CN100378425C - Method and apparatus for cooling of fluids and desiccant cooling of gases - Google Patents

Abstract

The gas flow Aa, which is saturated with vapor of water or other volatile liquids and is suspended in a large amount of mist-like fine water or particles of other volatile liquids, is sent to one side of the straight cross-flow or counter-flow heat exchanger 3 The small through-hole group 4, the fluid B to be cooled passes through another small through-hole group 5, and sensible heat exchange is performed between the gas flow Aa and the fluid B. As the temperature of the gas flow Aa rises, in the gas flow Aa Fluid B is cooled by vaporization of the suspended particles of volatile liquid. If water is used as the fine particles of the volatile liquid suspended in the gas stream Aa, a large amount of cold air can be supplied cheaply, and if a liquid with a low boiling point such as methanol is used as the fine particles of the volatile liquid, the cooling temperature can be lowered.

Description

Method and apparatus for cooling of fluids and desiccant cooling of gases

technical field

The present invention relates to a fluid cooling method and apparatus by means of heat exchange of fluid such as air with air or liquid with gas, and a method and apparatus for dehumidifying cooling of gas such as air as the application thereof.

Background technique

In order to cool air or other gases or liquids, volatile refrigerants such as freons have been compressed and liquefied by compressors, and cooled by the heat of vaporization of liquefied freons. Such refrigerators are common. In addition, in order to release the heat of compression of freon, such a refrigerator uses a cooling tower in which freon passes through the serpentine pipe, water is sprayed on the serpentine pipe while air flows in the opposite direction, and the water is cooled by the heat of vaporization of the water.

General air conditioners strive to obtain air with a comfortable temperature and humidity, but when dealing with high-temperature and humid outside air, the temperature and humidity must be lowered at the same time. In the case of such an air conditioner, since Freon is compressed by a compressor, it consumes a lot of energy, and there is a problem that Freon depletes atmospheric ozone. Furthermore, cooling towers also consume a lot of energy.

disclosure of invention

The present invention is a method and device for cooling a fluid such as air or other gas or liquid using a heat exchanger, and as its application, dehumidifying and cooling the gas such as air, with less energy, without using Freon, and continuously supplying Air with comfortable temperature and humidity, or other low-temperature and low-humidity gases.

The present invention uses a straight cross-flow heat exchanger or other heat exchangers in which two fluids of different temperatures do not directly contact each other, and cools the high-temperature fluid B by means of the sensible heat exchange between the low-temperature gas A and the high-temperature fluid B, and at the same time makes the low-temperature Gas A becomes saturated with water vapor or other volatile liquid vapor, and then becomes a state in which a large number of fine water droplets or other volatile liquid droplets are uniformly dispersed, that is, a large number of fine liquid droplets are suspended in the gas State gas flow Aa, the gas flow Aa is sent to one flow channel of the heat exchanger, and the high-temperature fluid B is sent to the other flow channel, and the sensible heat of the fluid B passes through the heat exchanger to make the above-mentioned gas flow Aa The fine liquid droplets M evaporate, the gas Aa is cooled by the heat of evaporation, and the fluid B is efficiently cooled by the heat exchange between the cooled gas flow Aa and the fluid B.

Brief description of the drawings

Fig. 1 is an explanatory diagram showing an example of the fluid cooling method and equipment of the present invention and a partially enlarged view thereof.

Fig. 2 is a perspective view showing an example of a straight cross-flow heat exchanger and a partially enlarged view thereof.

Fig. 3 is a cross-sectional view showing another example of the fluid cooling method and equipment of the present invention.

Fig. 4 is an explanatory view showing still another example of the fluid cooling method and equipment of the present invention.

FIG. 5 is an air graph showing data for the cooling of the fluid shown in FIG. 4 .

Fig. 6 is an explanatory diagram showing a comparative example of a fluid cooling method and equipment.

FIG. 7 is an air graph showing data for the cooling of the fluid shown in FIG. 6 .

Fig. 8 is an explanatory view showing still another example of the fluid cooling method and equipment of the present invention.

FIG. 9 is an air graph showing data for the cooling of the fluid shown in FIG. 8 .

Fig. 10 is an explanatory diagram showing data of cooling with methanol aqueous solution.

Figure 11 is an air graph showing data for cooling with aqueous methanol.

Fig. 12 is an explanatory view showing still another example of the fluid cooling method and equipment of the present invention.

Figure 13 is a perspective view of a counterflow heat exchanger.

Fig. 14 is a perspective view showing an example of a heat exchanger combining counterflow and crossflow.

Fig. 15 is a perspective view showing another example of a straight cross-flow heat exchanger.

Fig. 16 is an explanatory diagram showing an example of a method and equipment for dehumidifying and cooling gas according to the present invention.

Fig. 17 is an explanatory diagram showing another example of the method and equipment for dehumidifying and cooling gas according to the present invention.

Fig. 18 is an explanatory diagram showing still another example of the method and equipment for dehumidifying and cooling gas according to the present invention.

Fig. 19 is a block diagram showing an embodiment of a cooling device for a refrigerator according to the present invention.

Fig. 20 is a perspective view showing an embodiment of the cooling device of the refrigerator of the present invention.

Fig. 21 is a block diagram showing another embodiment of the cooling device of the refrigerator of the present invention.

