CN100378425C - Method and apparatus for cooling fluid and dehumidifying and cooling gas - Google Patents
Method and apparatus for cooling fluid and dehumidifying and cooling gas Download PDFInfo
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- CN100378425C CN100378425C CNB961981083A CN96198108A CN100378425C CN 100378425 C CN100378425 C CN 100378425C CN B961981083 A CNB961981083 A CN B961981083A CN 96198108 A CN96198108 A CN 96198108A CN 100378425 C CN100378425 C CN 100378425C
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- gas stream
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- heat exchanger
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- temperature
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- 239000012809 cooling fluid Substances 0.000 title claims description 7
- 238000000034 method Methods 0.000 title description 10
- 239000000112 cooling gas Substances 0.000 title description 2
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims abstract description 148
- 238000001816 cooling Methods 0.000 claims abstract description 103
- 239000012530 fluid Substances 0.000 claims abstract description 65
- 239000007788 liquid Substances 0.000 claims abstract description 59
- 238000002309 gasification Methods 0.000 claims abstract description 37
- 229920006395 saturated elastomer Polymers 0.000 claims abstract description 4
- 239000007921 spray Substances 0.000 claims description 37
- 238000004891 communication Methods 0.000 claims description 13
- 238000007791 dehumidification Methods 0.000 claims description 10
- 230000002411 adverse Effects 0.000 claims description 8
- 239000003595 mist Substances 0.000 claims description 7
- 238000007747 plating Methods 0.000 claims description 7
- 230000004087 circulation Effects 0.000 claims description 6
- 239000000725 suspension Substances 0.000 claims description 6
- 238000011144 upstream manufacturing Methods 0.000 claims description 6
- 230000008859 change Effects 0.000 claims description 5
- 239000000463 material Substances 0.000 claims description 5
- 239000011859 microparticle Substances 0.000 claims description 4
- 239000003463 adsorbent Substances 0.000 claims description 2
- 238000002156 mixing Methods 0.000 claims description 2
- 238000007599 discharging Methods 0.000 claims 2
- 239000005416 organic matter Substances 0.000 claims 2
- 238000010791 quenching Methods 0.000 claims 2
- 238000001035 drying Methods 0.000 claims 1
- OKKJLVBELUTLKV-UHFFFAOYSA-N Methanol Chemical compound OC OKKJLVBELUTLKV-UHFFFAOYSA-N 0.000 abstract description 24
- 238000009835 boiling Methods 0.000 abstract description 9
- 238000007667 floating Methods 0.000 abstract description 4
- 239000010419 fine particle Substances 0.000 abstract 4
- 239000007789 gas Substances 0.000 description 68
- 238000005507 spraying Methods 0.000 description 16
- 238000010586 diagram Methods 0.000 description 11
- 239000003507 refrigerant Substances 0.000 description 9
- 238000004378 air conditioning Methods 0.000 description 7
- 230000000694 effects Effects 0.000 description 7
- 239000007864 aqueous solution Substances 0.000 description 6
- 238000001179 sorption measurement Methods 0.000 description 6
- LFQSCWFLJHTTHZ-UHFFFAOYSA-N Ethanol Chemical compound CCO LFQSCWFLJHTTHZ-UHFFFAOYSA-N 0.000 description 5
- 239000004411 aluminium Substances 0.000 description 5
- 229910052782 aluminium Inorganic materials 0.000 description 5
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 description 5
- 238000010521 absorption reaction Methods 0.000 description 4
- 239000000498 cooling water Substances 0.000 description 4
- 238000001704 evaporation Methods 0.000 description 4
- 230000008020 evaporation Effects 0.000 description 4
- KWGKDLIKAYFUFQ-UHFFFAOYSA-M lithium chloride Chemical compound [Li+].[Cl-] KWGKDLIKAYFUFQ-UHFFFAOYSA-M 0.000 description 4
- LYCAIKOWRPUZTN-UHFFFAOYSA-N Ethylene glycol Chemical compound OCCO LYCAIKOWRPUZTN-UHFFFAOYSA-N 0.000 description 3
- MUBZPKHOEPUJKR-UHFFFAOYSA-N Oxalic acid Chemical compound OC(=O)C(O)=O MUBZPKHOEPUJKR-UHFFFAOYSA-N 0.000 description 3
- HEMHJVSKTPXQMS-UHFFFAOYSA-M Sodium hydroxide Chemical compound [OH-].[Na+] HEMHJVSKTPXQMS-UHFFFAOYSA-M 0.000 description 3
- 230000015572 biosynthetic process Effects 0.000 description 3
- 230000009467 reduction Effects 0.000 description 3
- 230000008929 regeneration Effects 0.000 description 3
- 238000011069 regeneration method Methods 0.000 description 3
- 238000005496 tempering Methods 0.000 description 3
- CURLTUGMZLYLDI-UHFFFAOYSA-N Carbon dioxide Chemical compound O=C=O CURLTUGMZLYLDI-UHFFFAOYSA-N 0.000 description 2
- NBIIXXVUZAFLBC-UHFFFAOYSA-N Phosphoric acid Chemical compound OP(O)(O)=O NBIIXXVUZAFLBC-UHFFFAOYSA-N 0.000 description 2
- XBDQKXXYIPTUBI-UHFFFAOYSA-M Propionate Chemical compound CCC([O-])=O XBDQKXXYIPTUBI-UHFFFAOYSA-M 0.000 description 2
- KXKVLQRXCPHEJC-UHFFFAOYSA-N acetic acid trimethyl ester Natural products COC(C)=O KXKVLQRXCPHEJC-UHFFFAOYSA-N 0.000 description 2
- 239000003570 air Substances 0.000 description 2
- 239000003795 chemical substances by application Substances 0.000 description 2
- 239000003230 hygroscopic agent Substances 0.000 description 2
- 230000008569 process Effects 0.000 description 2
- 230000001105 regulatory effect Effects 0.000 description 2
- 230000000630 rising effect Effects 0.000 description 2
- 239000000243 solution Substances 0.000 description 2
- 230000010148 water-pollination Effects 0.000 description 2
- 241000894006 Bacteria Species 0.000 description 1
- 229920000742 Cotton Polymers 0.000 description 1
- 241000195493 Cryptophyta Species 0.000 description 1
- YCKRFDGAMUMZLT-UHFFFAOYSA-N Fluorine atom Chemical compound [F] YCKRFDGAMUMZLT-UHFFFAOYSA-N 0.000 description 1
- 244000287680 Garcinia dulcis Species 0.000 description 1
- UFHFLCQGNIYNRP-UHFFFAOYSA-N Hydrogen Chemical compound [H][H] UFHFLCQGNIYNRP-UHFFFAOYSA-N 0.000 description 1
- CBENFWSGALASAD-UHFFFAOYSA-N Ozone Chemical compound [O-][O+]=O CBENFWSGALASAD-UHFFFAOYSA-N 0.000 description 1
- VYPSYNLAJGMNEJ-UHFFFAOYSA-N Silicium dioxide Chemical compound O=[Si]=O VYPSYNLAJGMNEJ-UHFFFAOYSA-N 0.000 description 1
- 230000009471 action Effects 0.000 description 1
- 229910000147 aluminium phosphate Inorganic materials 0.000 description 1
- 239000001569 carbon dioxide Substances 0.000 description 1
- 229910002092 carbon dioxide Inorganic materials 0.000 description 1
- KRVSOGSZCMJSLX-UHFFFAOYSA-L chromic acid Substances O[Cr](O)(=O)=O KRVSOGSZCMJSLX-UHFFFAOYSA-L 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000007797 corrosion Effects 0.000 description 1
- 238000005260 corrosion Methods 0.000 description 1
- VYQRBKCKQCRYEE-UHFFFAOYSA-N ctk1a7239 Chemical compound C12=CC=CC=C2N2CC=CC3=NC=CC1=C32 VYQRBKCKQCRYEE-UHFFFAOYSA-N 0.000 description 1
- 230000006866 deterioration Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000007613 environmental effect Effects 0.000 description 1
- 238000002474 experimental method Methods 0.000 description 1
- 238000000605 extraction Methods 0.000 description 1
- 239000004744 fabric Substances 0.000 description 1
- 238000011049 filling Methods 0.000 description 1
- 229910052731 fluorine Inorganic materials 0.000 description 1
- 239000011737 fluorine Substances 0.000 description 1
- 238000007710 freezing Methods 0.000 description 1
- 230000008014 freezing Effects 0.000 description 1
- AWJWCTOOIBYHON-UHFFFAOYSA-N furo[3,4-b]pyrazine-5,7-dione Chemical compound C1=CN=C2C(=O)OC(=O)C2=N1 AWJWCTOOIBYHON-UHFFFAOYSA-N 0.000 description 1
- 230000036541 health Effects 0.000 description 1
- 229910052739 hydrogen Inorganic materials 0.000 description 1
- 239000001257 hydrogen Substances 0.000 description 1
- 238000007654 immersion Methods 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 230000007246 mechanism Effects 0.000 description 1
- 229910052751 metal Inorganic materials 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 150000002739 metals Chemical class 0.000 description 1
- 235000006408 oxalic acid Nutrition 0.000 description 1
- 230000000505 pernicious effect Effects 0.000 description 1
- 229920000728 polyester Polymers 0.000 description 1
- 230000005855 radiation Effects 0.000 description 1
- 238000010992 reflux Methods 0.000 description 1
- 230000001932 seasonal effect Effects 0.000 description 1
- 238000005480 shot peening Methods 0.000 description 1
- 239000000741 silica gel Substances 0.000 description 1
- 229910002027 silica gel Inorganic materials 0.000 description 1
- SUKJFIGYRHOWBL-UHFFFAOYSA-N sodium hypochlorite Chemical compound [Na+].Cl[O-] SUKJFIGYRHOWBL-UHFFFAOYSA-N 0.000 description 1
- 239000001488 sodium phosphate Substances 0.000 description 1
- 229910000162 sodium phosphate Inorganic materials 0.000 description 1
- 238000005728 strengthening Methods 0.000 description 1
