JPH09292187A - Method of cooling fluid, method of dehumidification and cooling of gas and device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To be able to supply a large quantity of low-cost cold blast by using water as the suspended fine particles of volatile liquid in gas flow and to be able to lower cooling temperature by using low boiling point liquid such as methanol as the fine particles of the volatile liquid. SOLUTION: Gas flow Aa that is saturated with the steam of water or other liquid and suspended with the large quantity of the fine particles of water or other liquid is blown into a group of small through holes 4 on a side of a cross-flow type or a counter-flow type heat exchanger 3, gas flow B that is to be cooled is blown through the other group of small through holes 5, sensible heat is exchanged between the gas flow Aa and the gas flow B, the fine particles of the volatile liquid suspended in the gas flow Aa is evaporated and the gas flow B is cooled by the evaporation.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a method and apparatus for cooling a fluid such as air and air or a liquid and a gas by heat exchange, and a method and apparatus for dehumidifying and cooling a gas such as air.

[0002]

2. Description of the Related Art Conventionally, refrigerators are generally used for cooling air or other gases or liquids, in which a volatile refrigerant such as Freon is compressed and liquefied by a compressor and cooled by the heat of vaporization of liquefied Freon. is there. Further, in such a refrigerator, in order to release the heat of compression of CFCs, a cooling tower is used, in which CFCs are passed through a flexible pipe, water is made to flow down in the flexible pipe, and air is caused to flow in the counter direction, and cooled by the heat of vaporization of the water. There is.

[0003]

In general air conditioning, it is required to obtain air of comfortable temperature and humidity, and when treating hot and humid outside air, both temperature and humidity can be lowered. is necessary. In the case of performing such air conditioning, chlorofluorocarbon is compressed by a compressor, which consumes a large amount of energy and poses a problem of depleting the ozone layer of the atmosphere due to chlorofluorocarbon. In addition, the cooling tower consumes a lot of energy.

The present invention is a method and apparatus for cooling a fluid such as air or other gas or liquid using a heat exchanger and its application to dehumidify and cool the gas such as air having a comfortable temperature and humidity, etc. low temperature·
It is intended to continuously supply a low-humidity gas with a small amount of energy without using Freon.

[0005]

The present invention uses a cross-flow type heat exchanger or other heat exchangers in which two kinds of fluids having different temperatures do not come into direct contact with each other, to reveal a low temperature gas A and a high temperature fluid B. When the high temperature fluid B is cooled by heat exchange, the low temperature gas A is saturated with water vapor or other volatile liquid vapor, and a large amount of fine water droplets or other volatile liquid droplets are uniformly dispersed therein. State, that is, a gas flow Aa in a state where a large amount of fine droplets are suspended in the gas, which is fed into one flow path of the heat exchanger, and the hot fluid B is fed into the other flow path. , The sensible heat of the fluid B evaporates the fine droplets M in the gas Aa through the heat exchanger, the heat of vaporization cools the gas Aa, and the cooled gas flow Aa
The fluid B is cooled with high efficiency by heat exchange between the fluid B and the fluid B.

[0006]

BEST MODE FOR CARRYING OUT THE INVENTION The invention according to claim 1 of the present invention is a gas in which a mist of a volatile liquid is added to a gas flow A to bring it into a saturated state and a large amount of fine mist-like droplets M are suspended. Flow Aa, the gas flow Aa is passed through one flow path of a heat exchanger having a plurality of flow paths, and the fluid B to be cooled is passed through the other flow path,
While the gas flow Aa passes through one flow path of the heat exchanger, the sensible heat of the fluid B is applied to the gas flow Aa to raise the temperature of the gas flow Aa and the saturation degree of the gas phase portion (when the volatile liquid is water). Is a relative humidity), a large amount of fine droplets M floating in the gas flow Aa are vaporized, and the heat of vaporization continuously lowers the temperature of the gas flow Aa to continuously cool the fluid B. And a gas flow A in which a large number of fine droplets M are suspended.
The gas flow Aa is heated by the sensible heat exchange with the fluid B in the flow path of the heat exchanger, and the vaporization heat is taken away by the vaporization of the fine droplets M, and the temperature of the gas flow Aa is lowered.
It has an effect of cooling the fluid B.

(Example 1) A flat plate 1 made of a sheet of aluminum or other metal or a sheet of polyester or other synthetic resin and a corrugated plate 2 having a wavelength of 3.0 mm and a wave height of 1.6 mm are alternately and corrugated. Of the cross flow type heat exchanger 3 as shown in FIG.
Get. If small irregularities are formed on the surface of the sheet by blasting or the like, hydrophilicity is generated and the surface area is increased. To impart hydrophilicity to the aluminum sheet, the aluminum sheet is immersed in an aqueous solution of sodium phosphate, sodium hypochlorite, chromic acid, phosphoric acid, oxalic acid, sodium hydroxide, or the like, or immersed in boiling water. Generate a hydrophilic substance on the surface. When hydrophilicity is given to the aluminum sheet in this way, even if the water droplets adhere to the surface of the aluminum sheet, the water droplets become flat, and the fluid resistance does not increase.

A flat plate 1 and a corrugated plate 2 as a cross flow type heat exchanger 3.
However, if a small wave is formed on a part of the flat plate, the surface area is further increased and the heat exchange efficiency is increased. Further, when the surface of the flat plate 1 or the corrugated plate 2 is made black, radiation and absorption of radiant heat increase, and heat exchange efficiency improves.