The best form for carrying out the invention

In the invention described in claim 1 of the present invention, a mist of a volatile liquid is added to a gas flow A to make it saturated, and to become a gas flow Aa in which a large amount of mist-like fine liquid droplets M are suspended, and the gas flow Aa The flow Aa is passed into one flow channel of the heat exchanger with multiple flow channels and the fluid B to be cooled is passed into the other flow channel. During the gas flow Aa passing through the flow channel of the heat exchanger, the following The sensible heat of the fluid B is given to the gas flow Aa so that the temperature of the gas flow Aa rises and the saturation of the gas phase part (the relative humidity when the volatile liquid is water) decreases, so that a large number of fine droplets suspended in the gas flow Aa M is vaporized, and the temperature of the gas flow Aa is continuously lowered by its heat of vaporization, thereby continuously cooling the fluid B. The function of the gas flow Aa in which a large number of fine liquid droplets M are suspended is to lean against the flow channel of the heat exchanger. The sensible heat exchange with the fluid B is heated, and the gasification heat is taken away by the vaporization of the fine liquid droplets M, and the temperature of the gas flow Aa is lowered to cool the fluid B.

first embodiment

The flat plate 1 made of aluminum or other metal sheets or polyester or other synthetic resin sheets and the corrugated plate 2 with a wavelength of 3.0 mm and a wave height of 1.6 mm are alternately overlapped and contacted with each other, and the corrugated direction of the corrugated plate 2 is orthogonally overlapped step by step, A straight cross-flow heat exchanger as shown in FIG. 2 is obtained. In addition, forming small irregularities by shot blasting or the like on the surface of the thin plate imparts hydrophilicity and increases the surface area. In order to make the aluminum sheet hydrophilic, dip the sheet in an aqueous solution of sodium phosphate, sodium hypochlorite, chromic acid, phosphoric acid, oxalic acid, sodium hydroxide, etc., or dip it in boiling water for a short time, etc., on the surface of the aluminum sheet produce hydrophilic substances. In this way, if the surface of the thin plate is made hydrophilic, then when the fluid B is air or other gases, it is possible to prevent the deterioration of the gas circulation in the small through holes due to the pressure drop caused by water droplets.

Although a combination of the flat plate 1 and the corrugated plate 2 is shown as an example of the cross-flow heat exchanger 3, if fine corrugations are formed on a part of the flat plate, the surface area will be further increased and the heat exchange efficiency will be improved. In addition, if the surface of the flat plate 1 or the corrugated plate 2 is blackened, the radiation and absorption of radiant heat increase, and the heat exchange efficiency improves.

As shown in Fig. 2 and Fig. 3, the small through-hole group 4 on one side of the straight cross-flow heat exchanger 3 is arranged substantially vertically, and the small through-hole group 5 on the other side is arranged substantially horizontally, as shown in Fig. 3, the conduits 8a, 8b are respectively installed at the inlet 4a and the outlet 4b of the small through hole group 4, the air blower Fa and the water sprayer 6 are installed on the conduit 8a, and the conduits 9a, 9b are respectively installed on the small through holes. At the inflow port 5a and the outflow port 5b of the hole group 5 (FIG. 2), a blower F is attached to the duct 9a. Furthermore, Va in the figure is a valve for adjusting the spraying amount of the water sprayer 6 .

As the water sprayer 6, preferably the water droplets as fine as possible can be evenly distributed, such as air spray nozzles and the like are applicable. In addition, although the diameter of the water droplets is as thin as possible, it is best to have a diameter of about 10 μm. However, in the case of spraying with an air spray nozzle, if the maximum diameter of the water droplets is about 280 μm, about 70% of the water droplets have a diameter of less than 100 μm. The effect of the invention.

Furthermore, the air spray nozzle sprays with water and air, and if the water and air are still pressurized, the sprayed water droplets become smaller. In particular, the size of sprayed water droplets is easily affected by air pressure, and it is preferable to apply a pressure of 3kgf/cm2 ^or more. In addition, nozzles using only liquids can also be used.

Next, the action of this cooling device will be described. As shown in Figure 3, by using the above-mentioned water sprayer 6 in the external air or indoor air flow A, a large number of fine water droplets are sprayed into the air flow A, and the temperature is lowered by the heat of vaporization of the water droplets, and the relative humidity is increased. . Then, the air flow Aa in a state in which a large number of fine water droplets M are suspended is sent to one of the plurality of flow channel inlets 4a of the heat exchanger 3 by the discharge pressure of the blower Fa.

If the high-temperature air flow B is sent into the inlet 5a of the heat exchanger 3 with the other blower F, the air flow Aa will be taken away by the partition wall 1 (refer to FIG. 2 ) of the flow path while passing through the flow path of the heat exchanger 3. Sensible heat of the high-temperature air flow B, the temperature of the air flow Aa rises. As a result, the relative humidity of the air flow Aa decreases, a large number of fine water droplets M contained in the air flow Aa vaporize, the heat of vaporization reduces the humidity of the air flow Aa, and the high-temperature air flow B passes through the partition wall 1 to cool down.

The cooling principle of the cooling device will be further described in detail. The vapor pressure of the liquid in the droplet state is higher than that of the liquid with a horizontal liquid surface, and the smaller the diameter of the droplet, the higher the vapor pressure. This phenomenon can be expressed as a Kelvin formula as follows.

10g(pr/p)=20δM/ρrRT

where p is the vapor pressure at the horizontal liquid surface, Pr is the vapor pressure of a droplet of radius r, M is the molar mass, δ is the surface tension, ρ is the liquid density, R is the gas constant, and T is the absolute temperature.

