CN110360852B - Phase-change energy tower and heat exchange method thereof - Google Patents
Phase-change energy tower and heat exchange method thereof Download PDFInfo
- Publication number
- CN110360852B CN110360852B CN201910721329.XA CN201910721329A CN110360852B CN 110360852 B CN110360852 B CN 110360852B CN 201910721329 A CN201910721329 A CN 201910721329A CN 110360852 B CN110360852 B CN 110360852B
- Authority
- CN
- China
- Prior art keywords
- heat exchange
- heat
- exchange tube
- phase change
- refrigerant
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
- 238000000034 method Methods 0.000 title claims abstract description 23
- 230000008859 change Effects 0.000 claims abstract description 95
- 239000007788 liquid Substances 0.000 claims abstract description 73
- 239000003507 refrigerant Substances 0.000 claims abstract description 66
- 238000005507 spraying Methods 0.000 claims abstract description 40
- 239000012530 fluid Substances 0.000 claims abstract description 21
- 238000001704 evaporation Methods 0.000 claims abstract description 20
- 230000002829 reductive effect Effects 0.000 claims abstract description 17
- 230000008020 evaporation Effects 0.000 claims abstract description 15
- 230000036961 partial effect Effects 0.000 claims abstract description 15
- 238000007789 sealing Methods 0.000 claims abstract description 4
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims description 67
- 239000007921 spray Substances 0.000 claims description 16
- 239000000945 filler Substances 0.000 claims description 14
- 238000010438 heat treatment Methods 0.000 claims description 13
- 239000002002 slurry Substances 0.000 claims description 12
- 230000008014 freezing Effects 0.000 claims description 9
- 238000007710 freezing Methods 0.000 claims description 9
- 230000008023 solidification Effects 0.000 claims description 9
- 238000007711 solidification Methods 0.000 claims description 9
- 238000012544 monitoring process Methods 0.000 claims description 8
- 238000011010 flushing procedure Methods 0.000 claims description 4
- 239000006260 foam Substances 0.000 claims description 3
- 230000008018 melting Effects 0.000 claims description 3
- 238000002844 melting Methods 0.000 claims description 3
- 230000001737 promoting effect Effects 0.000 claims description 3
- 238000009833 condensation Methods 0.000 abstract description 16
- 230000005494 condensation Effects 0.000 abstract description 16
- 230000000694 effects Effects 0.000 abstract description 7
- 239000000243 solution Substances 0.000 description 50
- 238000001816 cooling Methods 0.000 description 19
- 230000005484 gravity Effects 0.000 description 10
- 239000003094 microcapsule Substances 0.000 description 10
- 238000012546 transfer Methods 0.000 description 9
- 238000005265 energy consumption Methods 0.000 description 8
- 230000008901 benefit Effects 0.000 description 6
- LYCAIKOWRPUZTN-UHFFFAOYSA-N Ethylene glycol Chemical compound OCCO LYCAIKOWRPUZTN-UHFFFAOYSA-N 0.000 description 3
- DNIAPMSPPWPWGF-UHFFFAOYSA-N Propylene glycol Chemical compound CC(O)CO DNIAPMSPPWPWGF-UHFFFAOYSA-N 0.000 description 3
- 238000004891 communication Methods 0.000 description 3
- 230000007423 decrease Effects 0.000 description 3
- 230000000670 limiting effect Effects 0.000 description 3
- 230000001105 regulatory effect Effects 0.000 description 3
- 238000009834 vaporization Methods 0.000 description 3
- 230000008016 vaporization Effects 0.000 description 3
- FAPWRFPIFSIZLT-UHFFFAOYSA-M Sodium chloride Chemical compound [Na+].[Cl-] FAPWRFPIFSIZLT-UHFFFAOYSA-M 0.000 description 2
- 238000004378 air conditioning Methods 0.000 description 2
- 238000006243 chemical reaction Methods 0.000 description 2
- 230000007797 corrosion Effects 0.000 description 2
- 238000005260 corrosion Methods 0.000 description 2
- 238000001514 detection method Methods 0.000 description 2
- 238000011161 development Methods 0.000 description 2
- 230000018109 developmental process Effects 0.000 description 2
- 238000000605 extraction Methods 0.000 description 2
- 230000007774 longterm Effects 0.000 description 2
- 239000000463 material Substances 0.000 description 2
- 230000009467 reduction Effects 0.000 description 2
- 238000005057 refrigeration Methods 0.000 description 2
- 230000000630 rising effect Effects 0.000 description 2
- 230000001932 seasonal effect Effects 0.000 description 2
- 230000001502 supplementing effect Effects 0.000 description 2
- LFQSCWFLJHTTHZ-UHFFFAOYSA-N Ethanol Chemical compound CCO LFQSCWFLJHTTHZ-UHFFFAOYSA-N 0.000 description 1
- 230000009471 action Effects 0.000 description 1
- 230000002528 anti-freeze Effects 0.000 description 1
- 230000002238 attenuated effect Effects 0.000 description 1
- 150000001875 compounds Chemical class 0.000 description 1
- 230000008094 contradictory effect Effects 0.000 description 1
- 230000001276 controlling effect Effects 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 239000000428 dust Substances 0.000 description 1
- 238000004134 energy conservation Methods 0.000 description 1
- 230000007613 environmental effect Effects 0.000 description 1
- 239000002803 fossil fuel Substances 0.000 description 1
- 239000000295 fuel oil Substances 0.000 description 1
- 230000017525 heat dissipation Effects 0.000 description 1
- 238000005338 heat storage Methods 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 239000012535 impurity Substances 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 239000011259 mixed solution Substances 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000000149 penetrating effect Effects 0.000 description 1
- 239000012782 phase change material Substances 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 230000008929 regeneration Effects 0.000 description 1
- 238000011069 regeneration method Methods 0.000 description 1
- 239000012266 salt solution Substances 0.000 description 1
- 239000011780 sodium chloride Substances 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28C—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA COME INTO DIRECT CONTACT WITHOUT CHEMICAL INTERACTION
- F28C1/00—Direct-contact trickle coolers, e.g. cooling towers
- F28C1/14—Direct-contact trickle coolers, e.g. cooling towers comprising also a non-direct contact heat exchange
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F25/00—Component parts of trickle coolers
- F28F25/02—Component parts of trickle coolers for distributing, circulating, and accumulating liquid
- F28F25/06—Spray nozzles or spray pipes
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F27/00—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus
- F28F27/003—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus specially adapted for cooling towers
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
The invention relates to the field of heat exchange equipment, in particular to a phase change energy tower and a heat exchange method thereof. A phase-change energy tower comprises a tower body; the inside of the tower body is provided with a heat exchange tube for sealing and conveying the refrigerant and a spraying system adopting a phase change medium as fluid; the spraying system comprises a sprayer which is arranged above the heat exchange tube and the spraying direction of which faces the heat exchange tube, and a liquid storage tank which is arranged below the heat exchange tube and is used for receiving the phase change medium; the liquid storage tank is communicated with the sprayer through a pipeline, and the phase change medium sprayed out by the sprayer exchanges heat with the refrigerant in the air exchange pipe in a mode of partial evaporation or condensation on the surface of the air exchange pipe. The phase change energy tower adopts a phase change heat exchange scheme in the closed energy tower, so that the heat exchange effect is improved, and the system operation cost is reduced.
