 14. heat exchange fins; 2. a second heat exchanger; 21. a second inlet; 22. a second outlet; 23. a third inlet; 24. a second heat exchange tube; 241. heat exchange flat tubes; 242. a header pipe; 3. an intermediate pipe; 4. a pressure regulating device; 5. a spraying device; 6. a water pump; 7. a water pan; 8. a spraying device; 91. a compression device; 911. a low pressure compressor; 912. a high pressure compressor; 913. a single compressor; 92. a throttling device; 93. an evaporator; 101. a first water pipe; 102. a second water pipe; 103. and a third water pipe.
Detailed Description
As shown in fig. 1, the present invention provides a condensing apparatus, comprising:
the heat exchanger comprises a first heat exchanger 1 and a second heat exchanger 2, wherein the first heat exchanger 1 is provided with a first inlet 11 allowing a refrigerant to enter and a first outlet 12 allowing the refrigerant to flow out after temperature reduction and heat exchange, and the second heat exchanger 2 is provided with a second inlet 21 allowing the refrigerant to enter and a second outlet 22 allowing the refrigerant to flow out after temperature reduction and heat exchange;
the supercooling section of the second heat exchanger 2 is provided with a third inlet 23 which can be communicated with the first outlet 12, the third inlet 23 and the first outlet 12 are communicated through an intermediate pipe 3, so that fluid flows to the second heat exchanger 2 from the first outlet 12, the intermediate pipe 3 and the third inlet 23 in sequence, and the pipe diameter of the first heat exchange pipe 13 of the first heat exchanger 1 is larger than that of the second heat exchange pipe 24 of the second heat exchanger 2.
According to the invention, the two heat exchangers are arranged, the heat exchange pipes of the two heat exchangers have different pipe diameters, the outlet of the heat exchanger with the large pipe diameter of the heat exchange pipe is communicated to the supercooling section of the heat exchanger with the small pipe diameter of the heat exchange pipe, and the mixture is discharged together after being mixed by the supercooling section with the small pipe diameter of the heat exchange pipe, so that the pipe diameter of the heat exchange pipe is suddenly reduced, the flow velocity of the refrigerant in the supercooling section heat exchange pipe is effectively increased, the retention time in the pipe is reduced, the liquid film refrigerant on the wall surface is quickly taken away, and the thickness of thick condensate on the inner wall of the heat exchange pipe is reduced, therefore, the condensation heat exchange effect is effectively enhanced, the heat exchange amount is increased, the refrigerant can be more and more quickly discharged from the supercooling section heat exchange pipe, the.
The invention 1, through changing the pipe diameter of each subarea of the heat exchanger, changes the flow velocity of the refrigerant in the liquid phase area and/or the gas phase area, thereby enhancing the heat exchange effect of the condenser.
2. The pipe diameter of the supercooling region is reduced to reduce the refrigerant charge amount in the condenser.
3. The evaporative cooling device is added, and the heat is absorbed by the evaporation of water drops on the surface of the heat exchanger, or the air inlet temperature is reduced by spraying, so that the heat exchange effect of the condenser is enhanced. The energy efficiency of a dual condensing temperature system or a single condensing temperature system is improved.
Preferably, the first and second electrodes are formed of a metal,
the supercooling section of the second heat exchanger 2 is a partial section of the second heat exchange tube 24 relatively close to the second outlet 22 (opposite to the second inlet 21); and/or the middle pipe 3 is also provided with a pressure regulating device 4. The preferred position of the supercooling section of the second heat exchanger is shown in fig. 1, and is located at the bottom of the second heat exchanger (because the second outlet of the second heat exchanger discharges the refrigerant at the bottom), because the refrigerant of the second heat exchanger flows in from the second inlet at the upper part and exchanges heat in the second heat exchanger, the refrigerant becomes most of liquid-phase refrigerant when reaching the bottom of the second heat exchanger, at this time, because the output pipeline of the first heat exchanger is connected, the flow rate of the refrigerant can be increased, the flow speed is increased, the refrigerant can be quickly discharged out of the second heat exchanger, the liquid film on the inner wall of the pipe is effectively reduced, and the heat exchange efficiency of the refrigerant in the supercooling section is effectively improved; the pressure of the refrigerant coming out of the first heat exchanger can be adjusted through the pressure adjusting device, so that the refrigerant can normally enter the supercooling degree of the second heat exchanger.