- 239000000126 substance Substances 0.000 description 1
- 229920003002 synthetic resin Polymers 0.000 description 1
- 239000000057 synthetic resin Substances 0.000 description 1
- RYFMWSXOAZQYPI-UHFFFAOYSA-K trisodium phosphate Chemical compound [Na+].[Na+].[Na+].[O-]P([O-])([O-])=O RYFMWSXOAZQYPI-UHFFFAOYSA-K 0.000 description 1
- 238000009834 vaporization Methods 0.000 description 1
Images
Classifications
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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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
- F24F1/0007—Indoor units, e.g. fan coil units
- F24F1/0043—Indoor units, e.g. fan coil units characterised by mounting arrangements
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F5/00—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater
- F24F5/0007—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater cooling apparatus specially adapted for use in air-conditioning
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
- F24F1/0007—Indoor units, e.g. fan coil units
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F3/00—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems
- F24F3/12—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling
- F24F3/14—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification
- F24F3/1411—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification by absorbing or adsorbing water, e.g. using an hygroscopic desiccant
- F24F3/1423—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification by absorbing or adsorbing water, e.g. using an hygroscopic desiccant with a moving bed of solid desiccants, e.g. a rotary wheel supporting solid desiccants
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
- F24H1/00—Water heaters, e.g. boilers, continuous-flow heaters or water-storage heaters
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F2203/00—Devices or apparatus used for air treatment
- F24F2203/10—Rotary wheel
- F24F2203/1028—Rotary wheel combined with a spraying device
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F2203/00—Devices or apparatus used for air treatment
- F24F2203/10—Rotary wheel
- F24F2203/1032—Desiccant wheel
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F2203/00—Devices or apparatus used for air treatment
- F24F2203/10—Rotary wheel
- F24F2203/1056—Rotary wheel comprising a reheater
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F2203/00—Devices or apparatus used for air treatment
- F24F2203/10—Rotary wheel
- F24F2203/1068—Rotary wheel comprising one rotor
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F2203/00—Devices or apparatus used for air treatment
- F24F2203/10—Rotary wheel
- F24F2203/1084—Rotary wheel comprising two flow rotor segments
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Life Sciences & Earth Sciences (AREA)
- Sustainable Development (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
A gas flow Aa saturated with vapor of a volatile liquid such as water and containing a large quantity of floating fine particles of a volatile liquid such as atomized water is sent into one group of small through holes 4 of a cross flow type or counter flow type heat exchanger 3, while a fluid B to be cooled is passed through another group of small through holes 5, sensible heat exchange being carried out between the gas flow Aa and fluid B, the fine particles of a volatile liquid floating in the gas flow Aa being gasefied in accordance with an increase in the temperature of the gas flow Aa, the fluid B being cooled owing to this gasification phenomenon. When water is used for the fine particles of a volatile liquid floating in the gas flow Aa, cold air flow can be supplied in large quantities at a low cost, and, when a liquid of a low boiling point, such as methanol is used for the fine particles of a volatile liquid, the cooling temperature can be reduced.
Description
Technical field
The present invention relates to by means of fluid for example cooling means heat exchange, fluid and the equipment of air and air or liquid and gas, and as the gas of its application for example dehumidifying and cooling method and the equipment of air.
Background technology
In order to cool off air or other gas or liquid, one to being with compressor waving property refrigerant such as freon to be compressed and liquefied, and cools off by the heat of gasification of the freon of liquefaction, and such refrigerator is general.So in addition refrigerator in order to emit the heat of compression of freon, uses to allow freon pass through coiled pipe, allows water spray this coiled pipe and allows air along flowing simultaneously in the other direction, the cooling tower that cools off by the heat of gasification of this water.
In general air-conditioning, make every effort to obtain the air of comfortable temperature and humidity, must reduce temperature and humidity simultaneously more in the occasion of handling the high temperature outside airs that wet.In the occasion of carrying out such air-conditioning owing to will use compressor compresses freon, so consumed energy is very big, and freon atmospheric ozone is destroyed is an individual problem.Moreover also consumed energy in large quantities of cooling tower.
Disclosure of an invention
The present invention utilizes heat exchanger to come for example method and apparatus of air or other gas or liquid of cooling fluid, and as its application, with for example air dewetting cooling of gas, with less energy, do not use fluorine Lyons, and supply with the air with comfortable temperature and humidity or the gas person of other low temperature and low humidities continuously.
Other heat exchangers that the present invention is to use orthogonal crossflow heat exchanger or two kinds of different fluids of temperature directly not to contact each other, sensible heat by means of cryogenic gas A and high temperature fluid B exchanges cooling down high-temperature fluid B, cryogenic gas A is become by the state of the saturated with vapor of steam or other volatile liquids, and then become and make fine water droplet or other volatile liquids drip the state that is scattered in equably in large quantities wherein, be the gas stream Aa of the state that in gas, suspends of a large amount of fine droplets, this gas stream Aa is sent into heat exchanger one side's runner, high temperature fluid B is sent into the opposing party's runner, the fine liquid drops M evaporation of sensible heat in heat exchanger makes above-mentioned gas stream Aa by fluid B, by its heat of evaporation refrigerating gas Aa, the heat exchange of flowing Aa and fluid B by this chilled gas comes cooling fluid B person expeditiously.
Brief description of drawings
Fig. 1 is key diagram and a part of enlarged drawing thereof of an example of expression fluid-cooled method and apparatus of the present invention.
Fig. 2 is perspective view and a part of enlarged drawing thereof of an example of expression orthogonal crossflow heat exchanger.
Fig. 3 is the cutaway view of another example of expression cooling means of fluid of the present invention and equipment.
Fig. 4 is the key diagram of another example of expression cooling means of fluid of the present invention and equipment.
Fig. 5 is the air curve map of data of the cooling of the fluid shown in the presentation graphs 4.
Fig. 6 is the key diagram of the reference examples of expression cooling means of fluid and equipment.
Fig. 7 is the air curve map of data of the cooling of the fluid shown in the presentation graphs 6.
Fig. 8 is the key diagram of another example of expression cooling means of fluid of the present invention and equipment.
Fig. 9 is the air curve map of data of the cooling of the fluid shown in the presentation graphs 8.
Figure 10 is the key diagram of expression with the data of the cooling of methanol aqueous solution.
Figure 11 is the air curve map of expression with the data of the cooling of methanol aqueous solution.
Figure 12 is the key diagram of another example of expression fluid cooling means of the present invention and equipment.
Figure 13 is the perspective view of contraflow heat exchanger.
Figure 14 is the perspective view of the example of the heat exchanger that makes up of expression adverse current and cross-current.
Figure 15 is the perspective view of another example of expression orthogonal crossflow heat exchanger.
Figure 16 is the key diagram of example of method and apparatus of the dehumidifying cooling of expression gas of the present invention.
Figure 17 is the key diagram of another example of method and apparatus of the dehumidifying cooling of expression gas of the present invention.
Figure 18 is the key diagram of another example of method and apparatus of the dehumidifying cooling of expression gas of the present invention.