As shown in FIGS. 2 and 3, one small through hole group 4 of this cross flow type heat exchanger 3 is arranged substantially vertically and the other small through hole group 5 is arranged substantially horizontally, and FIG. As shown in FIG. 5, ducts 8a and 8 are provided at the inlet 4a and the outlet 4b of the small through hole group 4, respectively.
b, the blower Fa and the water atomizer 6 are attached to the duct 8a.
, The ducts 9a and 9b are attached to the inlet 5a and the outlet 5b of the small through hole group 5 (FIG. 2), and the blower F is attached to the duct 9a. In the figure, Va is a valve for adjusting the spray amount of the water sprayer 6.

As the water sprayer 6, a water sprayer capable of uniformly distributing water droplets as small as possible is desirable. For example, an air mist nozzle or the like is suitable. Further, it is desirable that the water droplets be as small as possible, and the diameter is preferably about 10 μm, but when sprayed using an air mist nozzle, the maximum diameter of the water droplets is 2
When it is set to about 80 μm, the diameter of about 70% of water droplets becomes 100 μm or less, and the effect of the present invention is sufficiently exhibited.

The air mist nozzle sprays using water and air, and spraying water and air reduces the sprayed water droplets. In particular, the size of the spray water droplet is easily affected by the pressure of air, and it is desirable to apply a pressure of 3 kgf / cm ² or more. In addition to the air mist nozzle, a nozzle that uses only liquid may be used.

Next, the operation of this cooling device will be described. FIG.
As shown in (1), a large amount of fine water droplets are sprayed on the air flow A using the water sprayer 6 on the outside air or the indoor air flow A, thereby lowering the temperature and increasing the relative humidity by the heat of vaporization of the water droplets. Further, a large amount of fine water droplets M are sent as air flows Aa in a floating state to one of the plurality of flow path inlets 4a of the heat exchanger 3 by the discharge pressure of the blower Fa.

On the other hand, if the hot air flow B is sent into the flow path inlet 5a of the heat exchanger 3 by the blower F, the partition wall 1 ( (See Figure 2)
, The sensible heat of the high-temperature air flow B is removed and the temperature of the air flow Aa rises. As a result, the relative humidity of the air flow Aa decreases, a large amount of fine water droplets M contained in the air flow Aa evaporate, and the temperature of the air flow Aa is reduced by the heat of vaporization, so that the high temperature air flow B passes through the partition wall 1. Cooling.

The cooling principle of this cooling device will be described in more detail. The vapor pressure of a liquid is higher in a droplet state than in a state in which the liquid has a horizontal surface, and increases as the diameter of the droplet decreases. This phenomenon is expressed as Kelvin's equation as follows.

Log (p _r / p) = 2δM / ρrRT where p is the vapor pressure of the horizontal surface, p _r is the vapor pressure of the droplet of radius r, M is the molar mass, δ is the surface tension, and ρ is the liquid. density,
R is a gas constant and T is an absolute temperature.

Therefore, the smaller the radius of the water droplet, the faster the vaporization and the stronger the cooling action. Further, in the process of vaporizing the sprayed water droplet M in the heat exchanger 3, the diameter of the water droplet M becomes smaller, and the vapor pressure increases as the diameter of the water droplet M becomes smaller. The vaporization of the water droplet M proceeds. That is, the fine water droplets M are vaporized in the heat exchanger 3 in a very short time, and take up a large amount of vaporization heat.

Calculating by applying the above equation, in the case of water at 18 ° C., when the radius of the water droplet becomes 1 μ, the vapor pressure increases by 0.1% as compared with the case where the water surface is flat, and the radius of the water droplet becomes 1
At 0 μm, the vapor pressure increases by about 10%. Further, when the radius of the water droplet becomes 1 μm, the vapor pressure increases almost twice. When the air in which a large amount of the fine water droplets M floats is sent to the heat exchanger 3, the water droplets M suddenly vaporize in the heat exchanger 3.

Tests were carried out using this cooling device. As shown in FIG. 4, an air flow A having a temperature of 25.9 ° C., an absolute humidity of 8.05 g / kg, and a relative humidity of 39% is passed through the water sprayer 6 to adjust the temperature to 1
An air flow Aa having a relative humidity of 100% in which a large amount of fine water droplets M are suspended is set to 7.5 ° C., and this air flow Aa is the inlet of the small through hole group 4 arranged substantially vertically in the heat exchanger 3. It is fed into 4a at a wind speed of 2 m / sec. Meanwhile, the temperature is 70.6
C., high humidity 10.44 g / kg, relative humidity 5.2% of the high temperature air flow B is blown by the blower F to the inlet 5a of the group of small holes arranged almost horizontally in the heat exchanger 3 at a wind speed of 2 m / sec. To enter. The small through hole group 4 does not have to be exactly vertical, but water droplets may be sent in a state of being suspended in the air. FIG. 5 is an air diagram showing the air cooling at this time, and Table 1 shows the test results.

[0019]

[Table 1] Sensible heat exchange is performed between the hot air flow B and the air flow Aa,
As described above, the temperature of the air flow Aa is continuously decreased by vaporizing the fine water droplets suspended in the air flow Aa, and the air flow B is cooled to decrease the temperature of the air flow B without increasing the absolute humidity. Comfortable air with a temperature of 0.6 ° C, an absolute humidity of 10.44 g / 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 reach the temperature 3
An air flow Ab with a temperature of 0.7 ° C. and a relative humidity of 100% is obtained. This air flow Ab is released into the atmosphere.