Preferably, the first and second electrodes are formed of a metal,
the first heat exchanger 1 is a fin-type heat exchanger, the first heat exchange tube 13 is a serpentine bent tube, and a plurality of heat exchange fins 14 are arranged on the first heat exchange tube 13; and/or, the second heat exchanger 2 is a microchannel heat exchanger, the second heat exchange tube 24 includes heat exchange flat tubes 241 and a header 242, the supercooling section includes at least one heat exchange flat tube 241 near the second outlet 22, the intermediate tube 3 is communicated to the header 242 and is communicated with the heat exchange flat tube 241 in the supercooling section, and the cross-sectional area of the first heat exchange tube 13 is larger than that of the heat exchange flat tube 241. The first heat exchanger is a fin heat exchanger, the second heat exchanger is a microchannel heat exchanger, the refrigerant exchanges heat from the fin heat exchanger with a large pipe diameter and flows into the microchannel (enters the flat pipe) of the microchannel heat exchanger with a small pipe diameter, the flow cross section area is reduced, the flow velocity is increased, the refrigerant discharging effect is enhanced, the thickness of a liquid film on the inner wall of the pipe is reduced, and the heat exchange effect is effectively improved.
Preferably, the first and second electrodes are formed of a metal,
the first heat exchanger 1 is a fin heat exchanger, the second heat exchanger 2 is also a fin heat exchanger, and the cross-sectional area of the first heat exchange tube 13 is larger than that of the second heat exchange tube 24; or, the first heat exchanger 1 is a micro-channel heat exchanger, the second heat exchanger 2 is also a micro-channel heat exchanger, and the cross-sectional area of the heat exchange flat tube of the first heat exchanger 1 is larger than that of the heat exchange flat tube of the second heat exchanger 2. The structure is the preferable structure of the second embodiment and the structure of the third embodiment, that is, the first heat exchanger and the second heat exchanger are both fin heat exchangers, and the first heat exchanger and the second heat exchanger are both micro-channel heat exchangers, that is, the effect of reducing the flow channel, increasing the flow speed and improving the heat exchange capacity can be realized by setting the pipe diameters of the two fin heat exchangers to be different; and the cross-sectional areas of the flat pipes of the two micro-channel heat exchangers are set to be different, so that the flow channels can be reduced, the flow speed can be increased, and the heat exchange capacity can be improved.
Preferably, the first and second electrodes are formed of a metal,
the device further comprises an evaporative cooling device, and the evaporative cooling device can spray water or spray cooling on the first heat exchanger 1 and/or the second heat exchanger 2. According to the invention, the evaporative cooling device is additionally arranged, and the heat exchange effect of the condenser is enhanced by evaporating and absorbing heat on the surface of the heat exchanger through water drops or reducing the temperature of inlet air through spraying. Through the water pump circulating system, the water which is not evaporated or utilized is collected and fully utilized, so that a better energy-saving effect is achieved. Especially in high temperature and low humidity environments.
Preferably, the first and second electrodes are formed of a metal,
the evaporative cooling device comprises a spraying device 5, wherein the spraying device 5 is positioned above the first heat exchanger 1 so as to spray water onto the first heat exchanger 1. Can play through spray set and strengthen cooling effect and effect of cooling down to first heat exchanger, strengthen the heat transfer effect of condenser.
Preferably, the first and second electrodes are formed of a metal,
the evaporative cooling device further comprises a water pump 6 and a water receiving disc 7, the water pump 6 is communicated with the spraying device 5 through a first water pipe 101, the water receiving disc 7 is communicated with the water pump 6 through a second water pipe 102, and the water receiving disc 7 is located at the lower end of the first heat exchanger 1 and used for receiving water falling from the first heat exchanger 1. According to the invention, water dripping from the condenser can be collected through the water receiving disc, and is circularly pumped to the upper part of the first heat exchanger through the water pump, so that the first heat exchanger is further cooled and cooled, and water which is not evaporated or utilized is collected and fully utilized through the arranged water pump circulating system, thereby generating a better energy-saving effect.
Preferably, the first and second electrodes are formed of a metal,
the evaporative cooling device further comprises a spraying device 8, the spraying device 8 is communicated with the water pump 6 through a third water pipe 103, and the spraying device 8 can spray on the second heat exchanger 2. The effect and the effect of enhancing cooling of the second heat exchanger can be achieved through the spraying device, and the heat exchange effect of the condenser is enhanced.