Figure 19 is the block diagram of embodiment of the cooling device of expression refrigerator of the present invention.
Figure 20 is the perspective view of embodiment of the cooling device of expression refrigerator of the present invention.
Figure 21 is the block diagram of another embodiment of the cooling device of expression refrigerator of the present invention.
The optimal morphology that carries out an invention
Invention described in the claim 1 of the present invention, be that the mist that adds volatile liquid in gas stream A is done into saturation state, and become and make the gas stream Aa that vaporific fine droplets M suspends in large quantities, this gas stream Aa is fed the heat exchanger that has a plurality of runners a side runner and the fluid B of need cooling is fed the opposing party's runner, during the runner of gas stream Aa by a side of heat exchanger, the saturation degree (relative humidity when volatile liquid is water) of its gas phase part reduces along with to gas stream Aa the temperature of gas stream Aa being risen, make a large amount of fine droplets M gasifications that in gas stream Aa, suspend, reduce the temperature of gas stream Aa continuously by its heat of gasification, cooling fluid B person continuously whereby, the effect of the gas stream Aa that fine droplets M suspends in large quantities is, the interior sensible heat exchange with fluid B of runner that leans against heat exchanger is heated, take away heat of gasification by fine droplets M gasification, the temperature of gas stream Aa reduces and cooling fluid B.
The 1st embodiment
The flat board 1 and wavelength 3.0mm made by aluminium or other sheet metals or polyester or other synthetic resin thin plates, the corrugated plating 2 of wave height 1.6mm alternatively and also the ripple direction of corrugated plating 2 orthogonal ground is overlapping and be in contact with one another step by step, obtain orthogonal crossflow heat exchanger as shown in Figure 2.In addition, on thin sheet surface, then produce hydrophily and increase surface area with the little convex-concave of formation such as shot-peening.In order to make the aluminium sheet possess hydrophilic property, use sheet material is immersed in the aqueous solution of sodium phosphate, clorox, chromic acid, phosphoric acid, oxalic acid, NaOH etc., perhaps short time impregnating method in boiling water generates hydroaropic substance on the surface of aluminium sheet.If so hydrophily is done on the surface of thin plate, at fluid B the occasion of air or other gases then, can prevent because the pressure that water droplet causes reduces the circulation deterioration that makes gas in the small through hole.
Though illustrate dull and stereotyped 1 and the combination of corrugated plating 2 for example as cross-current type heat exchanger 3, if form tiny ripple on the part of flat board, then surface area further increases, the heat exchanger effectiveness raising.In addition, if the surface of flat board 1 or corrugated plating 2 is done black, then photothermal radiation, absorption increase, the heat exchanger effectiveness raising.
As shown in Fig. 2, Fig. 3, a side's of orthogonal crossflow heat exchanger 3 small through hole group 4 configuration vertically substantially, the opposing party's small through hole group 5 configuration flatly substantially, as shown in Figure 3, conduit 8a, 8b are installed on small through hole group 4 inflow entrance 4a and flow export 4b place respectively, pressure fan Fa and water spray device 6 are installed on conduit 8a,, pressure fan F are installed on conduit 9a inflow entrance 5a and the flow export 5b place that conduit 9a, 9b are installed on small through hole group 5 (Fig. 2) respectively.Moreover Va is a valve of regulating the spray amount of water spray device 6 among the figure.
Preferably can thin as far as possible water droplet distributed equably as water spray device 6, for example air-atomizing nozzle etc. is suitable for.In addition, though the thin as far as possible aspect of water droplet is preferably about diameter 10 μ m, in the occasion of using air-atomizing nozzle to spray, as to make the maximum gauge of water droplet be about 280 μ m, then about 70% drop diameter can be given full play to effect of the present invention below 100 μ m.
Moreover air-atomizing nozzle is water and air-atomizing, if water and air also pressurizes, the water droplet of then spraying diminishes.Particularly, the size of spraying water droplet is subject to the influence of air pressure, preferably applies 3kgf/cm
2Above pressure.In addition also can be with the nozzle that only uses liquid.
Next the effect of this cooling device is described.As shown in Figure 3,, fine water droplet is sprayed among the air stream A in large quantities, leans on the heat of gasification of water droplet to reduce temperature, and improve relative humidity by in outside air or indoor air stream A, using above-mentioned water spray device 6.Then and then do to become to make the air stream Aa of the state that a large amount of fine water droplets M suspends, send into a plurality of runners inlet 4a of a side of heat exchanger 3 by the discharge pressure of pressure fan Fa.
If the air of high temperature stream B is sent into the inflow entrance 5a of heat exchanger 3 with the opposing party's pressure fan F, then air stream Aa seizes the sensible heat of high temperature air stream B during by the runner of heat exchanger 3 by the next door 1 (with reference to Fig. 2) of stream, and air flows the temperature rising of Aa.The relative humidity of air stream Aa reduces as a result, and a large amount of fine water droplets M gasifications that contained among the air stream Aa are by the humidity of its heat of gasification reduction air stream Aa, by next door 1 cooling down high-temperature air stream B.
The cooling principle of this cooling device is described in further detail.The steam pressure of liquid has the state of horizontal liquid level high than liquid under the drop state, and the more little then steam pressure of the diameter of this drop is high more.This phenomenon can be used as Kelvin equation and is expressed as follows.
10g(pr/p)＝20δM/ρrRT
In the formula, p is the steam pressure of horizontal liquid level, and Pr is the steam pressure of the drop of radius r, and M is a molal weight, and δ is a surface tension, and ρ is a fluid density, and R is a gas constant, and T is an absolute temperature.
Thereby the more little then gasification of the radius of water droplet is fast more, and cooling effect is strong more.And then in the process that gasifies in heat exchanger 3 of the water droplet M after spraying, the diameter of water droplet M diminishes, because along with the diameter of the water droplet M steam pressure that diminishes raises, so the gasification of water droplet M is carried out post in heat exchanger 3.In other words, fine water M gasifies in the short time at the utmost point in heat exchanger 3, seizes a large amount of heat of gasification.
If use above-mentioned formula to calculate, then in the occasion of 18 ℃ of water, when the water droplet radius is 1 μ, compares when steam pressure and liquid level are smooth state and raise 0.1%, when the water droplet radius was 10m μ, steam pressure raise 10% approximately.And then when the water droplet radius was 1m μ, steam pressure almost raise exponentially.If the air that fine water droplets M suspends to the water yield is like this sent into heat exchanger 3, then presents the phenomenon of water droplet M rapid ground vapourization in heat exchanger 3.
Use this cooling device to test.As shown in Figure 4, the air stream A that makes 25.9 ℃ of temperature, absolute humidity 8.05g/kg, relative humidity 39% is by water spray device 6, temperature is reduced to 17.5 ℃, do to become to make the air stream Aa of the relative humidity 100% that a large amount of fine water droplets M suspends simultaneously, this air stream Aa is sent into the almost small through hole group's 4 of configuration the inlet 4a vertically of heat exchanger 3 with wind speed 2m/ second.On the other hand, second the high temperature air B of 70.6 ℃ of temperature, absolute humidity 10.44g/kg, relative humidity 5.2% is sent into small through hole group's the inflow entrance 5a of the almost horizontal arrangement of heat exchanger 3 with wind speed 2m/ by pressure fan F.Even small through hole group 4 is not accurately vertical, water droplet also can be used under the state that suspends in the air and send.Fig. 5 is the air cooled air curve map of representing at this moment, and table 1 is its result of the test.
Table 1 (sprayer is arranged)
Between high temperature air stream B and air stream Aa, carry out the sensible heat exchange, as mentioned above by flow the gasification of the fine water droplets that suspends among the Aa at air, reduce the temperature of air stream Aa continuously, cooling air stream B, air stream B does not improve absolute humidity and the temperature reduction, become the comfortable air of 18.6 ℃ of temperature, absolute humidity 10.44g/kg, relative humidity 78%, it is used as air feed SA.Gas stream Aa is owing to the air stream Ab that becomes 30.7 ℃ of temperature, relative humidity 100% by heat exchanger 3, and this air stream Ab is discharged in the atmosphere.
The sensible heat exchange efficiency η of this occasion
1Be depicted as 97.9% as the formula in the table 1 (1), show that heat exchanger effectiveness is very high.B, SA, Aa represent air themperature separately in the formula (1).The spray amount of this occasion water droplet M is approximately per hour 8-15 liter.The air stream A of this occasion and the flow of B are about 180m
3/ hour.Heat exchanger is of a size of 0.25m * 0.25m=0.0625m
2Area since its inlet 4a, 5a surface area be respectively 0.0625m
2, percent opening is about 40%, so the sectional area of small through hole is 0.0625m
2* 40%=0.025m
2, because wind speed is 2m/ second, so air quantity is 0.025m
2* 2m/ second=180m
3/ hour.