The sensible heat exchange efficiency η _{1 in} this case is 97.9% as shown in the equation (1) in Table 1, showing that the heat exchange efficiency is very high. In the formula (1), B, SA and Aa represent the temperature of each air. In this case, the spray amount of the water droplet M is about 1
8-15 liters per hour. Air flow A in this case
The flow rates of and B are about 180 m ³ / hour. The size of the heat exchanger is 0.25 × 0.25 = 0.0625 m ² , and the surface areas of its inlets 4a and 5a are 0.0625, respectively.
m ² , the open area ratio is about 40%, so the cross-sectional area of the small through holes is 0.
0625m ² × 40% = a 0.025 m ^2, air volume since the wind velocity is at 2m / sec 0.025 m ² × 2m / sec =
180m ³ / hour.

In order to compare with this, the test results in the case of using the same cross-flow heat exchanger as used in Example 1 as a control example and not using a water atomizer for the cooling air flow are shown in FIG. 6 and Table 2. And the psychrometric chart of FIG. 7. In the equation (2), B, Ba, and A each represent the temperature of air.

[0022]

[Table 2] Airflow A with a temperature of 22.3 ° C has a temperature of 62.0 due to sensible heat exchange.
℃ air flow Ab, high temperature air flow B 67.2 ℃ B
Becomes an air flow Ba having a temperature of 36.0 ° C. due to sensible heat exchange.
The absolute humidity is the same for both air flow A and air flow B. The sensible heat exchange efficiency η _{1 at} this time is 69.5% as shown in the equation (2) in Table 2. When water is sprayed, the sensible heat exchange efficiency is 97.9%, and when water is not sprayed, the sensible heat exchange efficiency is 69.5%, and spraying water increases the heat exchange efficiency by about 30%. In this case, other conditions are the same as in the case of spraying water in Example 1.

(Example 2) Similarly, using this cooling device, the temperature was 25.7 ° C. and the absolute humidity was 12.2 as shown in FIG.
Air of 0 g / kg and relative humidity of 59.0% was used as an air flow A with a wind speed of 2 m / sec, and this was passed through a water atomizer 6 to a temperature of 20.2.
An air flow Aa in which a large amount of fine mist-like water droplets having a temperature of 100 ° C. and a relative humidity of 100% is suspended uniformly is formed, and the air flow Aa is fed into the inlet 4a of the small through hole group 4 of the heat exchanger. On the other hand, the air to be cooled has a temperature of 34.2 ° C and an absolute humidity of 14.41 g /
High-temperature air having a relative humidity of 43% and kg is fed into the inlet 5a of the small through hole group 5 of the heat exchanger as an air flow B having a wind velocity of 2 m / sec.
The hot air flow B undergoes sensible heat exchange with the air flow Aa,
The air flow B became 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%,
The air flow Ab is released into the atmosphere. The air diagram at this time is shown in FIG. 9, and the test results are shown in Table 3.

[0024]

[Table 3] As shown in the figure, the heat of vaporization of the water droplets in the gas flow Aa is transferred to the gas flow B through the partition wall, the absolute humidity of the gas flow B does not change as shown in the air diagram, and the temperature along the horizontal line of the air diagram changes. After reaching the downward SA point (20.6 ° C.), the temperature of the air flow Aa rises up to the Ab point through the line of relative humidity of 100%. The sensible heat exchange efficiency in this case is 9 as shown in equation (3) in Table 3.
The value was 7.1%, which is almost the same as the sensible heat exchange efficiency of Example 1. That is, the temperature of the fluid B decreases and the temperature of the supply air SA increases by 2
When the temperature becomes 0.6 ° C., which is appropriate for air conditioning, the amount of water sprayed may be reduced to maintain the temperature. The amount of water sprayed in that case is about 8 liters / hour.

In order to compare with the above, as a control example, the same cross flow type heat exchanger as used in Example 1 was used and the test results when the water atomizer is not used for the cooling air flow are shown in FIG.
0, shown in the psychrometric chart of FIG. 11 and Table 4.

[0026]

[Table 4] 21.8 ° C air flow A becomes 32.7 ° C air flow Ab,
The hot air flow B of 34.4 ° C. becomes the air flow SA of 25.7 ° C. by sensible heat exchange with the air flow A. Absolute humidity is airflow A,
The air flow B does not change. The sensible heat exchange efficiency at this time is 69.0% as shown in the equation (4) in Table 4.

(Embodiment 3) As shown in FIG. 1, a water tank D for receiving water droplets discharged together with the air flow Ab in the apparatus of FIG. 3 explained in Embodiment 1, and a recirculation device for the water accumulated in the water tank D, that is, a pump P. , Water conduit 10, motor-operated valve Va and water level adjusting device or water level float Vs, water level sensor Se, motor valve Vb,
In addition, a spray amount adjusting device of the water droplet spraying device 6, that is, a thermocouple Ta, a thermocouple Tb, an electric signal amplifier C, and an electric valve Va are added. Parts in the figure that are assigned the same reference numerals as those in FIG. 3 are the same as the parts described in FIG.

A water conduit 10 for returning water in the water tank D to the water sprayer 6 is attached, and a pump P and a motor-operated valve Va are provided in the middle thereof. Further, a water supply pipe 11 is attached to the water tank D, a water level float Vs is floated on the water surface 13 in the water tank D, an on / off solenoid valve Vb provided in the water supply pipe 11 and a water level sensor Se are connected, and a part Q in FIG. 1 is enlarged. As shown in the figure, the change in water level is caught by the water level float Vs and the water level sensor Se, and the water surface reaches 13L.
Solenoid valve Vb opens and water is replenished when the temperature drops to 13H
If it goes up, the solenoid valve Vb is closed and the supply of water is stopped.