Therefore, the smaller the radius of the water droplet, the faster the gasification and the stronger the cooling effect. Furthermore, during the vaporization process of the sprayed water droplet M in the heat exchanger 3, the diameter of the water droplet M becomes smaller, and since the vapor pressure increases along with the smaller diameter of the water droplet M, the water droplet M in the heat exchanger 3 Gasification proceeds at an accelerated rate. In other words, the fine water M vaporizes in a very short time in the heat exchanger 3, taking away a large amount of heat of vaporization.

If the above formula is used to calculate, in the case of water at 18°C, when the radius of the water droplet is 1μ, the vapor pressure will increase by 0.1% compared with the state when the liquid surface is flat, and when the radius of the water droplet is 10mμ, the vapor pressure will increase by about 10%. . Furthermore, when the radius of the water droplet is 1 mμ, the vapor pressure almost doubles. When the air in which the fine water droplets M are suspended in this amount is sent into the heat exchanger 3 , the water droplets M are rapidly vaporized in the heat exchanger 3 .

Experiments were carried out using this cooling device. As shown in Fig. 4, the air flow A having a temperature of 25.9°C, an absolute humidity of 8.05g/kg, and a relative humidity of 39% is passed through the water sprayer 6, and the temperature is lowered to 17.5°C, while a large amount of fine water droplets M are suspended. The air flow Aa with a relative humidity of 100% is sent into the inlet 4a of the small through-hole group 4 arranged almost vertically in the heat exchanger 3 at a wind speed of 2 m/sec. On the other hand, the high-temperature air B with a temperature of 70.6°C, an absolute humidity of 10.44g/kg, and a relative humidity of 5.2% is sent by the blower F at a wind speed of 2m/s into the inlet of the small through-hole group arranged almost horizontally in the heat exchanger 3 5a. Even if the group of small through holes 4 is not exactly vertical, water droplets can be sent through in a suspended state in the air. FIG. 5 is an air curve diagram showing the air cooling at this time, and Table 1 shows the test results.

Table 1 (with sprayer)

Sensible heat exchange is performed between the high-temperature air flow B and the air flow Aa, and the temperature of the air flow Aa is continuously lowered by vaporization of the fine water droplets suspended in the air flow Aa as described above, cooling the air flow B, and the air flow B The temperature is lowered without increasing the absolute humidity, and the comfortable air with a temperature of 18.6°C, an absolute humidity of 10.44g/kg, and a relative humidity of 78% is used as the air supply SA. The gas flow Aa passes through the heat exchanger 3 to become an air flow Ab having a temperature of 30.7° C. and a relative humidity of 100%, and this air flow Ab is discharged into the atmosphere.

The sensible heat exchange efficiency η ₁ in this case is 97.9% as shown in the formula (1) in Table 1, indicating that the heat exchange efficiency is very high. In formula (1), B, SA, and Aa represent respective air temperatures. In this case, the spray volume of the water droplets M is about 8-15 liters per hour. The flow rate of the air streams A and B in this case is about 180 m ³ /hour. The size of the heat exchanger is the area of 0.25m×0.25m=0.0625m ² , since the surface areas of the inlets 4a and 5a are 0.0625m ² and the opening ratio is about 40%, the cross-sectional area of the small through hole is 0.0625m2. m ² ×40%=0.025m ² , since the wind speed is 2m/sec, the air volume is 0.025m ² ×2m/sec=180m ³ /hour.

In order to compare with this, as a comparative example, the test results of the same direct cross-flow heat exchanger used in the first embodiment without using a water sprayer in the cooling air flow are shown in Figure 6 and Table 2 and Figure 7 in the air graph.

Table 2 (without sprayer)

In formula (2), B, Ba, and A represent respective air temperatures. The air flow A at a temperature of 22.3°C becomes the air flow Ab at a temperature of 62.0°C due to sensible heat exchange, and the high-temperature air flow B at a temperature of 67.2°C becomes an air flow Ba at a temperature of 36.0°C due to sensible heat exchange. Absolute humidity does not change in air flow A, air flow B. The sensible heat exchange efficiency _η1 at this time was 69.5% as shown by the formula (2) in Table 2. The sensible heat exchange efficiency is 97.9% in the case of spraying water, and 69.5% in the case of not spraying water, and the heat exchange efficiency is increased by about 30% by spraying water. Other conditions in this case are the same as those in the case of spraying water in the first embodiment.

2nd embodiment.

In addition, the cooling device is also used, as shown in Figure 8, the air with a temperature of 25.7°C, an absolute humidity of 12.20g/kg, and a relative humidity of 59.0% is made into an air stream A of 2m/s in the wind bundle, and it is passed through the water sprayer 6 Make a temperature of 20.2° C., a relative humidity of 100%, and make a large amount of mist-like fine water droplets uniformly suspended air flow Aa, and send the air flow Aa to the inlet 4a of the small through hole group 4 of the heat exchanger. On the other hand, as the air that needs to be cooled, the high-temperature air with a temperature of 34.2°C, an absolute humidity of 14.41g/kg, and a relative humidity of 43% is made into an air flow B of a wind speed of 2m/second, and sent into the small through-hole group 5 of the heat exchanger. Entrance 5a. Sensible heat exchange is performed between the high-temperature air flow B and the air flow Aa, and the air flow B becomes the cooling air SA having a temperature of 20.6° C., an absolute humidity of 14.41 g/kg, and a relative humidity of 95%. The gas flow Aa becomes an air flow Ab having a temperature of 25° C. and a relative humidity of almost 100%, and the air flow Ab is discharged into the atmosphere. The air curve at this time is shown in FIG. 9 , and the test results are shown in Table 3.