Preferably, the first and second electrodes are formed of a metal,
the first heat exchanger 1 and the second heat exchanger 2 are arranged up and down, the first heat exchanger 1 is located above the second heat exchanger 2, the water pan 7 is arranged below the first heat exchanger 1 and above the second heat exchanger 2, and the spraying device 8 is arranged above the second heat exchanger 2 and below the water pan 7. The first heat exchanger, the water pan, the spraying device and the second heat exchanger are arranged from top to bottom in sequence, water received by the water pan can be pumped to the spraying device or the spraying device through the water pump, so that the functions of sharing and multiple purposes are realized, and the functions of enhancing heat exchange and cooling of the two heat exchangers can be realized simultaneously.
The present invention also provides an air conditioning system comprising a compression device 91, a throttling device 92, an evaporator 93 and a condensing device as described in any one of the preceding items, as shown in fig. 2-3.
1. The invention uses two or more heat exchangers with different pipe diameters, and combines the two heat exchangers in a parallel flow path mode to ensure that gas-liquid two-phase refrigerants are converged together and enter the heat exchanger with smaller pipe diameter together, thereby changing the flow velocity of the refrigerants in the condenser pipe, strengthening the condensation heat exchange effect and reducing the refrigerant filling amount in the condenser. (because the gas-liquid two-phase refrigerant is gathered together and enters the heat exchanger with smaller pipe diameter together, the reduction of the flow cross section area leads to the increase of the flow velocity of the refrigerant, the condensation heat exchange effect is strengthened, and the filling amount of the refrigerant in the condenser is reduced.)
2. The invention uses two or more heat exchangers with different pipe diameters in a parallel flow path mode in a double-condensation temperature system or a single-condensation temperature system, thereby improving the system performance and reducing the refrigerant charging amount of the system. (improving the flow velocity of the refrigerant and enhancing the heat exchange effect)
As shown in fig. 2, preferably,
the compression device 91 comprises a low-pressure compressor 911 and a high-pressure compressor 912, a gas outlet of the low-pressure compressor 911 is communicated with the second inlet 21 of the second heat exchanger 2, a gas outlet of the high-pressure compressor 912 is communicated with the first inlet 11 of the first heat exchanger 1, a second outlet 22 of the second heat exchanger 2 passes through the throttling device 92 and then is communicated with one end of the evaporator 93, and the other end of the evaporator 93 is divided into two paths and is respectively communicated with a gas suction port of the low-pressure compressor 911 and a gas suction port of the high-pressure compressor 912.
The first embodiment (dual condensing temperature system) of the air conditioning system of the present invention is a preferred structure, that is, the high-pressure compressor delivers the compressed high-pressure refrigerant to the first heat exchanger, the low-pressure compressor delivers the compressed low-pressure refrigerant to the second heat exchanger, and since the pressure of the first heat exchanger is higher than that of the second heat exchanger, the pressure of the refrigerant is adjusted by the pressure adjusting device on the intermediate pipe and introduced into the supercooling section of the second heat exchanger, so as to complete the mixing of the two refrigerants with different pipe diameters, increase the flow rate, discharge the refrigerant as soon as possible, reduce the thickness of the liquid film, and improve the heat exchange capability.
As shown in fig. 3, preferably,
the compression device 91 comprises a single compressor 913, an exhaust port of the single compressor 913 is divided into two paths and is respectively communicated to the first inlet 11 of the first heat exchanger 1 and the second inlet 21 of the second heat exchanger 2, the second outlet 22 of the second heat exchanger 2 is communicated with one end of the evaporator 93 after passing through the throttling device 92, and the other end of the evaporator 93 is communicated to an air suction port of the single compressor 913.
The second embodiment of the air conditioning system (single condensing temperature system) of the present invention is an optimal structure form, that is, a single compressor divides the compressed refrigerant into two paths and respectively delivers the two paths to the first heat exchanger and the second heat exchanger, the pressure of the first heat exchanger is equal to the pressure of the second heat exchanger, the refrigerant at the outlet of the first heat exchanger is introduced into the supercooling section of the second heat exchanger, so as to complete the mixing of the two refrigerants with different pipe diameters, increase the flow rate, discharge the refrigerant as soon as possible, reduce the thickness of the liquid film, and improve the heat exchange capability.