Description
Technical Field
The invention relates to the field of heat exchange equipment, in particular to a phase change energy tower and a heat exchange method thereof.
Background
Along with the high-speed growth of Chinese economy, the consumption of energy sources is larger and larger, and the ecological environment is destroyed by massive fossil fuel, so that the greenhouse effect is more and more serious. The energy consumption of the current building in China is huge, and the current building energy consumption accounts for about 27.5% of the energy consumption of the terminal in the whole society in China. And along with the development of town, the energy consumption of the building is rapidly increased, and the development of city causes a great pressure on the energy supply of building energy in China. The energy consumption of the air conditioner accounts for about 30% of the energy consumption of the building, and the improvement of the efficiency of the air conditioning system has great significance for energy conservation and emission reduction.
In the summer hot and winter cold areas of China, because the areas do not have central heating in winter, most of buildings are heated by adopting an electric or air source heat pump with auxiliary heat, a fuel oil boiler, a gas boiler and the like, and the problems of high-grade energy consumption, low primary energy utilization rate, pollution and the like exist. Meanwhile, due to the characteristic of low-temperature high-humidity outdoor air in winter in summer and winter, the outdoor heat exchanger of the air source heat pump system which is used more in the area is difficult to maintain to run under a dry working condition, water vapor in the air is condensed on the surfaces of the fins, and various performance coefficients of the system are greatly reduced after frosting occurs and even cannot work. Aiming at the climate characteristics of the area, the novel heat pump system of the heat source tower heat pump is developed by combining the advantages of the air source heat pump and the cooling tower for the water cooling unit, so as to solve the frosting problem of the outdoor heat exchanger and simultaneously utilizing the sensible heat of wet air and the phase change latent heat of water vapor in winter. The heat source tower is used as a cooling tower to discharge heat to the environment in summer and used as a heat source tower to absorb heat in the air by using the low-temperature antifreeze solution in winter. The equipment has the characteristics of double efficiency in winter and summer, improves the utilization rate of the equipment by one tower, and is energy-saving and environment-friendly.
The heat source tower heat pump solves the defects of idle cooling tower and boiler pollution in winter in the traditional water-cooling chiller boiler adding system, also avoids the frosting problem of the air source heat pump, and has the cost and maintenance cost far lower than those of the water-ground source heat pump system. However, because the heat dissipation of the heat source tower in summer mainly depends on latent heat due to different operating conditions in winter and summer, and the sensible heat ratio in the heat exchange amount of the heat source tower in winter is very large, the latent heat ratio is very small, and the heat exchange efficiency of the heat source tower in winter is lower than that in summer, the heat source tower is generally designed according to the operating conditions in winter, so that the designed heat source tower has a larger volume. The large volume of the heat source tower increases the cost of the heat source tower and is prone to problems with limited field. Meanwhile, building loads are different under different outdoor conditions, the heat source tower heat pump is mainly used in the middle and downstream regions of the Yangtze river at present, and the heat source tower has no obvious advantage in the regions with lower air temperature in winter. This is because the building load and the heat extraction amount from the heat source tower are contradictory, and the building heat load is large when the outdoor air temperature is low, but at this time, it has become difficult for the heat source tower to extract heat from the outdoor air. In such conditions, to extract more heat from the outdoor environment, the temperature of the circulating solution in the heat source tower must be reduced, and the temperature differential increased to extract more heat. As the solution temperature decreases, the evaporation temperature will decrease and the energy efficiency of the system will decrease. Therefore, the heat source tower has certain limit on the outdoor environment temperature in winter, and the heat taken by the heat source tower with the same volume can be attenuated when the environment temperature is too low, so that the heat required by the building is not likely to be satisfied. Therefore, the applicable area of the heat source tower at present is mainly the area of the middle and downstream of the Yangtze river, and the heat source tower is limited to be used in colder areas.
Therefore, how to increase the heat extraction amount of the heat source tower at low ambient temperature, reduce the volume of the heat source tower, increase the application range and efficiency of the heat source tower, and solve the problem of large occupied area of the heat source tower becomes a technical problem which needs to be solved urgently by those skilled in the art.
A cross-flow heat source tower based on phase-change microcapsule solution is recorded in Chinese patent publication No. CN109798615A, and belongs to the technical field of refrigeration air-conditioning. The heat source tower body is connected with a cooling tower fluid pipeline; an air inlet is arranged on the outer side wall of the heat source tower body; a heat exchange cavity is arranged in the heat source tower body, and the air inlet is communicated with the heat exchange cavity; the center of the heat exchange cavity of the heat source tower body is a central through cavity penetrating through the upper part and the lower part of the heat source tower body; PVC filler which absorbs heat from air is filled in the heat exchange cavity, and the PVC filler is phase-change microcapsule solution; the top of the heat exchange cavity is communicated with a cooling tower flowing liquid inlet pipeline; the bottom end of the heat source tower body is communicated with a cooling tower effluent liquid pipeline; liquid enters the filler part in the heat exchange cavity from the liquid inlet pipeline and flows back into the cooling tower from the liquid outlet pipeline at the bottom end of the heat source tower body. In the invention, the phase change material can change phase in the falling process of the phase change microcapsule solution, so that the specific heat capacity is larger, and the temperature is kept unchanged or the change amplitude is small after the solution absorbs heat. The technical scheme has shown that the phase change heat exchange is already applied in the heat source tower at present, and regarding the phase change heat exchange, the vaporization latent heat of water under normal pressure is more than 500 times of the specific heat capacity of water, and the solidification latent heat of water is nearly 80 times of the specific heat capacity of water, so that the heat exchange quantity can be greatly improved by utilizing the phase change, and the circulation quantity of a heat exchange medium is reduced. However, the disadvantage of the solution is that the microcapsule solution adopted in the spraying system of the solution is used as a circulating medium, and after the microcapsule solution is fully subjected to heat mass exchange with air in the filler, the phase change microcapsule solution is subjected to phase change at the moment. Although the phase change microcapsule solution is a novel working medium integrating heat storage and enhanced heat transfer characteristics compared with the common solution, potential safety hazards exist when the microcapsule solution is applied to a heat pump system. In addition, in the scheme of the prior application, the phase-change microcapsule solution adopts a spray open heat exchange mode, and certain problems exist in the application of the microcapsule solution to a heat pump system loop, such as impurity and dust problems caused by open heat exchange, and the like, and the operation cost of the open heat source tower is higher.