Upstream of the water sprayer 6, a temperature sensor such as a thermocouple Ta of the gas flow A and a temperature sensor such as a thermocouple Tb in the fluid B are arranged, and the thermocouples Ta and Tb are interposed by an electric signal amplifier C. connect. The temperature difference between the two thermocouples Ta and Tb is caught and put in the electric signal amplifier C, the electric valve Va is operated to increase the water spray amount as the temperature difference increases, and the water spray amount decreases as the temperature difference decreases. Reduce. If necessary, the output of the blower Fa is increased as the amount of sprayed water is increased to accelerate the air flow Aa.

In this case, when the amount of water sprayed from the water sprayer 6 is too large, fine water droplets collect on the inner wall surface of the small through hole group 4 of the heat exchanger 3 to form a water flow and drop without sufficient vaporization. I will end up. The water flow has an extremely small surface area as compared with the fine water droplets, and the amount of heat taken from the high-temperature air flow B causes less water vaporization and does not contribute to cooling. Therefore, the temperature of the gas flow Aa cannot be lowered sufficiently, and therefore the hot air flow B
The temperature cannot be lowered sufficiently. If the fine water droplets M in the gas flow Aa are sprayed so as to be uniformly contained in the required amount, the cooling efficiency is good and water can be saved.

Example 4 Instead of water (boiling point 100 ° C.) used in the sprayer 6, ethanol (boiling point 78.3) was used.
C.), methyl acetate (boiling point 56.3.degree. C.), methanol (boiling point 64.7.degree. C.), or a volatile organic liquid or a mixed liquid of volatile organic liquid and water can be used.

As shown in FIG. 2, fine particles of hygroscopic agent silica gel are sprinkled and adhered on both surfaces of the partition wall 1 made of an aluminum sheet having a thickness of 25 μ and the aluminum corrugated plate 2 having a wavelength of 3.4 mm and a wave height of 1.7 mm. 250mm x 25 by stacking alternately
A cross-flow heat exchanger 3 having a size of 0 mm × 250 mm is obtained.
FIG. 12 shows data when the cooling device shown in FIG. 12 was assembled using this heat exchanger 3 and a 45% aqueous solution of methanol was used in place of the water used for the sprayer 6 in Examples 1 and 2. In this case, since the aqueous methanol solution was used in place of water, the boiling point thereof decreased, and the temperature of the air stream A was 25.9 ° C. The air stream A was sprayed with the aqueous methanol solution (air stream A
a) The temperature dropped to 14.6 ° C.

By the heat exchange between the air flow Aa of 14.6 ° C. and the hot air flow B of 51.3 ° C., the low temperature air S of 17.2 ° C.
A was obtained. Therefore, low temperature air SA can be obtained by spraying using a liquid having a lower boiling point than spraying only water. FIG.
The air diagram of 1 is the above airflow B → SA and airflow A → A
It is a psychrometric chart which shows the state change of a-> Ab.

(Embodiment 5) As shown in FIG. 14, the apparatus of this embodiment is the same as the apparatus described in Embodiment 1 except that the outlet 4b of the heat exchanger 3 is used.
A humidifier 7 is provided on the upstream side of the water atomizer 6 by adding a device for returning the gas flow Ab discharged from the device to the high-humidity gas flow Aa. In FIG. 14, the outlet 4b of the heat exchanger 3 and the blower Fc are connected by the duct 8e, the blower Fc and the flow path of the high-humidity gas flow Aa are connected by the duct 8d, and the outside air OA is partly connected to the duct 8e. A branch duct K for connection is connected if necessary.

The humidifier 7 has a valve V in the middle of the water supply pipe Wp.
To be able to supply water should it need to be humidified. As the humidifier 7, for example, there is an ultrasonic type, a type using a large number of woven fabrics soaked with water, and the like.

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

In FIG. 12, a cooling unit Co is provided in the middle of the duct 8e, a large number of fins Fe are attached to the outer periphery of the duct 8e, a cover is attached to the cooling unit Co to connect the blower Fd, and the fins Fe are cooled by the blower Fd. The fluid Ab in the duct 8e is cooled, the moisture in the high humidity fluid Ab is cooled to cause dew condensation, and condensed water is stored in the tank Da, and the water in the tank is occasionally discharged by the valve Vc and returned to the sprayer 6.

Although the fluid cooling method of the present invention has been described with reference to the example of the air cooling method using the cross-flow heat exchanger, it can be similarly applied to the cooling of gas other than air or liquid such as water. Of course.

As the heat exchanger to be used, an oblique alternating current type, a counterflow type shown in FIG. 15, and a heat exchanger in which a counterflow and a crossflow shown in FIG. 16 are combined are used in place of the above-mentioned crossflow type. You can also In the counterflow type shown in FIG. 15 and in the heat exchanger in which the counterflow and the crossflow shown in FIG. 16 are combined, the gas flow Aa in which fine water droplets are suspended and the fluid B are respectively small in the direction of the arrow in the figure. After passing through the holes, they are discharged as a gas flow Ab and a fluid SA, respectively, and sensible heat exchange is performed between the fluids Aa and B. Also, as shown in FIG. 17, a large number of spacers 1 are provided between the flat plates 1, 1.
It is possible to use a cross-flow type heat exchanger assembled by sandwiching a large number of 2, 12, ... In each step in a direction orthogonal to each other. Also, as in the above honeycomb laminate, a counter-flow type, a counter-flow and a cross-flow are combined. A combined heat exchanger can also be used.