Table 3 (with sprayer)

As shown in the figure, the vaporization heat of water droplets in the gas flow Aa is transferred to the air flow B through the partition, as shown in the air curve diagram, the absolute humidity of the gas flow B remains unchanged, and the temperature decreases along the horizontal line of the air curve diagram to reach point SA (20.6°C), the air flow Aa passes the line with a relative humidity of 100%, and the temperature rises to point Ab. The sensible heat exchange efficiency in this case is 97.1% as shown in the formula (3) in Table 3, which is almost the same as the sensible heat exchange efficiency of the first embodiment. That is, when the temperature of the fluid B drops, if the temperature of the supply air SA becomes 20.6°C, which is suitable for air conditioning, the amount of sprayed water can be reduced. The spray volume of water is about 8 liters/hour.

3rd embodiment

As shown in FIG. 1, a water tank D for receiving water droplets discharged simultaneously with the air flow Ab is added to the equipment in FIG. 10. The electric valve Va and the water level regulating device are the water level float Vs, the water level sensor Se, the electric valve Vb, and the spray volume regulating device of the water droplet spraying device 6, namely the thermocouple Ta, the thermocouple Tb, the electrical signal amplifier C, and the electric valve Va. Components with the same reference numerals as those in FIG. 3 are the same as the components described in FIG. 3 in the first embodiment, so their explanations are omitted.

Install the water guide pipe 10 that returns the water in the water tank D to the water sprayer 6, and set the pump P and the electric valve Va in the middle. In addition, install the water supply pipe 11 on the water tank D, float the water level float Vs on the water surface 13 in the water tank D, and connect the on-off solenoid valve Vb set in the water supply pipe 11 with the water level sensor Se, as shown in Figure 1. The Q part is enlarged As shown in the figure, the water level float Vs and the water level sensor Se detect the change of the water level. If the water level drops to 13L, the solenoid valve Vb opens to supply water. If the water level rises to 13H, the solenoid valve Vb closes to stop the water supply.

A temperature sensor such as a thermocouple Ta of the gas stream A is arranged upstream of the water sprayer 6, a temperature sensor such as a thermocouple Tb is arranged in the fluid B, and an electric signal amplifier C is connected between the thermocouples Ta and Tb. Detect the temperature difference between the two thermocouples Ta, Tb and send it to the electrical signal amplifier. As the temperature difference becomes larger, the electric valve Va is operated to increase the amount of water spray, and as the temperature difference becomes smaller, the amount of water spray is reduced. . If necessary, the power of the blower Fa is increased to accelerate the air flow Aa simultaneously with the increase in the amount of sprayed water.

In this case, if the amount of spray from the water sprayer 6 is too much, the fine water droplets gather on the inner wall surface of the small through hole group 4 of the heat exchanger 3 to become a water flow, and cannot be fully vaporized, but drip. The water flow has an extremely small surface area compared with the fine water droplets, and when heat is taken away from the high-temperature air flow B, the vaporization of the water is reduced and does not contribute to cooling. Therefore, since the temperature of the gas stream Aa cannot be sufficiently lowered, the temperature of the high-temperature air stream B cannot be sufficiently lowered. If it is sprayed so that the fine water droplets M in the gas flow Aa contain the required amount uniformly, the cooling efficiency will be high and water can be saved.

4th embodiment

Also can use volatile organic liquids such as ethanol (78.3 ℃ of boiling points), methyl acetate (56.3 ℃ of boiling points), methyl alcohol (64.7 ℃ of boiling points) or the mixed liquid of volatile organic liquids and water, replace the water ( boiling point 100°C).

As shown in Figure 2, on the two surfaces of the partition wall 1 made of an aluminum sheet with a thickness of 25 μ and the aluminum corrugated plate 2 with a wavelength of 3.4 mm and a wave height of 1.7 mm, the microparticles of the heat-absorbing agent silica gel are dispersed and bonded, and they are Stacked alternately to obtain a straight cross-flow heat exchanger 3 with a size of 250mm×250mm×250mm. Using this heat exchanger 3, the cooling equipment shown in FIG. 10 was assembled, and the data when the water used in the nebulizer 6 in the first and second examples were replaced with a 45% aqueous solution of methanol is shown in FIG. 10 . In this case, since methanol aqueous solution is used instead of water, its boiling point is lowered, and the air flow A having a temperature of 25.9° C. is lowered to 14.6° C. after the methanol aqueous solution is sprayed (air flow Aa).

Low-temperature air SA of 17.2° C. is obtained by heat exchange between 14.6° C. of the air flow Aa and 51.3° C. of the high-temperature air flow B. Thus, if a liquid with a lower boiling point is sprayed than sprayed with water alone, low-temperature air SA can be obtained. The air graph in FIG. 11 is an air graph showing the state transitions of the above air flow B→SA and air flow A→Aa→Ab.

fifth embodiment

The equipment of this embodiment is as shown in Fig. 12, is to add the device that the gas flow Ab discharged from the outlet 4b of the heat exchanger 3 to the high-humidity gas flow Aa flow is added to the equipment described in the first embodiment. A humidifier 7 is provided on the upstream side of the water sprayer 6 . In Fig. 12, the outlet 4b of the heat exchanger 3 is connected to the air blower Fc with a conduit 8e, and the air blower Fc is connected with the flow path of the high-humidity gas flow Aa with a conduit 8d, and a part of the conduit 8e is connected to send air as required. Into the branch pipe K of the outside air OA.