For example, chinese patent publication No. CN207439195U discloses a heat source tower for exchanging heat with air in a phase change mode, which comprises a tower and a hot wall heat exchanger, wherein an axial flow fan is arranged at the upper part of the tower; the hot wall heat exchanger comprises an air heat exchange assembly and a non-freezing fluid heat exchange assembly, the air heat exchange assembly is arranged in the tower, the air heat exchange assembly comprises an upper communicating pipe, a lower communicating pipe, a first heat exchange wall and a heating device, the upper communicating pipe is communicated with the lower communicating pipe through the first heat exchange wall, and the lower communicating pipe of the air heat exchange assembly is connected with the heating device; the non-freezing liquid fluid heat exchange assembly comprises a non-freezing liquid heat exchange container and a second heat exchange wall, wherein two ends of the second heat exchange wall are respectively connected to an upper communicating pipe and a lower communicating pipe, and the second heat exchange wall, the upper communicating pipe connected with the second heat exchange wall and the lower communicating pipe are both arranged in the non-freezing liquid heat exchange container; one end of the unfrozen liquid heat exchange container is provided with a liquid inlet of the unfrozen liquid, and the other end of the unfrozen liquid heat exchange container is provided with a liquid outlet of the unfrozen liquid. The heat source tower provided by the utility model can defrost in time with low energy consumption and low cost. When the refrigerating function is realized in summer, the heat source tower of the scheme can be used as a cooling tower, the spraying circulating pump starts to work in the moment, and the spraying circulating pump does not need to work in winter, which is completely different from the existing closed heat source tower. During refrigeration, water is sprayed to the air heat exchange component through the spray header, a water film is formed on the surface of the first heat exchange wall, latent heat of phase change fluid (refrigerant) in the first heat exchange wall is absorbed under the action of high negative pressure, and then the phase change fluid evaporates by itself, so that the phase change fluid is condensed into liquid. The phase-change fluid which becomes liquid flows into the second heat exchange wall in the unfrozen fluid heat exchange assembly through the lower communication pipe to absorb the latent heat of the unfrozen fluid and then is evaporated, and the evaporated phase-change fluid flows into the air heat exchange assembly through the upper communication pipe to exchange heat with the air and the water film outside the air heat exchange assembly. In the scheme, the final temperature of the unfrozen liquid after cooling is lower than that of a conventional open heat source tower (cooling tower), and the closed phase-change remote heat exchange heat source tower can ensure that heat transfer is not influenced by biological slime thermal resistance of the open cooling tower forever, so that the operation cost of a heat pump system of the closed heat source tower is far lower than that of the heat pump system of the open heat source tower and a refrigerating system of the cooling tower. However, in the scheme, the refrigerant is selected as the phase-change fluid, and the spraying circulating pump does not need to work in winter.
The Chinese patent publication text with the authority of CN103438613B records a compound integrated heat source tower heat pump device, and the Chinese patent publication text with the authority of CN105698352B records a winter and summer double-efficient heat source tower for realizing solution regeneration by utilizing solar energy and a heat exchange method. Both of the above patent documents describe a solution for heat exchange with the refrigerant in the heat exchanger tubes by means of a spray system, but the solution is not combined with phase change heat exchange.
Disclosure of Invention
In order to solve the above problems, a first object of the present invention is to provide a phase-change energy tower, which adopts a phase-change heat exchange scheme in a closed energy tower, so as to improve heat exchange effect and reduce system operation cost. The second object of the invention is to provide a heat exchange method of the phase change energy tower.
In order to achieve the above purpose, the present invention adopts the following technical scheme:
a phase-change energy tower comprises a tower body; the method is characterized in that: the inside of the tower body is provided with a heat exchange tube for sealing and conveying the refrigerant and a spraying system adopting a phase change medium as fluid; the spraying system comprises a sprayer which is arranged above the heat exchange tube and the spraying direction of which faces the heat exchange tube, and a liquid storage tank which is arranged below the heat exchange tube and is used for receiving the phase change medium; the liquid storage tank is communicated with the sprayer through a pipeline, and the phase change medium sprayed out by the sprayer exchanges heat with the refrigerant in the air exchange pipe in a mode of partial evaporation or condensation on the surface of the air exchange pipe.
According to the technical scheme, the phase-change energy tower is characterized in that a phase-change medium is adopted in a spraying system in the phase-change energy tower, the phase-change medium sprayed by the spraying system can be adhered to the surface of a heat exchange tube to form a water film or thin ice, and is subjected to heat exchange with a refrigerant in the heat exchange tube in a partial evaporation or condensation mode, the vaporization latent heat of water at normal pressure is 500 times of the specific heat capacity of water, and the solidification latent heat of water is nearly 80 times of the specific heat capacity of water, so that the heat exchange capacity can be greatly improved by utilizing phase change. Compared with the patent text recording scheme with the publication number of CN109798615A, the scheme does not use the phase change medium as the medium in the heat pump circulation system, only uses the phase change medium as the secondary refrigerant, and the refrigerant is conveyed through the closed circulation loop, so that the phase change heat exchange scheme is adopted in the closed energy tower, the heat exchange effect is improved, and the system operation cost is reduced. The scheme of the Chinese utility model with the publication number of CN207439195U is that the refrigerant is selected as the phase-change fluid, the quality of the phase-change fluid is not much, and the heating temperature rising block can strive for more time for heating; however, the scheme uses the phase change medium as the secondary refrigerant, and has essential differences from the phase change medium.
Preferably, an air inlet is formed in the lower end portion of the tower body, an air outlet is formed in the top of the tower body, and a fan for promoting air flow from the air inlet to the air outlet is arranged in the tower body.
In this technical scheme, the inside refrigerant of heat exchange tube can carry out heat exchange (but the exclusive use air heat transfer, does not start spraying system this moment) with the inside air of tower, and the setting of above-mentioned air intake, air outlet and fan can promote inside circulation of air, promotes heat exchange efficiency.
Preferably, a filler is arranged in the tower body between the lower part of the heat exchange tube and the air inlet, and the filler can enable air and the phase change medium to exchange heat secondarily; the fan is positioned on an air outlet of the tower body, and a water/foam remover is arranged in the tower body between the fan and the heat exchange tube. On the basis of the scheme, the filler is positioned below the heat exchange tube, so that the secondary heat exchange between air and solution is facilitated, and the heat exchange is sufficient.