(Embodiment 6) 250 mm × as shown in FIG.
A 250 mm × 250 mm cross-flow heat exchanger 3 and a spray humidifier 6 are arranged, and a dehumidifying rotor 14 is arranged in front of the heat exchanger 3. The dehumidifying rotor 14 is formed by forming a honeycomb laminated body having an adsorbent or a hygroscopic agent bonded thereto into a cylindrical shape having a diameter of 320 mm and a width of 200 mm. Further, the dehumidifying rotor 14 is separated into an adsorption zone 16 and a regeneration zone 17 by separators 15 and 15 ′, and an arrow B → HA is provided by a duct (not shown).
→ The dehumidifying rotor 1 has a flow path as shown by SA.
4 is continuously rotated at 16 r.ph in the direction of the arrow in the figure. Temperature 34.0 ℃, absolute humidity 14.4g / kg, relative humidity 4
3.1% of outside air OA is changed into air flow B by the blower Fb,
This is performed at a wind speed of 2 m / sec in the adsorption zone 16 of the dehumidifying rotor 14.
Send to

As a result, the moisture of the air stream B is adsorbed and removed to obtain the dry air stream HA. Next, the dry air flow HA is fed into the inlet 5a of the horizontal small through-hole group 5 of the heat exchanger 3. The regeneration zone 17 of the dehumidifying rotor 14 is heated by the heater H to the outside air OA.
Is fed in the direction of the arrow in the figure as regeneration air RA heated to about 80 ° C., passes through the regeneration zone 17 to dehumidify and regenerate the dehumidifying rotor 14, and is discharged into the outside air as humid exhaust air EA.

On the other hand, the temperature of the air flow A is 26 ° C. and the relative humidity is 5
Humidification by spray humidifier 6 at 8% and relative humidity of 100
%, The temperature of the air stream Aa was 17.0 ° C.
Further, water is sprayed on the air flow Aa, and the water flow is sent to the inflow port 4a of the heat exchanger 3 in a state where countless fine water droplets float.

By passing through the heat exchanger 3, the above-mentioned dry air flow HA exchanges sensible heat with the air flow Aa in which a myriad of fine water droplets float, and inside the heat exchanger 3 as in the description of the first embodiment. It was cooled by the heat of vaporization of fine water droplets of the air flow Aa, and became a comfortable air supply SA with a temperature of 20.5 ° C, an absolute humidity of 4.5 g / kg and a relative humidity of 30%.

As can be seen from this example, the outside air having a temperature of 34 ° C., an absolute humidity of 14.4 g / kg and a relative humidity of 43.1% was dehumidified,
The temperature rises due to the heat of adsorption of moisture and the dry air whose humidity has decreased is passed through the heat exchanger 3 so that the temperature 2
Chilled dry air is obtained at 0.5 ° 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 appropriately humidified to provide comfortable air conditions.

As the dehumidifier, of course, in addition to the rotary type dehumidifier used in this embodiment, a dehumidifier such as a two-cylinder type, a cylinder type or a cassava type (manufactured by Kasaba USA) filled with a hygroscopic agent can be used. .

(Embodiment 7) In this embodiment, a process in which high temperature air at 70.0 ° C. is cooled by a heat exchanger and then dehumidified by a dehumidifying rotor will be described.

As shown in FIG. 19, the spray humidifier 6 is arranged on the upper side of the cross-flow heat exchanger 3 and the dehumidifying rotor 14 is arranged in the latter stage of the heat exchanger 3. Temperature 26.0 through blower Fa
OA, absolute humidity 12.2g / kg, relative humidity 58% outside air OA
When water is sprayed with a spray humidifier 6 to a relative humidity of 100%, the temperature rises to 17.5 ° C., and further water is sprayed onto the air flow Aa in which a large amount of fine particles of water are suspended in the heat exchanger 3. It passes through one flow path 4a.

On the other hand, the temperature is 70.0 ° C. and the absolute humidity is 14.4 g / k.
Air velocity B with g and 7% relative humidity is blown by blower Fb at 2
It is fed into the inlet 5a of the heat exchanger 3 at m / sec. The air flow B exchanges sensible heat with a 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 the air flow Aa has passed through the heat exchanger 3, the air flow Ab at the outlet of the heat exchanger 3 has a temperature of 30.0 ° C. and a relative humidity of about 100%.
Will be released into the open air. The dehumidifying rotor 14 is rotationally driven at 16 r.ph in the direction of the arrow in the figure.

The above-mentioned cooled air flow Ba is sent to the adsorption zone 16 of the dehumidifying rotor 14 to adsorb and remove the moisture to dry the air having a temperature of 55 ° C., an absolute humidity of 4.5 g / kg and a relative humidity of 5%. Get the flow HA. The operation of the dehumidifying rotor 14 is the fifth embodiment.
As described in the above. Dehumidification by adsorption method from high temperature air is extremely difficult, but effective dehumidification can be easily performed by using a dehumidifier after cooling with a heat exchanger as shown in this Example, and cooled dry air can be obtained. To be

(Example 8) Air flow H obtained in Example 7
A has a temperature of 55.0 ° C. and a relative humidity of 5%, and the temperature is too high and the relative humidity is too low for general air conditioning. Therefore, in this embodiment, this air flow HA is further passed through the heat exchanger 3b to obtain the supply air SA having a temperature and humidity suitable for air conditioning.

As shown in FIG. 20, the high temperature air flow B is passed through the cross flow type heat exchanger 3a and the dehumidification rotor 14 to obtain the air flow HA as in the seventh embodiment. The operation up to this point is exactly the same as that of the seventh embodiment, and thus the repeated description is omitted. Second
The cross-flow heat exchanger 3b is installed in the subsequent stage of the dehumidifying rotor 14, that is, in the flow path of the air flow HA flowing out from the outlet of the treated air.
The spray humidifier 6b is provided on the upstream side of the one flow path 4 of the second heat exchanger 3b as in the case of the above-described seventh embodiment. The operation of the second heat exchanger 3b is the same as that of the heat exchanger 3 of the seventh embodiment described above, and thus the description thereof is omitted.