For contrast therewith, routine in contrast, orthogonal crossflow heat exchanger that will be identical with employee among the 1st embodiment does not use the result of the test of the occasion of water spray device to be shown in the air curve map of Fig. 6 and table 2 and Fig. 7 in tempering air stream.
Table 2 (not having sprayer)
B, Ba, A represent air themperature separately in the formula (2).The air stream A that temperature is 22.3 ℃ is owing to the air that the sensible heat exchange becomes 62.0 ℃ of temperature flows Ab, and the high temperature air stream B that temperature is 67.2 ℃ becomes the air stream Ba of 36.0 ℃ of temperature owing to the sensible heat exchange.Absolute humidity flows among A, the air stream B at air and does not all change.The sensible heat exchange efficiency η of this moment
1Be depicted as 69.5% as the formula in the table 2 (2).At the occasion sensible heat exchange efficiency water spray is 97.9%, is 69.5% at the occasion sensible heat exchange efficiency water spray not, and by the spraying of water, heat exchanger effectiveness improves 30% approximately.Identical among other conditions of this occasion and the 1st embodiment the occasion of water spray.
The 2nd embodiment.
Use this cooling device in addition equally, as shown in Figure 8, the air of 25.7 ℃ of temperature, absolute humidity 12.20g/kg, the relative humidity 59.0% bundle 2m/ air stream A of second that does to become a common practice, make it pass through water spray device 6, the air stream Aa that does into 20.2 ℃ of temperature, relative humidity 100% and vaporific fine water droplets is suspended in large quantities equably flows the inlet 4a that Aa sends into the small through hole group 4 of heat exchanger to this air.As the air of needs cooling the high temperature air of 34.2 ℃ of temperature, absolute humidity 14.41g/kg, relative humidity 43% is done into the wind speed 2m/ air stream B of second on the other hand, send into the small through hole group's 5 of heat exchanger inlet 5a.Carry out the sensible heat exchange between high temperature air stream B and the air stream Aa, air stream B becomes the cooling air SA of 20.6 ℃ of temperature, absolute humidity 14.41g/kg, relative humidity 95%.Gas stream Aa becomes almost 100% air stream Ab of 25 ℃ of temperature, relative humidity, and air stream Ab is discharged in the atmosphere.The air curve map of this moment is shown in Fig. 9, and result of the test is shown in table 3.
Table 3 (sprayer is arranged)
As shown in the figure, the heat of gasification of water droplet is passed to air stream B by the next door among the gas stream Aa, as shown in the air curve map, the absolute humidity of gas stream B is constant, temperature reduces arrival SA point (20.6 ℃) along the horizontal line of air curve map, air stream Aa is through the line of relative humidity 100%, and temperature is elevated to the Ab point.The sensible heat exchange efficiency of this occasion such as table 3 Chinese style (3) are depicted as 97.1%, with the sensible heat exchange efficiency of the 1st embodiment much at one.In other words, the occasion in that the temperature of fluid B descends if the temperature of air feed SA becomes 20.6 ℃, is fit to idle call, and then the spray amount of water can reduce.The spray amount of water is about 8 liters/hour.
The 3rd embodiment
As shown in fig. 1, the tank D of the water droplet that increase acceptance and air stream Ab discharge simultaneously on the equipment of the Fig. 3 that illustrates in the 1st embodiment, the reflux that lodges in the water of this tank D is that pump P, aqueduct 10, motor-driven valve Va and water level control apparatus are water-level float Vs, level sensor Se, motor-driven valve Vb, and the spray amount adjusting device of water droplet sprayer unit 6 is thermocouple Ta, thermocouple Tb, electric signal amplifier C, motor-driven valve Va.Have among the figure with the part of Fig. 3 same numeral since be with in the 1st embodiment the identical person of part illustrated in fig. 3, so its explanation is omitted.
The aqueduct 10 that water in the tank D is refluxed to water spray device 6 is installed, and the way is provided with pump P and motor-driven valve Va therein.In addition, feed pipe 11 is installed on tank D, floating water-level float Vs on the water surface 13 in tank D, the power on/off magnet valve Vb that is located in the feed pipe 11 is connected with level sensor Se, as shown in the Q portion enlarged drawing of Fig. 1, with the variation of water-level float Vs and level sensor Se sensed water level, if the underwater drops to 13L, then magnetic valve Vb opens and make-up water, if the water surface rises to 13H, then magnetic valve Vb closes and stops the supply of water.
At the temperature sensor of the upstream of water spray device 6 configuration gas stream A thermocouple Ta for example, configuration temperature sensor thermocouple Tb for example in fluid B, C is connected between this thermocouple Ta and the Tb the electric signal amplifier.Detect the temperature difference of these two thermocouple Ta, Tb and send into the electric signal amplifier, along with temperature difference becomes big and operation motor-driven valve Va increases the water spray amount, along with temperature difference diminishes and the water spray amount is reduced.As required, when the water spray amount increases, the power of pressure fan Fa is increased, so that air stream Aa is quickened.
If this occasion is too much from the spray amount of water spray device 6, then fine water droplets accumulates on small through hole group 4 the internal face of heat exchanger 3 becomes current, can not fully gasify simultaneously, but drip.These current are compared with fine water droplets, and surface area becomes minimum, and when high temperature air stream B seizes heat, the gasification of water reduces, and is helpless to cooling.Thereby, the temperature of gas stream Aa is fully reduced, so can not reduce the temperature of high temperature air stream B fully.Become to make the fine water droplets M in the gas stream Aa to contain necessary amount equably if spray, cooling effectiveness height then, water also can be saved.
The 4th embodiment
Also can use the mixing material of ethanol (78.3 ℃ of boiling points), methyl acetate (56.3 ℃ of boiling points), methyl alcohol volatile organic liquids such as (64.7 ℃ of boiling points) or volatile organic liquid and water, replace the water (100 ℃ of boiling points) that in sprayer 6, uses.
As shown in Figure 2, on two surfaces of the corrugate aluminium plates 2 of the next door 1 of making and wavelength 3.4mm, wave height 1.7mm with the aluminium sheet of thickness 25 μ, the microparticle of discrete bond temperature absorption agent silica gel, alternatively superimposed them, obtain the orthogonal crossflow heat exchanger 3 of the size of 250mm * 250mm * 250mm.Use this heat exchanger 3, the cooling device of assembling shown in Figure 10, the data when being used for the water of sprayer 6 with 45% aqueous solution replacement of methyl alcohol in the 1st, 2 embodiment are shown in Figure 10.This occasion is owing to replace water with methanol aqueous solution, so its boiling point reduces, temperature is that 25.9 ℃ air stream A (air stream Aa) after the methanol aqueous solution spraying is reduced to 14.6 ℃.
Because 14.6 ℃ of this air stream Aa flow 51.3 ℃ the heat exchange of B with high temperature air, obtain 17.2 ℃ Cryogenic air SA.If thereby use then can obtain Cryogenic air SA than only spraying with the more lower boiling liquid of water spray.The air curve map of Figure 11 is the air curve map of the state variation of the above air stream B → SA of expression and air stream A → Aa → Ab.
The 5th embodiment
The equipment of present embodiment is to increase gas stream Ab that the outlet 4b from heat exchanger 3 the is discharged device to the gas stream Aa of high humility stream on the equipment that illustrates in the 1st embodiment as shown in Figure 12, at the upstream side of water spray device 6 humidifier is set.With conduit 8e the outlet 4b of heat exchanger 3 is connected with pressure fan Fc in Figure 12, with conduit 8d pressure fan Fc is connected with the runner of the gas stream Aa of high humility, connection is used for sending into as required the branched pipe K of outside air OA on the part of conduit 8e.
On humidifier 7,, can when the needs humidification, supply with water at the valve of the installation midway V of feed pipe Wp.As humidifier 7, there is the multilayer of using for example ultrasonic type, immersion to weave cotton cloth etc.
Make gas stream Aa by heat exchanger 3, with pressure fan Fc the exhaust Ab from outlet 4b is refluxed, Ac uses as gas stream.By humidifier 7 and then the gas stream Aa that becomes to make fine water droplets M to suspend in large quantities by sprayer 6 lanes, heat exchanger 3 is sent in circulation to this gas stream Ac as required.