In the humidifier 7, a valve V is installed in the middle of the water supply pipe Wp, and water can be supplied when humidification is required. As the humidifier 7, for example, an ultrasonic type, a water-soaked multilayer woven cloth, etc. are used.

The gas stream Aa is passed through the heat exchanger 3, and the exhaust gas Ab from the outlet 4b is refluxed by the blower Fc to be used as the gas stream Ac. This gas stream Ac is made into a gas stream Aa in which a large amount of fine water droplets M are suspended by the nebulizer 6 through the humidifier 7 as needed, and is circulated to the heat exchanger 3 .

In Fig. 12, a cooling part Co is set in the middle of the duct 8e, and a plurality of fins Fe are installed on the outer circumference of the duct 8e. Wind shields are installed on these fins and a blower Fd is connected, and the fins Fe are cooled by the blower Fd. The fluid Ab in the conduit 8e cools the moisture in the high-humidity fluid Ab to make it condense, and accumulates the dew in the water tank Da, and the water in the water tank is often discharged by the valve Vc, and returns to the sprayer 6.

Although the fluid cooling method of the present invention has been described as an example of an air cooling method using a straight cross-flow heat exchanger, it goes without saying that it can be similarly implemented for cooling of gases other than air, water, or other liquids.

As the heat exchanger used, an oblique cross-flow type, a counter-flow type shown in FIG. 13 , and a combination of a counter-flow and cross-flow type shown in FIG. 14 may be used instead of the above-mentioned straight cross-flow type. In the counter-flow heat exchanger shown in Figure 13 and the combined counter-flow and cross-flow heat exchanger shown in Figure 14, the gas flow Aa and fluid B that suspend the fine water droplets pass through the small through holes in the direction of the arrow in the figure. Inside, they are discharged as gas flow Ab and fluid SA respectively, and sensible heat exchange is performed between the two fluids Aa and B. In addition, as shown in Figure 15, a straight cross heat exchanger composed of a plurality of spacers 12, 12... between the plates 1, 1... along the vertical direction of each level can be used. In addition, A heat exchanger of a counter-flow type, a combination of counter-flow and cross-flow can be used as in the honeycomb laminate described above.

sixth embodiment

As shown in FIG. 16 , a straight cross-flow heat exchanger 3 of 250 mm×250 mm×250 mm and a spray humidifier 6 are arranged, and a dehumidification rotor 14 is arranged in the preceding stage of the heat exchanger 3 . The dehumidifying rotor 14 is made into a cylindrical shape with a diameter of 320mm and a width of 200mm by combining the honeycomb composite of adsorbent or moisture absorbent. In addition, the dehumidification rotor 14 is divided into an adsorption area 16 and a regeneration area 17 by the partitions 15, 15', and the flow paths are respectively formed by conduits (not shown) as shown by arrows B→HA→SA. The dehumidification rotor 14 is separated by 16 Rotation per hour is driven continuously in the direction of the arrow in the figure. The outside air OA with a temperature of 34.0° C., an absolute humidity of 14.4 g/kg and a relative humidity of 43.1% is made into an air flow B by the blower Fb, and sent to the adsorption area 16 of the dehumidification rotor 14 at a wind speed of 2 m/s.

Thereby, the moisture of the air flow B is adsorbed and removed, and the dry air flow HA is obtained. Next, the dry air flow HA is sent into the inlet 5a of the small horizontal through-hole group 5 of the heat exchanger 3 . In the regeneration zone 17 of the dehumidification rotor 14, the outside air OA is turned into regeneration air RA heated to about 80°C by the heater H, which is sent in along the direction of the arrow in the figure, and the dehumidification rotor 14 is dehumidified and regenerated through the regeneration zone 17. Exhaust as humid exhaust EA to the outside air.

On the other hand, when the temperature of the airflow A is 26°C and the relative humidity is 58%, humidification is performed by the mist humidifier 6 so that the relative humidity is 100%, and the temperature of the airflow Aa becomes 17.0°C. Further, water is sprayed into the air flow Aa to make numerous fine water droplets suspended, and sent to the inflow port 4a of the heat exchanger 3 .

The above-mentioned dry air HA passes through the heat exchanger 3, thereby exchanging sensible heat with the air flow Aa in which numerous fine water droplets are suspended. As in the description of the first embodiment, inside the heat exchanger 3, the heat exchange between the fine water droplets of the air flow Aa is carried out. The heat of vaporization is cooled to become a comfortable supply air SA with a temperature of 20.5° C., an absolute humidity of 4.5 g/kg, and a relative humidity of 30%.

It can be seen from this embodiment that the outside air at 34°C, absolute humidity 14.4g/kg, and relative humidity 43.1% is dehumidified, and the temperature is increased by the heat of adsorption of moisture, while the dry air with reduced humidity passes through the heat exchanger 3, thereby This gives cooled dry air at a temperature of 20.5° C., an absolute humidity of 4.5 g/kg, and a relative humidity of 30%. When this air is used for air conditioning, it can be properly humidified to create a comfortable air condition.