Preferably, the heat exchange tube is a spiral coil, and two axially adjacent coil units in the spiral coil are arranged in a staggered manner; one end of the spiral coil pipe is a liquid inlet and outlet end, and the other end of the spiral coil pipe is an air inlet and outlet end; the liquid inlet and outlet ends of the spiral coil are provided with a distributor, the distributor is connected with each liquid inlet and outlet end of the heat exchange tube, the liquid inlet and outlet tube is provided with a one-way valve, and the flow direction of the one-way valve is opposite to that of the distributor. In the scheme, the spiral coil is adopted for the purpose of pressure drop of medium in the tube; in general, the pressure drop in a pipe is typically composed of two parts, namely, the on-way resistance and the local resistance, which typically has a coefficient of resistance that is several times that of the on-way resistance. In the traditional multi-flow tube bank arrangement mode, when a medium flows in a tube, the direction needs to be changed by 180 degrees when the flow is changed, so that local resistance is increased once every direction change, the total pressure drop is increased, the spiral tube basically has along-path resistance, the local resistance is negligible, and the total pressure drop of the medium in the tube can be reduced. Further, the two axially adjacent coil units are staggered, namely the upper and lower coil units are staggered, and the coils of the lower coil unit are positioned between the two coils of the upper coil unit. Because, traditional calandria is arranged in line, and upper and lower calandria aligns promptly, and water sprays on the pipe row from the top, because the clearance between the pipe row, some water can't spray on the pipe and cause to spray insufficiently, and the wind of below also has some short circuit from the pipe row in addition, makes wind and pipe heat transfer insufficient. The staggered arrangement that this scheme adopted, medium, the fluid on the coil pipe of upper coil pipe unit can drop to on the coil pipe of lower floor's coil pipe unit along the pipe surface, so all water can spray on the pipe, sprays fully like this, and in addition, the wind that comes on the bottom can not short circuit, and wind produces the vortex through crisscross pipe moreover, has strengthened the heat transfer effect of wind side. In addition, the distributor has the advantages of being uniform in distribution and high in heat exchange coefficient.
Preferably, at least a first temperature sensor for measuring the surface temperature of the coil pipe, a second temperature sensor for measuring the temperature of the phase-change medium in the liquid storage tank and a third temperature sensor for detecting the air temperature of the air inlet are arranged in the tower body. The detection data provided by the first temperature sensor, the second temperature sensor and the third temperature sensor is used for monitoring the operation of the heat source tower in the scheme.
Preferably, an auxiliary heating device is arranged in the liquid storage tank and is used for assisting heating when the ambient temperature is particularly low.
When the refrigerant flows through the heat exchanger tube, the spraying system sprays the phase-change medium in the liquid storage tank to the surface of the heat exchanger tube through the sprayer, and performs heat exchange with the refrigerant in the heat exchanger tube in a mode of partial evaporation or condensation; so as to liquefy or gasify the refrigerant in the heat exchange tube.
Preferably, the heat exchange method includes a summer mode and a winter mode;
Summer mode: refrigerant gas enters the gas inlet and outlet ends of the heat exchange tube; the spraying system is operated, a phase-change medium is sprayed on the surface of the heat exchange tube through a sprayer, a water film is formed on the surface of the heat exchange tube by the phase-change medium, heat is absorbed by a partial evaporation method, the refrigerant in the heat exchange tube releases heat to be liquefied, and finally the refrigerant is discharged through the liquid inlet and outlet ends of the heat exchange tube;
Winter mode: the refrigerant liquid enters the liquid inlet and outlet ends of the heat exchange tube, and the temperature of the refrigerant liquid is lower than the solidification temperature of the phase change medium; the spraying system is operated, a phase change medium is sprayed on the surface of the heat exchange tube through the sprayer, the phase change medium forms thin ice on the surface of the heat exchange tube, heat is released in a partial condensation mode, the refrigerant in the heat exchange tube absorbs the heat to be gasified, and finally the refrigerant is discharged through the air inlet end and the air outlet end of the heat exchange tube.
Preferably, in winter mode of the heat exchange method;
Setting a unit time T, and monitoring the change of the difference between the solution temperature and the surface temperature of the coil; when the difference value between the temperature of the surface of the coil pipe and the freezing point of the corresponding solution is reduced to a set value, increasing the flow rate of a spraying system, flushing thin ice on the surface of the coil pipe into a liquid storage tank, and melting the thin ice into liquid; when the difference between the temperature of the surface of the coil pipe and the freezing point of the corresponding solution is reduced to a set value, the flow of the spraying system is regulated back to normal.
Preferably, in winter mode of the heat exchange method;
An online solution specific gravity meter is arranged in the liquid storage tank, and when ice slurry starts to be generated on the surface of the coil pipe, certain ice slurry can be accumulated in the liquid storage tank; when the specific gravity of the solution is greater than a set value, increasing the flow of a spraying system, flushing the thin ice on the surface of the coil into a liquid storage tank, and melting the thin ice into liquid; when the specific gravity of the solution is smaller than the set value, the flow of the spraying system is regulated back to normal.
The two schemes are mainly characterized in that the flow of the spraying system is controlled by detecting the difference of data, and the thin ice on the surface of the coil pipe is flushed into the liquid storage tank in a flow increasing mode of the spraying system, so that the two schemes are two parallel embodiments, and one scheme is adopted.
In combination with all the structures, the phase-change energy tower has the following advantages:
The spiral coils are adopted and staggered up and down, so that the resistance of the refrigerant in the tube is smaller, the spraying heat exchange outside the tube is more sufficient, and the total heat transfer coefficient is higher;
the heat exchange coil is free of fins, so that the problems of corrosion and scaling caused by long-term operation are avoided, and the operation is maintenance-free;
The heat is absorbed by the water evaporation latent heat in summer as the evaporation cold, the water condensation or even icing latent heat is absorbed by the heat source tower in winter, the water-saving phase change latent heat in different seasons is fully utilized, and the heat exchanger efficiency is higher;
When the evaporator is used as a heat source tower, the refrigerant inlet adopts a distributor, so that the distributor is more uniform in distribution and higher in heat exchange, and when the evaporator is used for evaporating and cooling in summer, the distributor is bypassed through the one-way valve;
the filler is positioned below the coil pipe, and air and solution exchange heat for the second time, so that heat exchange is complete;
The refrigerant directly enters the heat source tower to exchange heat with the solution, so that the intermediate heat exchange temperature difference is reduced, and the system efficiency is higher;
compared with the traditional air cooling unit, the coil pipe in winter can not frost, the operation efficiency is improved, and the use of a user can not be influenced;
The method has the advantages that the method is more energy-saving according to the change of the seasonal environment and the change of multiple modes of the service condition;
The closed structure is adopted, so that little water flows, and the water consumption is reduced.
Drawings
Fig. 1 is a schematic diagram of a phase change energy tower according to the present invention.
Description of the embodiments
Embodiments of the present invention are described in detail below, examples of which are illustrated in the accompanying drawings, wherein like or similar reference numerals refer to like or similar elements or elements having like or similar functions throughout. The embodiments described below by referring to the drawings are illustrative and intended to explain the present invention and should not be construed as limiting the invention.