In Figure 12, cooling end Co is set in the centre of conduit 8e, a plurality of fin Fe are installed on the periphery of conduit 8e, fan housing is installed on these fins and is connected pressure fan Fd, by coming cooling fins Fe by pressure fan Fd, fluid Ab in the cooling duct 8e, the moisture in the cooling high humility fluid Ab makes it dewfall, and dew is lodged in the water tank Da, often by the water in the valve Vc discharge water tank, be back to sprayer 6.
Though the example with the air cooling method that uses the orthogonal crossflow heat exchanger has illustrated fluid cooling means of the present invention, much less, can implement too in the gas beyond air or the cooling of water or other liquid.
The heat exchanger that uses also can use the above-mentioned orthogonal cross flow of heat exchanger replacement of the adverse current shown in reverse-flow, the Figure 14 shown in skewed crossing streaming, Figure 13 and cross-current combination.In the heat exchanger of adverse current shown in reverse-flow, the Figure 14 shown in Figure 13 and cross-current combination, all be that gas stream Aa, the fluid B that fine water droplets is suspended passes through in the small through hole along the direction of arrow among the figure respectively, discharge as gas stream Ab, fluid SA respectively, between two fluid Aa, B, carry out the sensible heat exchange.In addition, can use as shown in Fig. 15, dull and stereotyped 1,1 ... between, clip a plurality of separators 12,12 along the vertical direction of each grade ... the orthogonal V shape heat exchanger of forming, in addition, also can use and same reverse-flow, the adverse current of the superimposed body of above-mentioned honeycomb and the heat exchanger of cross-current combination.
The 6th embodiment
As shown in Figure 16, orthogonal crossflow heat exchanger 3 and the atomizing humidifier 6 of configuration 250mm * 250mm * 250mm are at the prime configuration dehumidifying rotor 14 of heat exchanger 3.Dehumidifying rotor 14 is the superimposed system of honeycomb that combines adsorbent or hygroscopic agent to be become diameter 320mm, width 200mm's is cylindrical.In addition, dehumidifying rotor 14 is separated into adsorption zone 16 and renewing zone 17 by separator 15,15 ', shown in arrow B → HA → SA, constitute flow path by conduit (not shown) respectively, dehumidifying rotor 14 by with 16 change/hour rotate driving continuously along the direction of arrow among the figure.By pressure fan Fb the outside air OA of 34.0 ℃ of temperature, absolute humidity 14.4g/kg, relative humidity 43.1% is done into air stream B, second it is sent into the adsorption zone 16 of dehumidifying rotor 14 with wind speed 2m/.
Whereby, the moisture of air stream B is removed in absorption, obtains dry air stream HA.Then dry air stream HA is sent into the horizontal small through hole group's 5 of heat exchanger 3 inlet 5a.In the renewing zone 17 of dehumidifying rotor 14, by heater H outside air OA is done to become to be heated to regeneration air RA about 80 ℃, send into along the direction of arrow among the figure, the regeneration of dehumidifying rotor 14 dehumidifications, in outside air, discharge as many wet exhaust EA by renewing zone 17.
On the other hand, if be that 26 ℃, relative humidity are in the temperature of air stream A, do into relative humidity 100% by atomizing humidifier 6 humidifications at 58% o'clock, then the temperature of air stream Aa becomes 17.0 ℃.And then water is flowed Aa to this air spray, do into the state of the countless suspensions of fine water droplets, send into the inflow entrance 4a of heat exchanger 3.
Above-mentioned dry air HA is by heat exchanger 3, air stream Aa with the countless suspensions of fine water droplets carries out the sensible heat exchange whereby, same with the explanation of the 1st embodiment, in heat exchanger 3 inside, the heat of gasification that flows the fine water droplets of Aa by air is cooled, and becomes the comfortable air feed SA of 20.5 ℃ of temperature, absolute humidity 4.5g/kg, relative humidity 30%.
From then on an embodiment as seen, 34 ℃, the outside air dehumidifying of absolute humidity 14.4g/kg, relative humidity 43.1%, temperature is leaned on the heat of adsorption of moisture and is raise, the dry air that reduces with seasonal humidity passes through heat exchanger 3, obtains the chilled dry air of 20.5 ℃ of temperature, absolute humidity 4.5g/kg, relative humidity 30% whereby.In the occasion that this air is used for air-conditioning, humidification and do into comfortable air conditions suitably.
As dehumidifier, in present embodiment, use rotary, can certainly use double-cylinder type, column type or the Kathabar formula (U.S. Kathabar corporate system: make lithium chloride solution in container, drip of filling hygroscopic agent, air is flowed by the window of container one side, makes the device of airborne moisture adsorption in lithium chloride solution) etc. dehumidifier.
The 7th embodiment
In the present embodiment, after the high temperature air of narration by 70.0 ℃ of cools down, by the process of dehumidifying rotor dehumidifying.
As shown in Figure 17, at the upper side configuration atomizing humidifier 6 of orthogonal crossflow heat exchanger, dehumidifying rotor 14 is configured in the back level of heat exchanger 3.Water is sprayed in the outside air OA of 26.6 ℃ of temperature, absolute humidity 12.2g/kg, relative humidity 58% in atomizing humidifier 6 by pressure fan Fa, when doing into relative humidity 100%, just become 17.5 ℃ of temperature, further water to wherein spraying, make air stream Aa that the droplet of a large amount of water suspends runner 4a by heat exchanger 3 one sides.
On the other hand, second the air of 70.0 ℃ of temperature, absolute humidity 14.4g/kg, relative humidity 7% stream B is sent into the inlet 5a of heat exchanger 3 with wind speed 2m/ with pressure fan Fb.Air stream B carries out the sensible heat exchange and becomes the air stream Ba of low temperature in heat exchanger.The absolute humidity of the absolute humidity of air stream Ba and air stream B much at one.Air stream Aa becomes the air stream Ab of 30.0 ℃ of temperature, relative temperature about 100% by behind the heat exchanger 3 in the exit of heat exchanger 3, discharge in outside air.Dehumidifying rotor 14 is by 16 to change/hour to drive along direction of arrow rotation among the figure.
Above-mentioned chilled air is flowed the adsorption zone 16 that Ba sends into dehumidifying rotor 14, and moisture is removed in absorption, obtains the dry air stream HA of 55 ℃ of temperature, absolute humidity 4.5g/kg, relative humidity 5%.The operation of dehumidifying rotor 14 is as described in the 5th embodiment.Though very difficult with the suction type dehumidifying from high temperature air, shown in the embodiment like this,, then can effectively dehumidify simply if after with cools down, use dehumidifier, can obtain chilled dry air.
The 8th embodiment
Resulting air stream HA in the 7th embodiment, temperature is that 55.0 ℃, relative humidity are 5%, as general idle call, temperature is too high and relative humidity is low excessively.Therefore present embodiment is to make this air stream HA further by heat exchanger 3b, so that obtain having the air feed SA of the temperature and humidity that is suitable for idle call.
As shown in Figure 18, make high temperature air stream B by orthogonal crossflow heat exchanger 3a and dehumidifying rotor 14 equally, obtain air stream HA with the 7th embodiment.Because operation and the 7th embodiment so far are identical, so omit repeat specification.Second orthogonal crossflow heat exchanger 3b is arranged on the back level of dehumidifying rotor 14, promptly the flow path of the air HA that flows out from the outlet of handling air, also atomizing humidifier 6b similarly is set with above-mentioned the 7th embodiment at the upstream side of the side's of second heat exchanger 3b runner 4.Because the effect of this second heat exchanger 3b is identical with the heat exchanger 3 of above-mentioned the 7th embodiment, so omit explanation.
On the other hand, the dry air HA of the adsorption zone 16 by dehumidifying rotor 14 is sent into the horizontally disposed small through hole group's 5 of heat exchanger 3b runner inlet 5a, with contain a large amount of fine water droplets and chilled air stream Aa and carry out the sensible heat exchange, obtain the comfortable air feed SA of 20.5 ℃ of temperature, absolute humidity 4.5g/kg, relative humidity 30%.If the occasion increase and decrease at the air condition of regulating air feed SA is flowed the water yield of spraying among the Aa to air, then can change the temperature of air feed SA, on the other hand in the low excessively occasion of the humidity of air feed SA, if reduce the regeneration temperature of dehumidifying rotor, then because the reduction of the wet-out property of dehumidifying rotor 14, so can improve the humidity of air feed SA, can freely carry out comfortable air-conditioning.
In above the 6th～the 8th embodiment, if low-boiling liquid, for example ethanol, methyl acetate, methyl alcohol etc. are sprayed in air stream Aa, with the water that replaces using in the atomizing humidifier, then can further reduce the temperature of air supply stream SA.