On the other hand, the dry air flow HA passing through the adsorption zone 16 of the dehumidifying rotor 14 is fed to the flow path inlet 5a of the small through hole group 5 installed horizontally of the heat exchanger 3b, and contains a large amount of fine water droplets. Sensible heat exchange is performed with the cooled air flow Aa, and the temperature becomes 2
A comfortable air supply SA of 0.5 ° C, absolute humidity of 4.5 g / kg and relative humidity of 30% is obtained. When adjusting the air condition of the supply air SA, the temperature of the supply air SA can be changed by adjusting the amount of water sprayed in the air flow Aa, while when the humidity of the supply air SA is too low, the dehumidification rotor If the regeneration temperature is lowered, the dehumidifying performance of the dehumidifying rotor 14 is lowered, so that the humidity of the supply air Sa can be raised and free and comfortable air conditioning can be performed.

If a liquid having a low boiling point, such as ethanol, methyl acetate, or methanol, is sprayed onto the air stream Aa instead of the water used in the spray humidifier in the above Examples 6 to 8, the temperature of the supply air stream SA is further increased. Can be lowered.

Furthermore, an ultrasonic atomizing device can be used as the atomizing means in all the examples. In addition to the air mist nozzle, a one-fluid nozzle that does not use air can be used as the water sprayer. In the above embodiment, the relative humidity is set to 100% in one stage of the spray humidifier and a large amount of fine particles of water are suspended. However, a plurality of stages of the spray humidifier are provided and the relative humidity is set to 100% in the first stage. It may be humidified so that a large amount of fine particles of water may be suspended in the next stage. The point is that the air in which a large amount of fine particles of water having a diameter of about 10 μ are suspended in the air having a relative humidity of 100% may be passed through the heat exchanger.

In the above embodiments, as the heat exchanger, the one in which the corrugated plates and the flat plates are alternately laminated is illustrated, but the present invention is not limited to this, and the heat exchanger may have a plurality of flow paths and have a large surface area. Any material may be used, and for example, a heat pipe may be provided with flow paths having a large number of heat exchange fins at both ends.

[0056]

Since the present invention is configured as described above, the relative humidity 1 is provided in one flow path of a heat exchanger having a plurality of fluid passages.
A large amount of fine water droplets are uniformly and uniformly suspended in 00% air, and the atomized gas flow Aa is passed as a cooling gas flow, and the fluid B to be cooled, such as air or water, is passed through the other flow passage to form fine water droplets. The gas flow Aa and the fluid B in which the air is suspended are in contact with each other via a partition wall to heat the gas flow Aa, thereby lowering the relative humidity of the gas flow Aa and evaporating fine water droplets to cool the gas flow Aa by the heat of evaporation. This is the principle of cooling the fluid B via the partition wall, and its feature is that the degree of cooling the fluid B can be controlled by adjusting the amount of water spray in the water sprayer 6. Alternatively, as the temperature difference between the gas flow Aa and the hot air flow B increases, the amount of water spray increases, so that the fluid Aa strengthens the cooling degree of the hot air flow B in proportion to the temperature difference between the hot air flow B and the hot air flow B. , The airflow B can be cooled to a substantially constant comfortable temperature. Furthermore, by combining this cooling device and a dehumidifier, dry cooling air can be easily obtained.

Cross-flow heat exchanger 3 as described in Example 1
The sensible heat exchange efficiency is about 97% or more when the spray humidifier 6 is arranged in the air and the high temperature air flow B is cooled by using the air flow Aa in which a large amount of fine water droplets are suspended as the cooling air flow. showed that. When the same crossflow type heat exchanger as that used in Example 1 was used and a sprayer and a humidifier were not used for the cooling air flow, the sensible heat exchange efficiency was as shown in Comparative Example 1 in Example 1. It is 63%, which shows that the efficiency of heat exchange in cooling the fluid of the present invention is remarkably high.

The energy consumption required for this heat exchange is about 250 W of operating energy of the blower, whereas the heat energy required for cooling the fluid B is, for example, 1.5 times to several tens of times the energy consumption, This value increases as the temperature of the fluid B increases.

This fluid cooling device can be used for cooling a gas, and a dehumidifier can be added to this to be used for dehumidifying and cooling a gas as shown in Examples 6 to 8, and used as an air conditioner. be able to. In this case, the operating cost becomes extremely low as described above. For example, when used for dehumidifying and cooling in a closed room, it is not necessary to repeatedly circulate the indoor air to continuously use fresh outside air to perform dehumidifying and cooling. I can continue. Therefore, an increase in carbon dioxide and other harmful gases in the indoor air can be suppressed, and a comfortable space can be provided.

Furthermore, since there is no need to use CFC as in conventional cooling, there is no environmental problem, and there is no need to use a compressor to generate bacteria or mold due to the hot air of the exhaust heat. Also has an extremely excellent effect.

[0061]

[Brief description of drawings]

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

FIG. 2 is a perspective view showing an example of a 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 apparatus of the present invention.

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

5 is a psychrometric chart showing data for cooling the fluid shown in FIG.

FIG. 6 is an explanatory diagram showing a comparative example of a method and an apparatus for cooling a fluid.

7 is a psychrometric chart showing data for cooling the fluid shown in FIG.

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

9 is a psychrometric chart showing cooling data for the fluid shown in FIG. 8. FIG.

FIG. 10 is an explanatory diagram showing heat exchange data of a control example.

FIG. 11 is a psychrometric chart showing heat exchange data of a control example.

FIG. 12 is an explanatory diagram showing data of cooling using an aqueous methanol solution.