In the description of the present invention, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "clockwise", "counterclockwise", etc. indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings are merely for convenience in describing the present invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, be configured and operated in a specific orientation, and thus should not be construed as limiting the present invention.
Furthermore, the terms "first," "second," and the like, are used for descriptive purposes only and are not to be construed as indicating or implying a relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defining "a first" or "a second" may explicitly or implicitly include one or more such feature. In the description of the present invention, unless otherwise specified, the meaning of "a plurality" is two or more, unless otherwise clearly defined.
In the present invention, unless explicitly specified and limited otherwise, the terms "mounted," "connected," "secured," and the like are to be construed broadly and may be, for example, fixedly connected, detachably connected, or integrally connected; can be mechanically or electrically connected; can be directly connected or indirectly connected through an intermediate medium, and can be communication between two elements. The specific meaning of the above terms in the present invention can be understood by those of ordinary skill in the art according to the specific circumstances.
In the present invention, unless expressly stated or limited otherwise, a first feature "above" or "below" a second feature may include both the first and second features being in direct contact, as well as the first and second features not being in direct contact but being in contact with each other through additional features therebetween. Moreover, a first feature being "above," "over" and "on" a second feature includes the first feature being directly above and obliquely above the second feature, or simply indicating that the first feature is higher in level than the second feature. The first feature being "under", "below" and "beneath" the second feature includes the first feature being directly under and obliquely below the second feature, or simply means that the first feature is less level than the second feature.
Examples
A phase change energy tower as shown in fig. 1 includes a tower body 12. The tower body 12 is internally provided with a heat exchange tube 11 for sealing and conveying the refrigerant and a spraying system adopting a phase change medium as fluid. The spraying system comprises a sprayer 13 arranged above the heat exchange tube 11 and having a spraying direction facing the heat exchange tube 11, and a liquid storage tank 14 arranged below the heat exchange tube 11 and used for receiving the phase change medium. The liquid storage tank 14 is communicated with the sprayer 13 through a pipeline, a solution pump 15 is arranged on the pipeline and used for supplying power to the sprayer 13 from the liquid storage tank 14, a liquid level meter 16 and a liquid supplementing channel 17 are arranged on the liquid storage tank 14, and when the liquid level meter 16 monitors that the phase change medium in the liquid storage tank 14 is lower than a set height, the phase change medium is supplemented through the liquid supplementing channel 17. In addition, an auxiliary heating device is arranged in the liquid storage tank 14 and is used for auxiliary heating when the ambient temperature is particularly low, so as to prevent the phase-change medium from solidifying in the liquid storage tank 14.
The heat exchange tube 11 is a spiral coil, and two axially adjacent coil units in the spiral coil are arranged in a staggered manner. One end of the spiral coil pipe is a liquid inlet and outlet end, and the other end is an air inlet and outlet end. The liquid inlet and outlet ends of the spiral coil are provided with a distributor 18, and the distributor 18 is connected with each liquid inlet and outlet end of the heat exchange tube 11. In the above solutions, the purpose of using helical coils is to reduce the pressure drop of the medium in the tube. In general, the pressure drop in a pipe is typically composed of two parts, namely, the on-way resistance and the local resistance, which typically has a coefficient of resistance that is several times that of the on-way resistance. The conventional multi-flow tube array is shown in the following figure, when the medium flows in the tube, the direction needs to be changed by 180 degrees when the flow is changed, so that the local resistance is increased once every direction change, the total pressure drop is increased, the spiral tube basically has the along-path resistance, the local resistance is negligible, and the total pressure drop of the medium in the tube can be reduced. Further, the two axially adjacent coil units are staggered, namely the upper and lower coil units are staggered, and the coils of the lower coil unit are positioned between the two coils of the upper coil unit. Because, traditional calandria range is straight-lined, and upper and lower calandria is to it, and water sprays on the tube bank from the top, because the clearance between the tube bank, some water can't spray on the tube and cause to spray insufficiently, and the wind of below also has some short circuit from the tube bank in addition, makes wind and tube heat transfer insufficient. The staggered arrangement that this scheme adopted, medium, the fluid on the coil pipe of upper coil pipe unit can drop to on the coil pipe of lower floor's coil pipe unit along the pipe surface, so all water can spray on the pipe, sprays fully like this, and in addition, the wind that comes on the bottom can not short circuit, and wind produces the vortex through crisscross pipe moreover, has strengthened the heat transfer effect of wind side. In addition, the distributor 18 is used for distributing more uniformly and exchanging heat more.
An air inlet is formed in the lower end portion of the tower body 12, an air inlet grille 19 is arranged on the air inlet, an air outlet is formed in the top of the tower body 12, and a fan 10 for promoting air flow from the air inlet to the air outlet is arranged in the tower body 12. In this technical scheme, the inside refrigerant of heat exchange tube 11 can carry out the heat exchange with the inside air of tower body 12, and the setting of above-mentioned air intake, air outlet and fan 10 can promote inside circulation of air, promotes heat exchange efficiency. In a further preferred scheme, a filler 101 is arranged in the tower body 12 between the lower part of the heat exchange tube 11 and the air inlet, and the filler 101 can enable air and the phase change medium to exchange heat secondarily. The fan 10 is positioned on an air outlet of the tower body 12, and a foam remover 102 is arranged in the tower body 12 between the fan 10 and the heat exchange tube 11. On the basis of the scheme, the filler 101 is positioned below the heat exchange tube 11, so that the secondary heat exchange between air and solution is facilitated, and the heat exchange is sufficient.
In the above solution, at least a first temperature sensor for measuring the surface temperature of the coil, a second temperature sensor for measuring the temperature of the phase change medium in the liquid storage tank 14, and a third temperature sensor for detecting the air temperature of the air inlet are provided in the tower body 12. The detection data provided by the first temperature sensor, the second temperature sensor and the third temperature sensor are used for monitoring the operation of the heat source tower in the scheme, namely, the temperature of the heat exchanger coil and the temperature of the air inlet are detected, and the environmental temperature and the use load are judged. The refrigerant in the heat exchange tube 11 exchanges heat with the air in the tower 12, and the phase change medium in the sprayer 13 exchanges heat to make different modes of adjustment according to the ambient temperature and the use load, including but not limited to the following modes:
When the ambient temperature is relatively low, such as in excessive seasons or even when the ambient temperature is lower than the indoor temperature, but the indoor needs to be refrigerated: at this time, the system can be switched to a natural cooling mode, the compressor is not turned on, and the heat source tower fan 10 is turned on and off according to the condensing temperature.
When the ambient temperature is low in summer, the heat source tower fan 10 is in an on mode and an off mode according to the condensation temperature, and when the heat source tower fan 10 is started, the solution pump is in an on mode and an off mode according to the condensation temperature.