As a dehumidifier, in addition to the rotary type used in this embodiment, it is certainly possible to use a double-tube type, a cylindrical type, or a Kathabar type (made by Kathabar Corporation of the United States: make the lithium chloride solution drip in the container, and at the same time A dehumidifier such as a device that makes air flow through the window on one side of the container and absorbs the moisture in the air on the lithium chloride solution).

Seventh embodiment

In this embodiment, the process of dehumidifying by the dehumidification rotor after cooling the high-temperature air at 70.0° C. by the heat exchanger is described.

As shown in FIG. 17 , the spray humidifier 6 is arranged on the upper side of the straight cross-flow heat exchanger, and the dehumidification rotor 14 is arranged at the subsequent stage of the heat exchanger 3 . Water is sprayed in the spray humidifier 6 through the blower Fa to the outside air OA with a temperature of 26.6°C, an absolute humidity of 12.2g/kg, and a relative humidity of 58%. When the relative humidity is 100%, the temperature becomes 17.5°C. Water is sprayed thereinto, and the air flow Aa in which a large amount of water droplets are suspended passes through the flow channel 4a of the heat exchanger 3 side.

On the other hand, the air flow B with a temperature of 70.0° C., an absolute humidity of 14.4 g/kg, and a relative humidity of 7% is sent into the inlet 5a of the heat exchanger 3 by the blower Fb at a wind speed of 2 m/sec. The air flow B undergoes sensible heat exchange in the heat exchanger to become a low-temperature air flow Ba. The absolute humidity of the air flow Ba is almost the same as that of the air flow B. After passing through the heat exchanger 3, the air flow Aa becomes an air flow Ab with a temperature of 30.0°C and a relative temperature of about 100% at the outlet of the heat exchanger 3, and is discharged to the outside air. The dehumidification rotor 14 is rotationally driven in the direction of the arrow in the figure at 16 rpm.

The above-mentioned cooled air flow Ba is sent to the adsorption zone 16 of the dehumidification rotor 14, and the moisture is removed by adsorption to obtain a dry air flow HA with a temperature of 55° C., an absolute humidity of 4.5 g/kg, and a relative humidity of 5%. The operation of the dehumidification rotor 14 is as described in the fifth embodiment. Although it is extremely difficult to dehumidify by adsorption from high-temperature air, as shown in this example, if a dehumidifier is used after cooling with a heat exchanger, dehumidification can be easily and effectively obtained, and cooled dry air can be obtained.

Eighth embodiment

The air flow HA obtained in the seventh embodiment has a temperature of 55.0° C. and a relative humidity of 5%, which is too high in temperature and too low in relative humidity for general air conditioning. Therefore, in this embodiment, the air flow HA is further passed through the heat exchanger 3b in order to obtain the supply air SA having a temperature and humidity suitable for air conditioning.

As shown in FIG. 18, the high-temperature air flow B is passed through the straight cross flow heat exchanger 3a and the dehumidification rotor 14 similarly to the seventh embodiment to obtain the air flow HA. Since the operation up to this point is completely the same as that of the seventh embodiment, repeated description is omitted. The second straight cross-flow heat exchanger 3b is arranged in the rear stage of the dehumidification rotor 14, that is, in the flow path of the air HA flowing out from the outlet of the process air, in the flow channel 4 on one side of the second heat exchanger 3b The spray humidifier 6b is provided on the upstream side as in the seventh embodiment described above. Since the function of the second heat exchanger 3b is the same as that of the heat exchanger 3 of the seventh embodiment described above, description thereof will be omitted.

On the other hand, the dry air HA passing through the adsorption area 16 of the dehumidification rotor 14 is sent into the flow channel inlet 5a of the small through hole group 5 arranged horizontally in the heat exchanger 3b, and is mixed with the air flow that contains a large amount of fine water droplets and cooled. Aa performs sensible heat exchange to obtain a comfortable supply air SA with a temperature of 20.5° C., an absolute humidity of 4.5 g/kg, and a relative humidity of 30%. If the amount of water sprayed into the air flow Aa is increased or decreased when adjusting the air state of the air supply SA, the temperature of the air supply SA can be changed. On the other hand, if the humidity of the air supply SA is too low, if the dehumidification rotor Since the dehumidification performance of the dehumidification rotor 14 is lowered at the regeneration temperature, the humidity of the supply air SA can be increased, and comfortable air conditioning can be performed freely.

In the above 6th to 8th embodiments, if a liquid with a low boiling point, such as ethanol, methyl acetate, methanol, etc., is sprayed into the air flow Aa to replace the water used in the spray humidifier, the supply air can be further reduced. The temperature of stream SA.

Also, in all embodiments, an ultrasonic atomizing device can be used as the atomizing mechanism. Furthermore, as the water sprayer, in addition to the air spray nozzle, a single fluid nozzle that does not use air can be used. Furthermore, although in the above embodiments, the relative humidity is made 100% with the first-stage spray humidifier, and at the same time, it is made to suspend a large amount of water particles, but the spray humidifier can also be set to multi-stage, and the primary humidification To make the relative humidity 100%, and to suspend a large amount of fine particles of water in the secondary stage. What is important is that the air in the state where water fine particles with a diameter of about 10 μ are suspended in a large amount in the air with a relative humidity of 100% passes through the heat exchanger.

Although in the above embodiments, the corrugated plate and the flat plate are alternately laminated as a heat exchanger, the present invention is not limited to these, as long as there are multiple flow channels, the surface area of the flow channels is large, for example What is necessary is to provide flow passages with a plurality of heat exchanging fins at both ends of the heat pipe.