Also have, in all embodiments, can be with supersonic atomizer as atomising mechanism.In addition, as the water spray device, except air-atomizing nozzle, can use single fluid nozzle without air.Moreover, though in above embodiment, relative humidity is done into 100% with 1 grade of atomizing humidifier, do simultaneously to become to make the particulate of a large amount of water to suspend, but also can be set as atomizing humidifier multistage, become to make relative humidity become 100% at elementary humidification, become to make the particulate of a large amount of water to suspend secondary the lane.Importantly, the air of the particulate that makes the water about diameter 10 μ a large amount of states that suspend in the air of relative humidity 100% is just passable by heat exchanger.
Though in above embodiment, showed for example corrugated plating and dull and stereotyped mutual superimposed person as heat exchanger, but the invention is not restricted to these, so long as have a plurality of runners, the big person of water passage surface area is just passable, and the runner person who for example is provided with a plurality of heat-exchange fins at the two ends of heat pipe is just passable.
The 9th embodiment
In Figure 19, the 18th, known refrigerator, inside has compressor (not shown).The 19th, heat exchanger, the runner 20 of one side is snakelike tubulose, the opposing party's runner 21 is for surrounding the shell-like of snakelike tubulose runner 20.
In a side's of heat exchanger 19 runner 20, the Freon gas of the high temperature that comes out from compressor (Chlorofluorocarbons hydrogen: the trade mark of U.S. DuPont company) or other refrigerant flow through, cooling water flows through in the opposing party's of heat exchanger 19 runner 21.
The opposing party's of heat exchanger 19 runner 21 22 is connected with a side's of orthogonal crossflow heat exchanger 3 runner by the road, is provided with circulating pump 23 in the way of pipeline 22.In other words, become the state that cooling water circulates between heat exchanger 19 and the cross-current type heat exchanger 3 under air-tight state.Moreover 9a, 9b are chambers.
Fa is a pressure fan, and the suction side is discharged side and combined with the upper end of chamber 24 atmosphere opening.In addition, the lower end of chamber 24 is connected with the opposing party's of orthogonal crossflow heat exchanger 3 runner inlet 4a.And the opposing party's of orthogonal crossflow heat exchanger 3 runner exit is to atmosphere opening.
D is a water receiving tank, is arranged on the below of orthogonal crossflow heat exchanger 3, and it is provided with adjutage 26.
As shown in Figure 20, one side's of this orthogonal crossflow heat exchanger 3 small through hole group's 4 axis is almost vertically arranged, another small through hole group 5 axis is almost flatly arranged, chamber 24 is installed on small through hole group 4 inflow entrance 4a, and pressure fan Fa and water spray device 6 are installed on chamber 24.In addition, on small through hole group 5 inflow entrance 5a and flow export 5b, chamber 9a, 9b are installed respectively, on chamber 9a, 9b, connect pipe 22.
The Action Specification of above formation is as follows.At first, be illustrated with regard to the cooling body that uses orthogonal crossflow heat exchanger 3.Make pressure fan Fa work and form air stream A, water sprayer 6 is done into gas stream Aa to water to wherein spraying.The water yield of spraying will surpass the amount that gasifies owing to spraying.So, the part gasification of the water droplet of being sprayed, owing to gasification seizes heat of gasification, the temperature of the gas stream Aa that is carried in the chamber 24 descends.In addition, the air in the chamber 24 are gas stream Aa, and relative humidity becomes 100%, and it is promptly vaporific to become the state that the particulate of water a large amount of in this air suspends.
Then, the air that suspends in large quantities of this fine water droplets enters a side's of orthogonal crossflow heat exchanger 3 small through hole group 4.When refrigerator 18 was running status, the temperature of the refrigerant of carrying in a side's of heat exchanger 19 runner 20 uprised, and carried out heat exchange with the water of carrying in the opposing party's of heat exchanger 19 runner 21.
The water of carrying in the opposing party's of heat exchanger 19 runner 21 by pump 23 circulations, enters the opposing party's of orthogonal crossflow heat exchanger 3 small through hole group 5 by pipe 22 and chamber 9a.Then, between a side small through hole group 4 and the opposing party's small through hole group 5,1 carries out the sensible heat exchange through the next door.In other words, the cooling water of the small through hole group 5 by the opposing party cools off by the gas stream Aa of the small through hole group 4 by a side, and the gas stream Aa of the small through hole group 4 by a side is heated simultaneously.
So the relative humidity of the gas stream Aa of the small through hole group 4 by a side becomes below 100%, the particulate gasification of wherein contained a large amount of water, heat of gasification is seized and gas stream Aa is cooled.
Thus, the temperature of the gas stream Aa of small through hole group 4 by a side almost keeps constant low-temperature condition, so the cooling water of the small through hole group 5 by the opposing party is cooled in the gamut of the small through hole group 5a of heat exchanger 3 He on the total length continuously, it is constant that its temperature also almost keeps.
If this occasion is too much from the spray amount of water spraying device 6, then fine water droplet gathers on the next door of aggegation in the small through hole group 4 of orthogonal crossflow heat exchanger 3, become big water droplet or current, this big water droplet or current are compared with fine water droplets, surface area becomes minimum, the heat that seizes from refrigerant can not make the temperature of gas stream Aa fully reduce, thereby the temperature of refrigerant can not fully reduce.Become to make the fine water droplets in the gas stream Aa that evenly contains more more slightly than necessary Min. if spray, cooling effectiveness height then, water also can be saved.
Then, the water droplet of gasification does not accumulate among the water receiving tank D in the small through hole group 4 of orthogonal crossflow heat exchanger 3, is discharged by adjutage 26.As mentioned above, because the amount that the water yield of spraying from water spraying device 6 gasifies in the small through hole group 4 of orthogonal crossflow heat exchanger 3 no better than, so the water yield of accumulating among the water receiving tank D is seldom, even discarded also no problem fully.Thereby, do not recycle from the water of water spray device 6 spraying, do not have the thing that algae etc. is taken place.
Though in above embodiment, showed the example of water as the liquid that is cooled, but consider freezing of winter, also can in the water that is cooled, add the antifreezing agents such as ethylene glycol of 50% capacity degree, in order to prevent the corrosion of heat exchanger 19 or orthogonal crossflow heat exchanger 3, also can consider to add anticorrosive.
The 10th embodiment
Another embodiment of the cooling device of refrigerator is shown in Figure 21.As follows with the difference of the embodiment of Figure 19.In other words, the 9th embodiment shown in Figure 19 makes water pass through the opposing party's of orthogonal crossflow heat exchanger 3 small through hole group, but this embodiment is the opposing party of orthogonal crossflow heat exchanger 3 is crossed in order from the circulation of air of pressure fan F small through hole group 5.
In other words, F is a pressure fan, combines with the inlet of chamber 9a.The outlet of chamber 9a is incorporated into the opposing party's of orthogonal crossflow heat exchanger 3 small through hole group 5 inlet.Small through hole group 5 outlet 5b goes up in conjunction with the inlet of chamber 9b, and the outlet of chamber 9b is incorporated into radiator 28.
In addition, pipeline 27 is set, so that order is passed through radiator 28 from the refrigerant that refrigerator 18 comes out.And the formation beyond the above-mentioned difference is identical with the 9th embodiment, so omit explanation.
This embodiment is cooled betwixt for air depends on the small through hole group 5 of pressure fan F by the opposing party of orthogonal crossflow heat exchanger 3, arrives radiator 28.Refrigerant from the high temperature of refrigerator 18 27 is sent radiator 28 to by the road, dissipates the heat of refrigerant.Air by small through hole group 5 is sent to this radiator 28.
In other words, radiator 28 leans on the small through hole group 5 chilled air streams by the opposing party of orthogonal crossflow heat exchanger 3 to cool off, and compares with the direct cooler of air of outer boundary, and efficient improves a lot.
In applicant's experiment, use orthogonal crossflow heat exchanger 3 identical persons with the 9th embodiment shown in above-mentioned Figure 19, when 35 ℃ of outside air temperatures, relative humidity 39%, make air in the small through hole group 4 of orthogonal crossflow heat exchanger 3, flow with pressure fan Fa with the speed of 2m/ second, with the water of 12 liters of/hour flows of sprayer 6 sprayings.So the temperature that enters the air of radiator 28 from orthogonal crossflow heat exchanger 3 becomes 18.6 ℃, the cooling effect of refrigerant is high.