When the ambient temperature is higher in summer; the heat source tower fan 10 operates in the strongest gear, and is used for improving the system efficiency according to the rated frequency and the frequency-increasing operation mode of the condensation temperature solution pump.
When the ambient temperature is very low in winter; the heat source tower fan 10 operates in the strongest gear, and may have an ice slurry phase change heat mode and an auxiliary heating mode.
When the ambient temperature is low in winter; the heat source tower fan 10 operates and may have a vapor condensed phase conversion heat mode and an ice slurry phase conversion heat mode.
When the ambient temperature is higher in winter; the heat source tower blower 10 has two modes of on and off according to the evaporation temperature, and the solution pump has two modes of on and off when the heat source tower blower 10 is turned on.
In the above-mentioned scheme, the phase-change medium sprayed by the sprayer 13 exchanges heat with the refrigerant inside the heat exchange tube in a manner of partial evaporation or condensation on the surface of the heat exchange tube. The phase change medium adopted by the scheme can be an alcohol solution such as ethylene glycol or propylene glycol or a salt solution such as sodium chloride mixed solution, and the concentration of the solution can be regulated according to the minimum operating environment temperature so as to change the freezing point, so that the method is suitable for the natural environment of the region where the phase change energy tower is positioned. The technical scheme relates to a phase-change energy tower, wherein a phase-change medium is adopted in a spraying system in the phase-change energy tower, the phase-change medium sprayed by the spraying system can be adhered to the surface of a heat exchange tube 11 to form a water film or thin ice, and the water film or the thin ice is subjected to heat exchange with a refrigerant in the heat exchange tube 11 in a partial evaporation or condensation mode, the vaporization latent heat of water at normal pressure is 500 times of the specific heat capacity of water, and the solidification latent heat of water is nearly 80 times of the specific heat capacity of water, so that the heat exchange capacity can be greatly improved by utilizing phase change. Compared with the patent text recording scheme with the publication number of CN109798615A, the scheme does not use the phase change medium as the medium in the heat pump circulation system, only uses the phase change medium as the secondary refrigerant, and the refrigerant is conveyed through the closed circulation loop, so that the phase change heat exchange scheme is adopted in the closed energy tower, the heat exchange effect is improved, and the system operation cost is reduced. The scheme of the Chinese patent with the publication number of CN207439195U is that the refrigerant is selected as the phase-change fluid, the quality of the phase-change fluid is not much, and the heating temperature rising block can strive for more time for heating. However, the scheme uses the phase change medium as the secondary refrigerant, and has essential differences from the phase change medium.
In combination with all the structures, the phase-change energy tower has the following advantages:
the spiral coils are adopted and are staggered up and down, the resistance of the refrigerant in the tube is smaller, the spraying heat exchange outside the tube is more sufficient, and the total heat transfer coefficient is higher.
The heat exchange coil is free of fins, so that the problems of corrosion and scaling caused by long-term operation are avoided, and the operation is maintenance-free;
The heat source tower absorbs water condensation and even icing latent heat in summer as evaporation cold through water evaporation latent heat, and the heat exchanger is higher in efficiency by fully utilizing water-saving phase change latent heat in different seasons.
When the evaporator is used as a heat source tower, the refrigerant inlet adopts the distributor 18, so that the distributor is more uniform in distribution and higher in heat exchange, and when the evaporator is used for evaporating and cooling in summer, the distributor 18 is bypassed through the one-way valve.
The filler 101 is positioned below the coil pipe, and air and solution exchange heat for the second time, so that heat exchange is sufficient.
The refrigerant directly enters the heat source tower to exchange heat with the solution, so that the intermediate heat exchange temperature difference is reduced, and the system efficiency is higher.
Compared with the traditional air cooling unit, the coil pipe in winter can not frost, the operation efficiency is improved, and the use of a user can not be influenced.
The multiple modes are switched according to the change of the seasonal environment and the use condition, so that the energy is saved.
The closed structure is adopted, so that little water flows, and the water consumption is reduced.
Examples
This embodiment is a heat exchange method based on the phase change energy tower of embodiment 1, and thus is implemented using the specific phase change energy tower of embodiment 1 described above. Specifically, the present embodiment relates to a heat exchange method of a phase-change energy tower, when the refrigerant flows through the inside of the heat exchanger tube, the spraying system sprays the phase-change medium in the liquid storage tank 14 to the surface of the heat exchanger tube 11 through the sprayer 13, and performs heat exchange with the refrigerant inside the heat exchanger tube in a manner of partial evaporation or condensation. So as to liquefy or gasify the refrigerant in the heat exchange tube 11.
The heat exchange method comprises a summer mode and a winter mode.
Summer mode: the refrigerant gas enters the gas inlet and outlet ends of the heat exchange tube 11. The spraying system operates, a phase change medium is sprayed on the surface of the heat exchange tube 11 through the sprayer 13, a water film is formed on the surface of the heat exchange tube 11 by the phase change medium, heat is absorbed by a partial evaporation method, the refrigerant in the heat exchange tube releases heat to be liquefied, and finally the refrigerant is discharged through the liquid inlet and outlet ends of the heat exchange tube 11.
Winter mode: the refrigerant liquid enters the liquid inlet and outlet ends of the heat exchange tube 11, and the temperature of the refrigerant liquid is lower than the solidification temperature of the phase change medium. The spraying system operates, a phase change medium is sprayed on the surface of the heat exchange tube 11 through the sprayer 13, the phase change medium forms thin ice on the surface of the heat exchange tube 11, heat is released in a partial condensation mode, the refrigerant in the heat exchange tube absorbs the heat to be gasified, and finally the refrigerant is discharged through the air inlet and outlet ends of the heat exchange tube 11.
Compared with the prior art, the heat exchange scheme of the energy source tower has the main difference with the prior art that the phase change heat exchange is performed in winter, the heat exchange spiral coil is used as an evaporator, two-phase refrigerant enters a coil sense through the distributor 18, and refrigerant media can be uniformly distributed, so that the heat exchange efficiency is improved on one hand, and the surface heat exchange of the coil is uniform on the other hand, so that the control of phase change heat is also facilitated. In winter, the phase change has two modes, and the two modes can occur simultaneously. The first mode is that water vapor in the air is condensed into water due to the reduction of the temperature of the air, heat is released to exchange heat with the air and the coil, and as mentioned above, the condensation latent heat of the water is tens times of the specific heat capacity of the water, so that the heat exchange efficiency of the heat source tower can be greatly improved through the condensation phase change heat exchange of the water, and the circulating air quantity is reduced. In another mode, part of the circulating solution is pulped, water is solidified into ice to release heat, and heat exchange quantity and heat exchange efficiency can be greatly improved in a short time.