9th embodiment

In Fig. 19, 18 is a known refrigerator with a compressor (not shown) inside. Reference numeral 19 denotes a heat exchanger, one flow channel 20 of which is in the shape of a serpentine tube, and the other flow channel 21 is in the shape of a sleeve surrounding the serpentine tube-shaped flow channel 20 .

In the flow passage 20 on one side of the heat exchanger 19, high-temperature Freon gas (chlorofluorocarbons: a trademark of DuPont, U.S.) or other refrigerants from the compressor flow through, and on the other side of the heat exchanger 19 Cooling water flows through the flow channel 21.

The other flow path 21 of the heat exchanger 19 is connected to one flow path of the straight cross-flow heat exchanger 3 via a pipe line 22 , and a circulation pump 23 is provided in the middle of the line line 22 . That is, cooling water circulates between the heat exchanger 19 and the cross-flow heat exchanger 3 in a sealed state. Furthermore, 9a, 9b are chambers.

Fa is a blower, the suction side is open to the atmosphere, and the discharge side is combined with the upper end of the chamber 24 . In addition, the lower end of the chamber 24 is connected to the other flow path inlet 4 a of the straight cross-flow heat exchanger 3 . Furthermore, the other channel outlet of the straight cross-flow heat exchanger 3 is opened to the atmosphere.

The spray device 6 is installed in the chamber 24, and while the relative humidity of the air in the chamber 20 is made into 100%, it is further made into a state in which a large amount of fine water droplets are suspended, that is, mist. As the spray device 6, an air spray nozzle is used, and a water booster pump P and a compressor 25 are connected.

D is a water receiving tank, which is arranged under the straight cross-flow heat exchanger 3, and it is provided with a drain pipe 26.

As shown in Figure 20, the axes of the small through-hole group 4 on one side of the straight cross-flow heat exchanger 3 are arranged almost vertically, and the axes of the other small through-hole group 5 are arranged almost horizontally. A chamber 24 is installed on the inflow port 4a of 4, and a blower Fa and a water sprayer 6 are installed on the chamber 24. In addition, chambers 9a, 9b are attached to the inlet 5a and outlet 5b of the group of small through holes 5, respectively, and pipes 22 are connected to the chambers 9a, 9b.

The operation of the above configuration will be described below. First, the cooling mechanism using the straight cross-flow heat exchanger 3 will be described. The blower Fa is operated to form an air flow A, and water is sprayed thereinto by a water sprayer 6 to form a gas flow Aa. The amount of water sprayed exceeds the amount vaporized due to spraying. Then, a part of the sprayed water droplets is vaporized, and the heat of vaporization is deprived by the vaporization, so that the temperature of the gas flow Aa sent in the chamber 24 is lowered. In addition, the air in the chamber 24 , that is, the gas flow Aa, has a relative humidity of 100%, and a large amount of fine particles of water are suspended in the air, that is, in a mist state.

Then, the air in which a large number of fine water droplets are suspended enters one of the small through-hole groups 4 of the straight cross-flow heat exchanger 3 . When the refrigerator 18 is in the operating state, the temperature of the refrigerant sent through one flow path 20 of the heat exchanger 19 becomes high, and heat exchange is performed with the water sent through the other flow path 21 of the heat exchanger 19 . .

The water conveyed in the flow channel 21 on the other side of the heat exchanger 19 is circulated by the pump 23, and enters the small through hole group 5 on the other side of the straight cross-flow heat exchanger 3 through the pipe 22 and the chamber 9a. Then, sensible heat exchange is performed between the small through hole group 4 on one side and the small through hole group 5 on the other side via the partition wall 1 . That is, the cooling water passing through the other group of small through holes 5 is cooled by the gas flow Aa passing through the one group of small through holes 4 , while being heated by the gas flow Aa passing through the one group of small through holes 4 .

Then, the relative humidity of the gas flow Aa passing through one of the small through hole groups 4 becomes 100% or less, and a large amount of water particles contained therein are vaporized, and the heat of vaporization is taken away to cool the gas flow Aa.

Thus, the temperature of the gas flow Aa passing through one small through hole group 4 is kept at a constant low temperature state, so the cooling water passing through the other small through hole group 5 is distributed throughout the small through hole group 5a of the heat exchanger 3. It is cooled continuously in the area and over the entire length, and its temperature is kept almost constant.

In this case, if the amount of spraying from the water spraying device 6 is too much, the fine water droplets gather and condense on the partition walls in the small through-hole group 4 of the straight cross-flow heat exchanger 3, and become large water droplets or water flows. The surface area of the water flow is extremely small compared with the fine water droplets, and the heat taken from the refrigerant cannot sufficiently lower the temperature of the gas flow Aa, so the temperature of the refrigerant cannot be sufficiently lowered. If it is sprayed so that there are slightly more fine water droplets in the uniformly contained gas flow Aa than the necessary minimum, the cooling efficiency is high and water can be saved.

Then, the unvaporized water droplets in the small through-hole group 4 of the straight cross-flow heat exchanger 3 accumulate in the water receiving tank D and are discharged from the water discharge pipe 26 . As mentioned above, since the amount of water sprayed from the water spray device 6 is almost equal to the amount vaporized in the small through-hole group 4 of the straight cross-flow heat exchanger 3, the amount of water accumulated in the water receiving tank D is very small, and even if it is completely discarded No problem either. Therefore, the water sprayed from the water sprayer 6 is not recycled, and algae and the like do not occur.