FIG. 13 is a psychrometric chart showing data of cooling using an aqueous methanol solution.

FIG. 14 is an explanatory diagram showing still another example of the fluid cooling method and apparatus of the present invention.

FIG. 15 is a perspective view of a counterflow heat exchanger.

FIG. 16 is a perspective view showing an example of a heat exchanger in which a counter flow and a cross flow are combined.

FIG. 17 is a perspective view showing another example of a cross-flow heat exchanger.

FIG. 18 is an explanatory view showing another example of the method and apparatus for dehumidifying and cooling gas according to the present invention.

FIG. 19 is an explanatory view showing another example of the method and apparatus for dehumidifying and cooling gas according to the present invention.

FIG. 20 is an explanatory view showing still another example of the method and apparatus for dehumidifying and cooling gas according to the present invention.

[Explanation of symbols]

 1 flat plate 2 corrugated plate 3 cross flow type heat exchanger 6 atomizer 7 humidifier 14 dehumidification rotor Aa supersaturated gas flow B fluid to be cooled D water tank

Claims (26)

[Claims] 1. A heat exchanger having a plurality of flow paths, wherein the gas flow A is a gas flow Aa containing a vapor of a volatile liquid in a saturated state and a large amount of atomized fine droplets M are suspended. The sensible heat of the fluid B is added to the gas flow Aa while passing the gas flow Aa through one flow path and the fluid B to be cooled through the other flow path, and passing the gas flow Aa through one flow path of the heat exchanger. To raise the temperature of the gas flow Aa, vaporize a large amount of fine droplets M suspended in the gas flow Aa, and continuously lower the temperature of the gas flow Aa by the heat of vaporization of the droplets Aa and the fluid B. A method of cooling a fluid, characterized in that the fluid B is continuously cooled by heat exchange. 2. The method of cooling a fluid according to claim 1, wherein the floating amount of the fine droplets M in the gas flow Aa is changed according to the change in the difference between the temperature of the gas flow Aa and the temperature of the fluid B. . 3. The cooling of the fluid according to claim 1, wherein the flow velocity of the gas flow Aa in which the fine droplets M are suspended is changed according to the change in the difference between the temperature of the gas flow Aa and the temperature of the fluid B. Method. 4. A gas flow in which a gas flow A is a gas flow saturated with a vapor of a volatile liquid, and a mist of the volatile liquid is added to the gas flow to suspend a large amount of fine droplets M. The fluid cooling method according to claim 1, wherein the fluid cooling method is Aa. 5. The gas flow Ab containing the volatile liquid vapor discharged from the outlet of one passage of the heat exchanger is returned to the inlet side of the one passage of the heat exchanger, and a mist of the volatile liquid is added thereto. 5. The method of cooling a fluid according to claim 1, wherein the fine liquid droplets M are suspended in a gas flow Aa and are used while being circulated. 6. The volatile liquid is water, a volatile organic liquid or a mixed liquid of a volatile organic liquid and water.
To the fluid cooling method according to claim 5. 7. The method for cooling a fluid according to claim 1, wherein the volatile liquid is sprayed by a gas-liquid mixing type nozzle. 8. The method for cooling a fluid according to claim 1, wherein the diameter of the sprayed droplets is 280 μm or less. 9. A heat exchanger having a plurality of flow paths, which is a gas flow Aa in which a mist of a volatile liquid is added to a gas flow A to make it saturated and in which a large amount of fine mist-like droplets M are suspended. The gas flow Aa is passed through one of the flow paths, and the dry gas flow B that has been dehumidified by a dehumidifier is passed through the other flow path, while the gas flow Aa passes through one flow path of the heat exchanger. A sensible heat of the gas flow B is applied to Aa to raise the temperature of the gas flow Aa,
The fine droplets M floating in a are vaporized, and the temperature of the gas flow Aa is continuously lowered by the heat of vaporization thereof, and the gas flow B is cooled by heat exchange between the gas flow Aa and the gas flow B, and the dried A method for dehumidifying and cooling a gas, which comprises continuously supplying the gas. 10. A heat exchanger having a plurality of flow paths, which is a gas flow Aa in which a mist of a volatile liquid is added to the gas flow A to make it saturated and a large amount of fine mist-like droplets M are suspended. The gas flow Aa is passed through one flow path and the gas flow B is passed through the other flow path, and sensible heat of the gas flow B is applied to the gas flow Aa while the gas flow Aa passes through the flow path of the heat exchanger. The temperature of the gas flow Aa is raised, the fine liquid droplets M suspended in the gas flow Aa are vaporized, and the temperature is continuously lowered by the heat of vaporization thereof, and the gas is exchanged by the heat exchange between the gas flow Aa and the gas flow B. A method for dehumidifying and cooling gas, characterized in that the stream B is cooled, and then the cooled gas stream Ba is passed through a dehumidifier to dehumidify and continuously supply the cooled dry gas. 11. A heat exchanger having two or more heat exchangers having a plurality of flow paths and a dehumidifying means are used, and a mist of a volatile liquid is added to a gas flow A passing through the two heat exchangers to form a saturated state and a mist state. A gas flow Aa in which a large amount of fine droplets M are suspended is formed, and the gas flow Aa is fed into one flow path of each of the two heat exchangers, and the other flow of the first heat exchanger is supplied. The gas flow B is sequentially passed through the passage, the dehumidifying means, and the other flow path of the second heat exchanger, and the gas flow Aa is
While passing through the first flow path of the heat exchanger, the sensible heat of the gas stream B and the high temperature dry gas stream HA after dehumidifying by the dehumidifying means is given to the gas stream Aa to raise the temperature of the gas stream Aa, Fine droplets M suspended in the gas flow Aa are converted into high temperature gas flows B and HA.