There are two concepts for specific control methods using ice slurry circulating solution phase change media: a method for controlling the phase change of ice slurry includes such steps as measuring the temp of refrigerant medium in coil tube, measuring the temp of T Pipe at surface of coil tube, monitoring the temp of refrigerant medium in coil tube and the heat exchange quantity of coil tube, if the temp of refrigerant medium in coil tube is raised in short time while the heat exchange quantity of coil tube is obviously increased, setting a time T, integrating control, monitoring the difference between temp of solution and surface temp of coil tube, increasing the frequency of solution pump, flushing ice slurry on coil tube, and increasing the flow rate.
In another control method, an on-line solution specific gravity meter is arranged in the solution tank, when ice slurry is generated on the surface of the coil pipe, certain ice slurry is accumulated in the solution tank, the specific gravity of the solution is changed, the specific gravity change value can be set by monitoring the specific gravity change value, for example, when the specific gravity increase value exceeds 5%, the frequency of the solution pump is adjusted, when the specific gravity is recovered to be normal, for example, the specific gravity change value is less than 2%, the value can be set, and the frequency of the solution pump is reduced to be normal.
The two schemes are mainly different in that the flow of the spraying system is controlled by detecting the difference of data, and the thin ice on the surface of the coil pipe is flushed into the liquid storage tank 14 in a flow increasing mode of the spraying system, so that the two schemes are two parallel embodiments, and one scheme is adopted.
In the description of the present specification, a description referring to terms "one embodiment," "some embodiments," "examples," "specific examples," or "some examples," etc., means that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the present invention. In this specification, schematic representations of the above terms do not necessarily refer to the same embodiments or examples. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples.
Although embodiments of the present invention have been shown and described above, it will be understood that the above embodiments are illustrative and not to be construed as limiting the invention, and that variations, modifications, alternatives, and variations may be made in the above embodiments by those skilled in the art without departing from the spirit and principles of the invention.
Claims (2)
1. A heat exchange method of a phase change energy tower is characterized by comprising the following steps of: the phase change energy tower comprises a tower body (12); a heat exchange tube (11) for sealing and conveying the refrigerant and a spraying system adopting a phase change medium as fluid are arranged in the tower body (12); the spraying system comprises a sprayer (13) which is arranged above the heat exchange tube (11) and the spraying direction of which faces the heat exchange tube (11), and a liquid storage tank (14) which is arranged below the heat exchange tube (11) and is used for receiving phase change media; the liquid storage tank (14) is communicated with the sprayer (13) through a pipeline, and a phase change medium sprayed out of the sprayer (13) exchanges heat with a refrigerant in the heat exchange tube (11) in a mode of partial evaporation or solidification on the surface of the heat exchange tube (11);
An air inlet is formed in the lower end part of the tower body (12), an air outlet is formed in the top of the tower body (12), and a fan (10) for promoting air flow from the air inlet to the air outlet is arranged in the tower body (12);
A filler (101) is arranged in the tower body (12) between the lower part of the heat exchange tube (11) and the air inlet, and the filler (101) can enable air and a phase change medium to exchange heat secondarily; the fan (10) is positioned on an air outlet of the tower body (12), and a foam remover (102) is arranged in the tower body (12) between the fan (10) and the heat exchange tube (11);
The heat exchange tube (11) is a spiral coil, and two axially adjacent coil units in the spiral coil are arranged in a staggered manner; one end of the spiral coil pipe is a liquid inlet and outlet end, and the other end of the spiral coil pipe is an air inlet and outlet end; a distributor (18) is arranged at the liquid inlet and outlet end of the spiral coil, the distributor (18) is connected with each liquid inlet and outlet end of the heat exchange tube (11), a one-way valve is arranged on the liquid inlet and outlet tube, and the flow direction of the one-way valve is opposite to that of the distributor (18); at least a first temperature sensor for measuring the surface temperature of the coil pipe, a second temperature sensor for measuring the temperature of the phase-change medium in the liquid storage tank (14) and a third temperature sensor for detecting the air temperature of the air inlet are arranged in the tower body (12);
The heat exchange method of the phase change energy tower adopts the following scheme that when the refrigerant flows through the heat exchange tube (11), the spraying system sprays the phase change medium in the liquid storage tank (14) to the surface of the heat exchange tube (11) through the sprayer (13) and exchanges heat with the refrigerant in the heat exchange tube (11) in a partial evaporation or solidification mode; so as to liquefy or gasify the refrigerant in the heat exchange tube (11);
it includes a summer mode and a winter mode;
Summer mode: refrigerant gas enters the air inlet end and the air outlet end of the heat exchange tube (11); the spraying system is operated, a phase change medium is sprayed on the surface of the heat exchange tube (11) through a sprayer (13), a water film is formed on the surface of the heat exchange tube (11) by the phase change medium, heat is absorbed by a partial evaporation method, the refrigerant in the heat exchange tube (11) releases heat to be liquefied, and finally the heat is discharged through the liquid inlet and outlet ends of the heat exchange tube (11);
Winter mode: the refrigerant liquid enters the liquid inlet and outlet ends of the heat exchange tube (11), and the temperature of the refrigerant liquid is lower than the solidification temperature of the phase change medium; the spraying system is operated, a phase change medium is sprayed on the surface of the heat exchange tube (11) through a sprayer (13), the phase change medium forms thin ice on the surface of the heat exchange tube (11), heat is released in a partial solidification mode, the refrigerant in the heat exchange tube (11) absorbs the heat to be gasified, and finally the refrigerant is discharged through the air inlet end and the air outlet end of the heat exchange tube (11);
in winter mode, for a certain concentration of solution corresponding to a freezing point temperature Tice, when T pipe < = Tice-0.5 ℃, monitoring the temperature of refrigerant medium in the coil and heat exchange heat of the coil, wherein the temperature of refrigerant in the coil rises temporarily and the heat exchange heat of the coil obviously increases, setting a time T, then carrying out integral control on the time T, by monitoring the difference value change of the temperature of the solution and the surface temperature of the coil, accumulating to the set value of 360 ℃ for a second when the integral value, increasing the frequency of a solution pump, flushing ice slurry on the surface of the coil with large water, melting the flushed ice slurry into a solution again into a solution tank, and when the difference value between the surface temperature of the coil and the freezing point of the corresponding solution is reduced to the set value, reducing the solution pump to normal running frequency, thereby completing an ice slurry phase change heat exchange cycle.