FIG. 1 is a condenser of two heat exchangers with different pipe diameters combined in a parallel flow path mode, and the condenser consists of a micro-channel heat exchanger, a finned tube heat exchanger, a spraying device, a water pump and a water pan. Fig. 2 shows a dual condensing temperature system using the condenser, which comprises a condenser, a high-pressure compressor, a low-pressure compressor, an evaporator, a pressure regulating device and a throttling device of two heat exchangers with different pipe diameters combined in a parallel flow path mode. The micro-channel heat exchanger and the finned tube heat exchanger can be placed up and down as shown in figure 1, or can be placed left and right or front and back. The spraying device corresponds to the finned tube heat exchanger and is positioned right above the finned tube heat exchanger. The water pan corresponds to the finned tube heat exchanger and is positioned under the finned tube heat exchanger. The spraying device corresponds to the micro-channel heat exchanger, and can be positioned right above the micro-channel heat exchanger or in front of the windward side of the micro-channel heat exchanger.
The discharge gas phase refrigerant from the low pressure compressor flows into the microchannel heat exchanger. The gas-phase refrigerant is cooled into a gas-liquid two-phase state in the microchannel heat exchange flat tube by forced convection air with the temperature lower than that of the refrigerant after n processes, and the proportion of the liquid-phase refrigerant is gradually increased. The gas-phase refrigerant discharged from the high-pressure compressor flows into the finned tube heat exchanger. The forced convection air absorbs heat when flowing on the surface of the fins, so that the gas-phase refrigerant in the copper pipe is gradually condensed into the gas-liquid two-phase refrigerant. And after the pressure of the refrigerant at the outlet of the finned tube heat exchanger is reduced by the pressure regulating device, the refrigerant is converged with the refrigerant at the outlet of the nth flow path of the microchannel heat exchanger and enters the supercooling section of the microchannel heat exchanger together. The refrigerant subcooled in the microchannel heat exchanger then flows through the throttling device and enters the evaporator to absorb heat. Then part of the gas-phase refrigerant enters the low-pressure compressor, the other part of the gas-phase refrigerant enters the high-pressure compressor, and the refrigerant completes one cycle. Because the diameter of the micro-channel heat exchange flat tube is small, the flow of the refrigerant is increased, so that the flow velocity of the refrigerant in the tube is increased, the heat exchange effect is enhanced, and the small diameter of the micro-channel heat exchange flat tube enables the filling amount of the refrigerant to be reduced.
And evaporative cooling devices are arranged on the two heat exchangers so as to improve the refrigeration efficiency. The micro-channel heat exchanger is preferably provided with a spray device, the spray device is located in front of the windward side of the heat exchanger, the water pump sends part of water in the water pan into the spray device for atomization and spraying, fine water drops directly evaporate into water vapor in the air, the air is cooled, the temperature difference between the micro-channel heat exchanger and the air is improved, and the heat exchange effect is enhanced.
The spraying device is preferably arranged on the top of the finned tube heat exchanger, and sprayed water slides downwards along the surfaces of fins and heat exchange tubes of the heat exchanger under the action of gravity to form a water film. And the heat of the finned tube heat exchanger is absorbed in the water film evaporation process, so that the heat exchange effect of the finned tube heat exchanger is enhanced. By controlling the amount of the drenching water, the drenching water can be completely evaporated on the surface of the heat exchanger. If the evaporation is not completed, the spraying water flows to a water receiving tray below the heat exchanger. The water collected by the water receiving tray is sent into the spraying device and the spraying device through the water pump. The water used by the evaporative cooling device is preferably condensed water from an indoor evaporator, and can also be tap water or other water sources.
1. Furthermore, the micro-channel heat exchanger can be replaced by a small-diameter finned tube heat exchanger, and liquid-phase refrigerant in the supercooling section of the finned tube heat exchanger with a larger tube diameter and liquid-phase refrigerant in the supercooling section of the finned tube heat exchanger with a small tube diameter are converged and then jointly enter the supercooling section of the finned tube heat exchanger with the small tube diameter, so that the flow speed in the supercooling section of the finned tube heat exchanger with the small tube diameter is increased, and the heat exchange effect is enhanced.