Although in the above embodiment, water is shown as the example of the cooled liquid, considering the freezing in winter, antifreezes such as ethylene glycol of 50% capacity level can also be added in the cooled water, in order to prevent the heat exchanger 19 or For the corrosion of straight cross-flow heat exchanger 3, it is also possible to consider adding an anti-corrosion agent.

10th embodiment

Another embodiment of a cooling device for a refrigerator is shown in FIG. 21 . The difference from the embodiment of Fig. 19 is as follows. That is to say, the ninth embodiment shown in Fig. 19 makes water pass through the small through hole group 5 on the other side of the straight cross-flow heat exchanger 3, but this embodiment makes the air flow from the blower F pass through the direct cross-flow heat exchanger 3. The other small through-hole group 5 of the cross-flow heat exchanger 3 .

That is, F is a blower combined with the inlet of the chamber 9a. The outlet of the chamber 9 a is connected to the inlet of the other small through-hole group 5 of the straight cross-flow heat exchanger 3 . The outlet 5b of the small through hole group 5 is connected with the inlet of the chamber 9b, and the outlet of the chamber 9b is connected with the radiator 28.

In addition, a piping 27 is provided so that the refrigerant coming out of the refrigerator 18 passes through the radiator 28 . In addition, the configuration other than the above-mentioned difference is the same as that of the ninth embodiment, so description thereof will be omitted.

In this embodiment, the air passes through the small through-hole group 5 on the other side of the straight cross-flow heat exchanger 3 by the blower F, and is cooled therebetween to reach the radiator 28 . The high-temperature refrigerant from the refrigerator 18 is sent into the radiator 28 through the pipeline 27 to dissipate the heat of the refrigerant. Air passing through the group of small through holes 5 is sent into the radiator 28 .

That is to say, the radiator 28 is cooled by the air flow cooled by the small through-hole group 5 on the other side of the straight cross-flow heat exchanger 3, and the efficiency is much improved compared with that directly cooled by outside air.

In the applicant's experiment, using the same straight cross-flow heat exchanger 3 shown in the ninth embodiment shown in Fig. The speed of second makes air flow in the small through-hole group 4 of straight cross-flow heat exchanger 3, sprays the water of 12 liters/hour flow with sprayer 6. Then, the temperature of the air entering the radiator 28 from the straight cross-flow heat exchanger 3 becomes 18.6° C., and the cooling effect of the refrigerant is extremely high.

In this embodiment, the cooling device of the refrigerator of the present invention can be installed before the radiator of the existing air conditioner, and the efficiency of the refrigerator of the existing air conditioner or refrigerator can be improved with simple construction.

Industrial Applicability

Because the present invention is constituted as described above, so its principle is to make the relative humidity be 100%, and then make the mist-like gas flow Aa that fine water droplets evenly suspend in a large number pass as the gas flow with a plurality of fluid passages for cooling. One flow channel of the heat exchanger allows the fluid B to be cooled, such as air or water, to pass through the other flow channel, so that the gas flow Aa suspended by fine water droplets contacts the fluid B through the partition wall, and the gas flow Aa is heated to reduce the gas flow. The relative humidity of Aa makes the fine water droplets evaporate, and cools the gas flow Aa by its heat of evaporation, and at the same time cools the fluid B through the next wall. degree. Or if the temperature difference between the gas flow Aa and the high-temperature air flow B increases, the amount of water spray is increased, then the fluid Aa strengthens the cooling degree of the high-temperature air flow in proportion to the temperature difference with the high-temperature air flow B, and the air flow B can be reduced. Cool down to an almost constant comfortable temperature. Furthermore, dry cooling air can be obtained easily by combining this cooling facility with a dehumidifier.

As described in the first embodiment, the spray humidifier 6 is arranged on the straight cross-flow heat exchanger 3, and the high-temperature air flow B is cooled by using the air flow Aa that suspends a large amount of fine water droplets as the cooling air flow Sensible heat exchange efficiency, exhibiting very high values of 97%-100%. Where the same straight cross-flow heat exchanger as used in the first example is used without the use of sprayers and humidifiers in the cooling air stream, as demonstrated in the first example as a comparative example, The sensible heat exchange efficiency was 63%, showing that the heat exchange efficiency in the fluid cooling of the present invention is remarkably high.

Furthermore, the energy consumption required for this heat exchange is about 250 W for the operation of the air blower. On the contrary, the heat energy required for the cooling of the fluid B becomes, for example, 1.5 times to several tens of times the energy consumption, and this value varies with the fluid B. rises with increasing temperature.

The fluid cooling equipment is used for gas cooling, and a dehumidifier is added on it, as shown in the sixth to eighth embodiments, it can be used for dehumidification and cooling of gas, and can be used as an air conditioner. Since the operation cost in this case is significantly low as mentioned above, in the case of dehumidification and cold room in a closed room, for example, there is no need to recycle the indoor air, and fresh outside air can be continuously taken in to maintain dehumidification. Cold Room. Therefore, the increase of carbon dioxide or other harmful gases in the indoor air can be completely prevented, and a comfortable space can be provided.

Furthermore, there is no environmental problem because Freon is not used like conventional cold rooms, and since there is no need to use a compressor, there is no bacteria or mold that grows due to the hot air that exhausts heat, so it is also excellent in terms of sanitation.

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.

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