2. The heat exchange method of a phase change energy tower according to claim 1, wherein: an auxiliary heating device is arranged in the liquid storage tank (14).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910721329.XA CN110360852B (en) | 2019-08-06 | 2019-08-06 | Phase-change energy tower and heat exchange method thereof |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910721329.XA CN110360852B (en) | 2019-08-06 | 2019-08-06 | Phase-change energy tower and heat exchange method thereof |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN110360852A CN110360852A (en) | 2019-10-22 |
| CN110360852B true CN110360852B (en) | 2024-06-11 |
Family
ID=68223432
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201910721329.XA Active CN110360852B (en) | 2019-08-06 | 2019-08-06 | Phase-change energy tower and heat exchange method thereof |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN110360852B (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111326822B (en) * | 2020-02-28 | 2021-08-13 | 西安交通大学 | Phase-change cooling system and working method thereof |
| CN111777990A (en) * | 2020-06-24 | 2020-10-16 | 华南理工大学 | Preparation and application of microcapsule type phase-change fluid applicable to low-temperature environment |
Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1595027A (en) * | 2004-06-24 | 2005-03-16 | 上海交通大学 | Defroster for realizing refrigerator evaporator frost-free operation |
| TW200521397A (en) * | 2003-12-31 | 2005-07-01 | Ind Tech Res Inst | Defrosting method and apparatus with adaptive control for refrigerators and refrigerating showcase |
| CA2590715A1 (en) * | 2007-02-13 | 2008-08-13 | Brr Technologies, Inc. | Unit cooler with integrated refrigeration and dehumidification |
| CN103438613A (en) * | 2013-09-02 | 2013-12-11 | 东南大学 | Compound integrated heat source tower heat pump device |
| CN105698352A (en) * | 2016-01-29 | 2016-06-22 | 东南大学 | Winter-summer double-efficient heat source tower for achieving solution regeneration through solar energy and heat exchange method |
| CN207439195U (en) * | 2017-11-09 | 2018-06-01 | 湖南创化低碳环保科技有限公司 | It is a kind of using phase transformation mode and the heat source tower and air-conditioning system of air heat-exchange |
| CN109574334A (en) * | 2018-12-20 | 2019-04-05 | 中科合成油技术有限公司 | The method that a kind of pair of strong brine carries out depth concentration and separation of solid and liquid |
| CN109798615A (en) * | 2019-01-25 | 2019-05-24 | 东南大学 | A kind of transverse flow type heat source tower based on phase-change microcapsule solution |
| CN210570083U (en) * | 2019-08-06 | 2020-05-19 | 英特换热设备(浙江)有限公司 | Phase-change energy tower |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US9528745B2 (en) * | 2011-07-12 | 2016-12-27 | Maersk Line A/S | Reducing or avoiding ice formation in an intermittently operated cooling unit |
-
2019
- 2019-08-06 CN CN201910721329.XA patent/CN110360852B/en active Active
Patent Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| TW200521397A (en) * | 2003-12-31 | 2005-07-01 | Ind Tech Res Inst | Defrosting method and apparatus with adaptive control for refrigerators and refrigerating showcase |
| CN1595027A (en) * | 2004-06-24 | 2005-03-16 | 上海交通大学 | Defroster for realizing refrigerator evaporator frost-free operation |
| CA2590715A1 (en) * | 2007-02-13 | 2008-08-13 | Brr Technologies, Inc. | Unit cooler with integrated refrigeration and dehumidification |
| CN103438613A (en) * | 2013-09-02 | 2013-12-11 | 东南大学 | Compound integrated heat source tower heat pump device |
| CN105698352A (en) * | 2016-01-29 | 2016-06-22 | 东南大学 | Winter-summer double-efficient heat source tower for achieving solution regeneration through solar energy and heat exchange method |
| CN207439195U (en) * | 2017-11-09 | 2018-06-01 | 湖南创化低碳环保科技有限公司 | It is a kind of using phase transformation mode and the heat source tower and air-conditioning system of air heat-exchange |
| CN109574334A (en) * | 2018-12-20 | 2019-04-05 | 中科合成油技术有限公司 | The method that a kind of pair of strong brine carries out depth concentration and separation of solid and liquid |
| CN109798615A (en) * | 2019-01-25 | 2019-05-24 | 东南大学 | A kind of transverse flow type heat source tower based on phase-change microcapsule solution |
| CN210570083U (en) * | 2019-08-06 | 2020-05-19 | 英特换热设备(浙江)有限公司 | Phase-change energy tower |
Also Published As
| Publication number | Publication date |
|---|---|
| CN110360852A (en) | 2019-10-22 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN110360769B (en) | Heat pump system with phase-change energy tower and heat exchange method thereof | |
| CN101457964B (en) | Cold storage air conditioner system with test function | |
| CN203116203U (en) | Air cooling air-conditioning system provided with condenser cooling supercooling device | |
| CN201177332Y (en) | Double cold source heat pump centralized type air conditioner device possessing heat recovery and ice cold-storage function | |
| CN101571331B (en) | Solar phase-change heat storage absorption refrigeration fresh-keeping system | |
| CN103423917A (en) | Air-source central air-conditioning hot water triple-generation heat pump unit | |
| CN202675964U (en) | Heat superconductor water source heat exchanger | |
| CN101140125A (en) | Dynamic ice cold-storage method and apparatus | |
| CN110360852B (en) | Phase-change energy tower and heat exchange method thereof | |
| CN101338958B (en) | Air conditioner heat exchange type condensator and spray evaporative cooling system | |
| CN102261706A (en) | Natural cold source multi-temperature-level cold accumulation system based on heat pipe | |
| CN210532739U (en) | Heat pump system with phase change energy tower | |
| CN101788205A (en) | Highly-efficient air energy water source heat pump integrated unit | |
| CN103499163A (en) | Direct expansion type solar heat pump air conditioning system | |
| CN111928389B (en) | Efficient cold and heat supply system based on combined operation of heat source tower and ice cold accumulation | |
| CN206905581U (en) | Data center's energy-saving multifunctional cooling tower | |
| CN210570083U (en) | Phase-change energy tower | |
| CN101936613B (en) | Integrated heat exchange system | |
| CN201852397U (en) | Improved heat-exchange device of evaporating cold and defrosting water | |
| CN204268750U (en) | A kind of net for air-source heat pump units utilizing waste heat energy storage to defrost | |
| CN203550280U (en) | Direct-expansion solar heat pump air-conditioning system | |
| CN104566726A (en) | Novel household efficient static ice-making and indirect de-icing type cooling air conditioning system | |
| CN201753994U (en) | Integrated heat exchange system | |
| CN104315635A (en) | Medium- and small-sized high-temperature-difference double-working-condition dynamic ice-slurry cold storage air conditioner | |
| CN212158210U (en) | Energy tower and heat pump system thereof |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| CB02 | Change of applicant information | ||
| CB02 | Change of applicant information |
Address after: 313300 phase III, Tangpu Industrial Park, Anji County, Huzhou Economic Development Zone, Zhejiang Province Applicant after: Zhejiang Intech Technology Co.,Ltd. Address before: 313300 phase III, Tangpu Industrial Park, Anji County, Huzhou Economic Development Zone, Zhejiang Province Applicant before: EXTEK ENERGY EQUIPMENT (ZHEJIANG) Ltd. |
|
| GR01 | Patent grant |