This embodiment can be provided with the cooling device of refrigerator of the present invention before the radiator of existing air-conditioning equipment, can improve the efficient of the refrigerator of existing air-conditioning equipment or freezer etc. with simple construction.
Industrial applicibility
Because the present invention constitutes as described above, so its principle be make relative humidity be 100% so that the vaporific gas stream Aa that does to become to make trickle water droplet to suspend equably in large quantities cross a side's of the heat exchanger that has a plurality of fluid passages runner with gas communication as cooling, the fluid B that order needs cooling for example air or water by the opposing party's runner, the gas stream Aa that fine water droplets is suspended contacts by the next door with fluid B, by heated air stream Aa, reduce the relative humidity of gas stream Aa, make the fine water droplets evaporation, come cooling gas flow Aa by its heat of evaporation, simultaneously by next door cooling fluid B, it is characterized in that, by the water spray amount in the increase and decrease water spray device 6, can control the degree of convection cell B cooling.If increase the water spray amount when perhaps the temperature difference of gas stream Aa and high temperature air stream B increases, then fluid Aa and the cooling degree of strengthening high temperature air stream with the temperature difference of high temperature air stream B pro rata can flow B to air and be cooled to almost constant comfortable temperature.And then, can easily obtain dry cooling air by making the combination of this cooling device and dehumidifier.
Described in the 1st embodiment, configuration atomizing humidifier 6 on orthogonal crossflow heat exchanger 3, sensible heat exchange efficiency when air that fine water droplet is suspended in large quantities stream Aa is come cooling down high-temperature air stream B as tempering air stream shows the very high value of 97%-100%.Use with the 1st embodiment in used identical orthogonal crossflow heat exchanger and in tempering air flows, do not use the occasion of sprayer and humidifier, as example is showed in contrast among the 1st embodiment, the sensible heat exchange efficiency is 63%, and the efficient of the heat exchange in the visible fluid cooling of the present invention is high significantly.
Moreover the required consumed energy of this heat exchange is, the operation energy of pressure fan is about 250W, and in contrast, the required heat energy of the cooling of fluid B becomes for example catabiotic 1.5 times to tens times, and this value raises with the rising of the temperature of fluid B.
This fluid cooling device is used for the cooling of gas, adds dehumidifier thereon, as showing among the 6th to the 8th embodiment, can be used for the dehumidifying cooling of gas, can be used as air-conditioning equipment and use.Because it is cheap significantly as mentioned above that this occasion is moved required funds, so in the occasion that for example is used for the dehumidifying cold-room in the confined chamber, there is no need indoor air is recycled repeatedly, can constantly be taken into fresh outside air and keep the dehumidifying cold-room.Thereby can prevent from fully the increase of carbon dioxide in the room air or other pernicious gases from can provide comfortable space.
Moreover, so owing to unlike cold-room always, use freon not have environmental problem, owing to there is no need to use compressor, do not produce bacterium class or mould that the hot blast because of heat extraction grows, so see that from the health aspect splendid effect is also arranged.
Claims (24)
1. fluid cooling means, it is characterized in that, the volatile liquid small droplet is suspended in the gas stream of the volatile liquid vapor that contains saturation state, obtain vaporific gas stream, this vaporific gas stream is fed a side's of the orthogonal crossflow heat exchanger that has a plurality of runners runner from the top, and the vaporific gas of ratio of need cooling is flowed the high fluid that is cooled of temperature feeds the opposing party in the mode with vaporific gas stream orthogonal runner, during a side's of vaporific gas communication over-heat-exchanger runner, give vaporific gas stream the sensible heat of the be cooled fluid higher than vaporific gas stream temperature, the temperature of vaporific gas stream is risen, make the fine droplets gasification that suspends in the vaporific gas stream, reduce the temperature of vaporific gas stream continuously by its heat of gasification, by means of the sensible heat exchange of vaporific gas stream and the be cooled fluid higher than vaporific gas stream temperature, the cooling fluid that is cooled continuously.
2. the fluid cooling means described in the claim 1 is characterized in that, according to the variation of the temperature of vaporific gas stream and the difference of the temperature of fluid change vaporific gas flow in the suspension amount of fine droplets.
3. the fluid cooling means described in the claim 1 is characterized in that, changes the flow velocity that vaporific gas that fine droplets suspends flows according to the variation of the temperature of vaporific gas stream and the difference of the temperature of fluid.
4. the described fluid cooling means of claim 1 is characterized in that, gas stream is done into the gas stream of saturation state with the steam of volatile liquid, and then adds the mist of volatile liquid in this gas stream, does into the vaporific gas stream that fine droplets suspends.
5. the described fluid cooling means of claim 1, it is characterized in that, the vaporific gas stream that contains a large amount of volatile liquid vapor of discharging from the outlet of a side's of heat exchanger passage is sent back to a side's of heat exchanger the entrance side of path, the mist that adds volatile liquid therein, the vaporific gas stream of doing into the fine droplets suspension recycles.
6. the described fluid cooling means of claim 1 is characterized in that, volatile liquid is the mixing material of water, volatile organic matter liquid or volatile organic matter liquid and water.
7. the described fluid cooling means of claim 1 is characterized in that, with gas-liquid mixed formula nozzle volatile liquid is sprayed.
8. the described fluid cooling means of claim 1 is characterized in that, the diameter of spray droplet is done into below the 280m μ.
9. gas dehumidification cooling means, it is characterized in that, make volatile liquid fine droplets be suspended in the gas stream of the volatile liquid vapor that contains saturation state, produce vaporific gas stream, this vaporific gas is flowed a side's of the orthogonal crossflow heat exchanger that feeds a plurality of runners that have mutual orthogonal from the top runner, and the dry gas that has dehumidified with dehumidifier is in advance circulated into the opposing party's runner, cross in vaporific gas communication during a side the runner of orthogonal crossflow heat exchanger, give vaporific gas stream the sensible heat of dry gas stream, the temperature of this vaporific gas stream is risen, make the fine droplets gasification that suspends in this vaporific gas stream, reduce the temperature of this vaporific gas stream continuously by its heat of gasification, by means of the heat exchange cool drying gas stream of vaporific gas stream, supply with chilled dry gas continuously with dry gas stream.
10. gas dehumidification cooling means, it is characterized in that, the fine droplets of volatile liquid is suspended in the gas stream of the volatile liquid vapor that contains saturation state, produce vaporific gas stream, this vaporific gas is flowed a side's of the orthogonal crossflow heat exchanger that feeds a plurality of runners that have mutual orthogonal from the top runner, and the above-mentioned vaporific gas of the ratio of need cooling is flowed the runner that the high gas communication of temperature is gone into the opposing party, cross in this vaporific gas communication during a side the runner of orthogonal crossflow heat exchanger, give vaporific gas stream the sensible heat of the gas stream higher than vaporific gas stream temperature, the temperature of this vaporific gas stream is risen, make the fine droplets gasification that suspends in this vaporific gas stream, reduce the temperature of vaporific gas stream continuously by its heat of gasification, sensible heat by means of the vaporific gas stream gas stream high with flow temperature than vaporific gas exchanges the high gas stream of the vaporific gas stream of cooling raio temperature continuously, then chilled gas communication is gone into the dehumidifier dehumidifying, supply with chilled dry gas continuously.
11. fluid cooling device, it is characterized in that, wherein the atomising device by means of volatile liquid adds gas stream to the mist of volatile liquid, become the saturated with vapor of volatilized property liquid, and the vaporific gas stream that the vaporific fine droplets of volatile liquid suspends therein, vaporific gas stream is fed from the top heat exchanger that has a plurality of runners a side runner and the high temperature fluid of need cooling is fed the opposing party's runner, during a side's of vaporific gas communication over-heat-exchanger runner, vaporific gas stream seizes the sensible heat of high temperature fluid, make the fine droplets gasification that suspends in the vaporific gas stream, reduce the temperature that vaporific gas flows continuously by its heat of gasification, cool off the high temperature fluid that needs cooling whereby continuously.
12. the fluid cooling device described in the claim 11 wherein at the upstream side of the atomising device of volatile liquid, is provided with the device of introducing volatile liquid vapor.
13. the fluid cooling device described in the claim 11 wherein is provided with the conduit and the pressure fan of entrance side of the gas stream Ab that discharges from a side's of heat exchanger outlet being guided to a side of heat exchanger, makes cooling with gas stream Aa circulation.
14. the described fluid cooling device of claim 11, wherein heat exchanger is orthogonal cross flow, diagonal flow type or the contraflow heat exchanger that constitutes by the superimposed body of honeycomb dull and stereotyped and that corrugated plating is alternatively superimposed, perhaps the heat exchanger of adverse current and cross-current combination.