Is vaporized by the sensible heat of the dry gas SA at a low temperature to continuously lower the temperature of the gas flow Aa.
A method for dehumidifying and cooling a gas, characterized in that the gas is continuously supplied. 12. A gas flow A by means of atomizing a volatile liquid.
A mist of a volatile liquid is added to form a gas flow Aa in which a large amount of fine mist-like droplets M in a saturated state are suspended, and the gas is supplied to one flow path of a heat exchanger having a plurality of flow paths. The fluid B to be cooled is passed through the flow passage Aa and the other flow passage, and while the gas flow Aa passes through one flow passage of the heat exchanger, the gas flow Aa is changed to the fluid B.
The sensible heat of the fluid B is taken away, and a large amount of fine droplets M floating in the gas flow Aa are vaporized, and the heat of vaporization continuously lowers the temperature of the gas flow Aa to continuously cool the fluid B. A fluid cooling device characterized by: 13. A fluid cooling apparatus according to claim 12, further comprising means for introducing volatile liquid vapor upstream of the volatile liquid atomizing means. 14. The cooling gas flow Aa is circulated by providing a duct and a blower for guiding the gas flow Ab discharged from one outlet of the heat exchanger to one inlet side of the heat exchanger. Fluid cooling system. 15. A cross flow type, diagonal flow type or counter flow type heat exchanger comprising a honeycomb laminate in which flat plates and corrugated plates are alternately stacked, or a combination of counter flow and cross flow. 15. The fluid cooling device according to claim 12, which is a heat exchanger. 16. A cross-flow type, a diagonal flow type or a counter-flow type heat exchanger in which sheets are stacked through a large number of spacers, or a heat exchanger in which a counter flow and a cross flow are combined. 15. The cooling device for fluid according to claim 12, wherein 17. The fluid cooling device according to claim 12, wherein the surface of the heat exchange element has hydrophilicity. 18. The fluid cooling device according to claim 15 or 16, wherein fine particles are fixed to the wall surface of the flow path of the heat exchanger. 19. The fine particles are fine particles of an adsorbent.
8. The cooling device for a fluid according to item 8. 20. A gas flow A by means of atomizing a volatile liquid.
A mist of a volatile liquid is added to form a gas flow Aa in which a large amount of fine mist-like droplets M in a saturated state are suspended, and the gas is supplied to one flow path of a heat exchanger having a plurality of flow paths. A high temperature gas flow B to be cooled is passed through the flow passage Aa and the other flow passage, and the gas flow Aa is passed while the gas flow Aa passes through one flow passage of the heat exchanger.
Removes the sensible heat of the gas flow B, vaporizes a large amount of fine droplets M floating in the gas flow Aa, and the heat of vaporization continuously lowers the temperature of the gas flow Aa to continuously cool the high temperature gas flow B. A dehumidifying and cooling device for gas, characterized in that a dehumidifying means is provided upstream of the heat exchanger for the high temperature gas flow so as to be cooled. 21. A gas flow A by means of atomizing a volatile liquid.
A mist of a volatile liquid is added to form a gas flow Aa in which a large amount of fine mist-like droplets M in a saturated state are suspended, and the gas is supplied to one flow path of a heat exchanger having a plurality of flow paths. A high temperature gas flow B to be cooled is passed through the flow passage Aa and the other flow passage, and the gas flow Aa is passed while the gas flow Aa passes through one flow passage of the heat exchanger.
Deprives the sensible heat of the high temperature gas flow B, and a large amount of fine droplets M floating in the gas flow Aa are vaporized and the heat of vaporization causes the gas flow A to flow.
A device for dehumidifying and cooling gas, characterized in that the temperature of a is continuously lowered to continuously cool the hot gas flow B, and a dehumidifying means is provided downstream of the heat exchanger for the hot gas flow. . 22. A gas flow A by means of atomizing a volatile liquid.
A mist of a volatile liquid is added to form a gas flow Aa in which a large amount of fine mist-like droplets M in a saturated state are suspended, and the gas is supplied to one flow path of a heat exchanger having a plurality of flow paths. A high temperature gas flow B to be cooled is passed through the flow passage Aa and the other flow passage, and the gas flow Aa is passed while the gas flow Aa passes through one flow passage of the heat exchanger.
Deprives the sensible heat of the high temperature gas flow B, and a large amount of fine droplets M floating in the gas flow Aa are vaporized and the heat of vaporization causes the gas flow A to flow.
Two gas cooling means for continuously cooling the high temperature gas flow B by continuously lowering the temperature of a are provided, and a dehumidifying means is provided in the flow of the cooled gas flow B between the both cooling means. A gas dehumidifying and cooling device. 23. The dehumidifying and cooling device for a gas according to claim 20, wherein a means for introducing the volatile liquid vapor is provided on the upstream side of the volatile liquid atomizer. 24. A cooling gas flow Aa is circulated by providing a duct and a blower for guiding the gas flow Ab discharged from one outlet of the heat exchanger to one inlet side of the heat exchanger. The gas dehumidifying and cooling device according to claim 22. 25. A heat exchanger of a cross flow type, a diagonal flow type or a counter flow type comprising a honeycomb laminated body in which flat plates and corrugated plates are alternately stacked, or a combination of a counter flow and a cross flow. 25. The gas dehumidifying and cooling device according to claim 20, which is a heat exchanger. 26. A cross-flow type, diagonal flow type or counter-flow type heat exchanger in which sheets are stacked through a large number of spacers, or a heat exchanger in which a counter flow and a cross flow are combined. The dehumidifying and cooling device for gas according to any one of claims 20 to 24.