2. And further. Fig. 3 shows a single condensing temperature system using the condenser, which includes a condenser, a compressor, an evaporator, a pressure regulator and a throttle device that are combined in a parallel flow path manner with a first heat exchanger 1 and a second heat exchanger 2. The compressor discharge is divided into two paths, wherein one path of gas-phase refrigerant flows into the second heat exchanger 2. The refrigerant finishes supercooling in the supercooling section at the bottom end of the second heat exchanger 2 and then flows out of the second heat exchanger 2, and the refrigerant with a certain supercooling degree enters the evaporator for evaporation phase change and heat absorption after throttling and pressure reduction through the throttling device.
The other path of the gas-phase refrigerant flows into the first heat exchanger 1. After the pressure of the refrigerant at the outlet of the first heat exchanger 1 is reduced by the pressure regulating device, the refrigerant is converged with the refrigerant at the outlet of the nth flow path of the second heat exchanger 2 and enters the supercooling section of the second heat exchanger 2 together. The refrigerant subcooled in the second heat exchanger 2 is then passed through a throttling device and enters the evaporator where it absorbs heat. The gas-phase refrigerant is absorbed again by the compressor, completing one refrigerant cycle. And evaporative cooling devices are arranged on the two heat exchangers so as to improve the refrigeration efficiency. The further first heat exchanger 1 and the second heat exchanger 2 may be a combination of different types of heat exchangers.
3. The condenser of the invention can be formed by combining more than two heat exchangers with different pipe diameters or different types, different heat exchangers through which the refrigerant flows are selected according to the state of the refrigerant, and the refrigerant with low dryness or full liquid phase exchanges heat in the heat exchange pipe with small pipe diameter, so that the heat exchange efficiency is improved and the refrigerant charge amount is reduced.
The above description is only for the purpose of illustrating the preferred embodiments of the present invention and is not to be construed as limiting the invention, and any modifications, equivalents and improvements made within the spirit and principle of the present invention are intended to be included within the scope of the present invention. The above description is only a preferred embodiment of the present invention, and it should be noted that, for those skilled in the art, several modifications and variations can be made without departing from the technical principle of the present invention, and these modifications and variations should also be regarded as the protection scope of the present invention.
Claims (12)
1. A condensing unit, characterized by: the method comprises the following steps:
the heat exchanger comprises a first heat exchanger (1) and a second heat exchanger (2), wherein the first heat exchanger (1) is provided with a first inlet (11) allowing refrigerant to enter and a first outlet (12) allowing the refrigerant to flow out after temperature-reducing heat exchange, and the second heat exchanger (2) is provided with a second inlet (21) allowing the refrigerant to enter and a second outlet (22) allowing the refrigerant to flow out after temperature-reducing heat exchange;
the supercooling section of the second heat exchanger (2) is provided with a third inlet (23) which can be communicated with the first outlet (12), the third inlet (23) and the first outlet (12) are communicated through an intermediate pipe (3), so that fluid flows to the second heat exchanger (2) from the first outlet (12), the intermediate pipe (3) and the third inlet (23) in sequence, and the pipe diameter of the first heat exchange pipe (13) of the first heat exchanger (1) is larger than that of the second heat exchange pipe (24) of the second heat exchanger (2).
2. A condensing unit according to claim 1, characterized in that:
the supercooling section of the second heat exchanger (2) is a partial pipe section of the second heat exchange pipe (24) relatively close to the second outlet (22); and/or the middle pipe (3) is also provided with a pressure regulating device (4).
3. A condensation device according to claim 1 or 2, characterized in that:
the first heat exchanger (1) is a fin type heat exchanger, the first heat exchange tube (13) is a snake-shaped bent tube, and a plurality of heat exchange fins (14) are arranged on the first heat exchange tube (13); and/or, the second heat exchanger (2) is a microchannel heat exchanger, the second heat exchange tube (24) comprises heat exchange flat tubes (241) and a collecting tube (242), the supercooling section comprises at least one heat exchange flat tube (241) close to the second outlet (22), the middle tube (3) is communicated to the collecting tube (242) and communicated with the heat exchange flat tube (241) in the supercooling section, and the cross sectional area of the first heat exchange tube (13) is larger than that of the heat exchange flat tube (241).
4. A condensation device according to claim 1 or 2, characterized in that:
the first heat exchanger (1) is a fin heat exchanger, the second heat exchanger (2) is also a fin heat exchanger, and the cross sectional area of the first heat exchange tube (13) is larger than that of the second heat exchange tube (24); or the first heat exchanger (1) is a micro-channel heat exchanger, the second heat exchanger (2) is also a micro-channel heat exchanger, and the cross-sectional area of the heat exchange flat pipe of the first heat exchanger (1) is larger than that of the heat exchange flat pipe of the second heat exchanger (2).