15. the described fluid cooling device of claim 11, wherein heat exchanger is orthogonal cross flow, diagonal flow type or the contraflow heat exchanger that sheet material is formed by stacking by a plurality of separators, perhaps the heat exchanger of adverse current and cross-current combination.
16. the described fluid cooling device of claim 14 is wherein being fixed microparticle on the runner wall of heat exchanger.
17. the fluid cooling device described in the claim 16, wherein microparticle is the microparticle of adsorbent.
18. gas dehumidification cooling device, it is characterized in that, atomising device by means of volatile liquid adds gas stream to the mist of volatile liquid, become the saturated with vapor of volatilized property liquid, and the vaporific gas stream that the vaporific fine droplets of volatile liquid suspends therein, this vaporific gas stream with water droplet swim aerial state feed from the top heat exchanger that has a plurality of runners a side runner and the gas communication of the high temperature of needs cooling is gone into the opposing party's runner, during a side's of vaporific gas communication over-heat-exchanger runner, vaporific gas stream seizes the sensible heat of fluid, the fine droplets gasification that suspends in the vaporific gas stream, reduce the temperature of vaporific gas stream continuously by its heat of gasification, cooling down high-temperature gas flows continuously whereby, heat exchanger upstream side at high temperature gas flow is provided with dehumidifying rotor, and the air of binding domain that will be by this dehumidifying rotor is as the above-mentioned high temperature gas flow that needs cooling.
19. gas dehumidification cooling device, it is characterized in that, atomising device by means of volatile liquid adds gas stream to the mist of volatile liquid, become saturation state and do into the vaporific gas stream of the vaporific fine droplets suspension of volatile liquid, vaporific gas stream is fed from the top heat exchanger that has a plurality of runners a side runner and the gas communication of the high temperature of needs cooling is gone into the opposing party's runner, during a side's of vaporific gas communication over-heat-exchanger runner, vaporific gas stream seizes the sensible heat of high temperature gas flow, make a large amount of fine droplets gasification that suspends in the vaporific gas stream, reduce the temperature of vaporific gas stream continuously by its heat of gasification, cool off the gas stream that needs cooling whereby continuously, the heat exchanger downstream that the gas that cools off at needs flows is provided with dehydrating unit.
20. gas dehumidification cooling device, it is characterized in that, atomising device by means of volatile liquid adds gas stream to the mist of volatile liquid, become saturation state and do into the vaporific gas stream of the vaporific fine droplets suspension of volatile liquid, this vaporific gas stream with water droplet swim aerial state feed from the top heat exchanger that has a plurality of runners a side runner and the gas communication of the high temperature of needs cooling is gone into the opposing party's runner, during a side's of vaporific gas communication over-heat-exchanger runner, vaporific gas stream seizes the sensible heat of the gas stream that needs cooling, make the fine droplets gasification that suspends in the vaporific gas stream, reduce the temperature of vaporific gas stream continuously by its heat of gasification, cooling needs the gas of cooling to flow continuously whereby, two such gas quench systems are set, between the flowing of the gas stream of needs in two gas quench systems cooling dehumidifying rotor are set.
21. the described gas dehumidification cooling device of claim 18 wherein at the upstream side of the atomising device of volatile liquid, is provided with the introducing device of volatile liquid vapor.
22. the described gas dehumidification cooling device of claim 18 wherein is provided with the conduit and the pressure fan of entrance side of the gas stream of discharging from a side's of heat exchanger outlet being guided to a side of heat exchanger, makes the circulation of vaporific gas stream.
23. the described gas dehumidification cooling device of claim 18, wherein heat exchanger is orthogonal cross flow, diagonal flow type or the contraflow heat exchanger that constitutes by the superimposed body of honeycomb dull and stereotyped and that corrugated plating is alternatively superimposed, perhaps the heat exchanger of adverse current and cross-current combination.
24. the described gas dehumidification cooling device of claim 18, wherein heat exchanger is orthogonal cross flow, diagonal flow type or the contraflow heat exchanger that sheet material is formed by stacking by a plurality of separators, perhaps the heat exchanger of adverse current and cross-current combination.
Applications Claiming Priority (6)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP32348695 | 1995-11-07 | ||
| JP323486/95 | 1995-11-07 | ||
| JP71183/96 | 1996-03-01 | ||
| JP7118396 | 1996-03-01 | ||
| JP181484/96 | 1996-06-21 | ||
| JP18148496A JP3554745B2 (en) | 1996-06-21 | 1996-06-21 | Refrigerator cooling system |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1201516A CN1201516A (en) | 1998-12-09 |
| CN100378425C true CN100378425C (en) | 2008-04-02 |
Family
ID=27300579
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB961981083A Expired - Fee Related CN100378425C (en) | 1995-11-07 | 1996-11-06 | Method and apparatus for cooling fluid and dehumidifying and cooling gas |
Country Status (4)
| Country | Link |
|---|---|
| KR (1) | KR100461934B1 (en) |
| CN (1) | CN100378425C (en) |
| AU (1) | AU708106B2 (en) |
| WO (1) | WO1997017586A1 (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101881491A (en) * | 2010-07-02 | 2010-11-10 | 上海理工大学 | Cross-flow type air handling device |
| CN102759228A (en) * | 2012-07-16 | 2012-10-31 | 西安工程大学 | Cooling and heating dual-purpose evaporative cooling air-conditioner heat exchanger |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| JP3594463B2 (en) * | 1997-10-15 | 2004-12-02 | 株式会社西部技研 | Gas adsorption device |
| JP4607356B2 (en) * | 2000-09-04 | 2011-01-05 | 株式会社西部技研 | Dehumidifying air conditioner |
| JP4466307B2 (en) * | 2004-09-30 | 2010-05-26 | マックス株式会社 | Ventilator and building |
| CN102155767B (en) * | 2008-12-15 | 2013-12-25 | 新疆绿色使者空气环境技术有限公司 | Multi-stage evaporating and cooling refrigeration method |
| NL2006314C2 (en) * | 2010-12-24 | 2012-06-27 | Optimair Holding B V | SYSTEM FOR DRYING AND / OR COOLING A AIR FLOW. |
| JP5771519B2 (en) * | 2011-12-26 | 2015-09-02 | リンナイ株式会社 | Latent heat exchanger and hot water supply device |
| JP6401291B2 (en) * | 2013-12-26 | 2018-10-10 | バーダス テクノロジーズ プライベート リミテッドＶｅｒｄｕｓ Ｔｅｃｈｎｏｌｏｇｉｅｓ Ｐｔｅ．Ｌｔｄ． | Fluid processing apparatus and method for cooling an air flow by fluid processing apparatus |
| CN104048378A (en) * | 2014-06-18 | 2014-09-17 | 南通鸿景天机械设备科技有限公司 | Circulating water indoor cooling system |
| US11000077B2 (en) * | 2017-07-10 | 2021-05-11 | ThermoBionics LLC | System, method, and apparatus for providing cooling |
| CN110482828A (en) * | 2019-09-05 | 2019-11-22 | 广东申菱环境系统股份有限公司 | A kind of industry sludge drying system |
| JP7365553B2 (en) * | 2019-10-25 | 2023-10-20 | 株式会社ノーリツ | heating water heater |
| CN111810455A (en) * | 2020-07-02 | 2020-10-23 | 河海大学 | Water supply device adopting spray water evaporation heat dissipation technology for shaft through-flow pump station |
| CN114198824A (en) * | 2020-09-18 | 2022-03-18 | 广州合一空调设备有限公司 | Special control system for all-in-one machine |
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- 1996-11-06 KR KR10-1998-0703383A patent/KR100461934B1/en not_active IP Right Cessation
- 1996-11-06 WO PCT/JP1996/003249 patent/WO1997017586A1/en active IP Right Grant
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| CN101881491B (en) * | 2010-07-02 | 2012-02-01 | 上海理工大学 | Cross-flow type air handling device |
| CN102759228A (en) * | 2012-07-16 | 2012-10-31 | 西安工程大学 | Cooling and heating dual-purpose evaporative cooling air-conditioner heat exchanger |
Also Published As
| Publication number | Publication date |
|---|---|
| CN1201516A (en) | 1998-12-09 |
| WO1997017586A1 (en) | 1997-05-15 |
| AU7505596A (en) | 1997-05-29 |
| AU708106B2 (en) | 1999-07-29 |
| KR19990067373A (en) | 1999-08-16 |
| KR100461934B1 (en) | 2005-05-17 |
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