5. A condensation device according to any one of claims 1-4, characterized in that:
the device is characterized by further comprising an evaporative cooling device, wherein the evaporative cooling device can spray water or mist for cooling the first heat exchanger (1) and/or the second heat exchanger (2).
6. A condensing unit according to claim 5, characterized in that:
the evaporative cooling device comprises a spraying device (5), wherein the spraying device (5) is positioned above the first heat exchanger (1) so as to spray water onto the first heat exchanger (1).
7. A condensing unit according to claim 6, characterized in that:
the evaporative cooling device further comprises a water pump (6) and a water receiving disc (7), the water pump (6) is communicated with the spraying device (5) through a first water pipe (101), the water receiving disc (7) is communicated with the water pump (6) through a second water pipe (102), and the water receiving disc (7) is located at the lower end of the first heat exchanger (1) and used for receiving water falling from the first heat exchanger (1).
8. A condensing unit according to claim 7, characterized in that:
the evaporative cooling device further comprises a spraying device (8), the spraying device (8) is communicated with the water pump (6) through a third water pipe (103), and the spraying device (8) can spray the second heat exchanger (2).
9. A condensing unit according to claim 8, characterized in that:
the first heat exchanger (1) and the second heat exchanger (2) are arranged up and down, the first heat exchanger (1) is located above the second heat exchanger (2), the water pan (7) is arranged below the first heat exchanger (1) and above the second heat exchanger (2), and the spraying device (8) is arranged above the second heat exchanger (2) and below the water pan (7).
10. An air conditioning system characterized by: comprising a compression device (91), a throttling device (92), an evaporator (93) and a condensation device according to any one of claims 1-9.
11. The air conditioning system of claim 10, wherein:
the compression device (91) comprises a low-pressure compressor (911) and a high-pressure compressor (912), wherein the exhaust port of the low-pressure compressor (911) is communicated with the second inlet (21) of the second heat exchanger (2), the exhaust port of the high-pressure compressor (912) is communicated with the first inlet (11) of the first heat exchanger (1), the second outlet (22) of the second heat exchanger (2) is communicated with one end of the evaporator (93) after passing through the throttling device (92), and the other end of the evaporator (93) is divided into two paths and is respectively communicated with the air suction port of the low-pressure compressor (911) and the air suction port of the high-pressure compressor (912).
12. The air conditioning system of claim 10, wherein:
the compression device (91) comprises a single compressor (913), an exhaust port of the single compressor (913) is divided into two paths and is respectively communicated to the first inlet (11) of the first heat exchanger (1) and the second inlet (21) of the second heat exchanger (2), a second outlet (22) of the second heat exchanger (2) is communicated with one end of the evaporator (93) after passing through the throttling device (92), and the other end of the evaporator (93) is communicated to an air suction port of the single compressor (913).
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| CN201911296504.1A CN111059802A (en) | 2019-12-16 | 2019-12-16 | Condensing equipment and air conditioning system who has it |
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| CN201911296504.1A CN111059802A (en) | 2019-12-16 | 2019-12-16 | Condensing equipment and air conditioning system who has it |
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| CN111895492A (en) * | 2020-08-14 | 2020-11-06 | 珠海格力电器股份有限公司 | Air conditioning system, air conditioner and control method of air conditioning system |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN111811040A (en) * | 2020-08-14 | 2020-10-23 | 珠海格力电器股份有限公司 | Air conditioning system and control method thereof |
| CN111895492A (en) * | 2020-08-14 | 2020-11-06 | 珠海格力电器股份有限公司 | Air conditioning system, air conditioner and control method of air conditioning system |
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| CN112050302A (en) * | 2020-09-17 | 2020-12-08 | 安徽建筑大学城市建设学院 | Air conditioner refrigerating system with high efficiency and low energy consumption |
| CN115218299A (en) * | 2022-06-16 | 2022-10-21 | 上海伯涵热能科技有限公司 | Ultra-high energy efficiency dehumidifier for cutting off thermal bridge connection between supercooling section and condensing section fin |
| CN115218298A (en) * | 2022-06-16 | 2022-10-21 | 上海伯涵热能科技有限公司 | Super-high energy efficiency dehumidifier with micro-channel heat exchanger adopted in condenser supercooling section |
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