JP2009008343A - Indirect evaporative cooler capable of optimizing sensible heat exchange - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an indirect evaporative cooler capable of suppressing energy consumption by adjusting an optimum ratio of F<SB>A</SB>to F<SB>B</SB>according to a state of air. <P>SOLUTION: This indirect evaporative cooler is characterized by comprising: a cooling part 1 lowering a dry bulb temperature of passing air by utilizing heat of evaporation; a cooling object part 2 adjoining the cooling part 1 by a sensibly-heat-exchangeable bulkhead, and lowering the dry bulb temperature of passing air by executing sensible heat exchange with the cooling part 1; a flow rate ratio regulation means 4 regulating a flow rate ratio of the air sent to the cooling part 1 and the cooling object part 2; an air condition detection part 5 detecting information required for calculating specific enthalpy of air sent to the cooling part 1 and the cooling object part 2; and a control means 100 controlling the operation of the flow rate ratio regulation means 4 to increase efficiency of the sensible heat exchange between the cooling part 1 and the cooling object part 2 based on the information detected by the air condition detection part 5. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to an indirect vaporizer used in an air conditioning system or the like. In particular, it relates to energy saving control of an indirect vaporizer.

  Ozone-depleting substances such as specified CFCs (CFC, HCFC, etc.) are obliged to phase out production according to the Montreal Protocol from the viewpoint of ozone layer protection. On the other hand, 3 gases (HFC, PFC, SF6) such as chlorofluorocarbons, which have been developed as substitutes for specific chlorofluorocarbons and have no fear of destruction of the ozone layer, are used as refrigerants (air conditioners, air conditioners for automobiles, etc.) due to their excellent characteristics. In the future, as the conversion from ozone-depleting substances becomes full-fledged, their usage and emissions are expected to increase. However, these three gases are compounds that exist stably in the atmosphere for a long period of time and exhibit a very strong greenhouse effect. Therefore, in the Kyoto Protocol, additional measures have been taken for three gases such as CFC substitutes. There is a strong demand to promote the development, dissemination and introduction of substances and equipment that have a smaller greenhouse effect and must strive to significantly reduce emissions.

  In such an environment, there is an indirect evaporative cooler that performs air conditioning without using three gases such as alternative chlorofluorocarbon (for example, Patent Document 1). The indirect evaporative cooler is separated from the wet flow path by a wet flow path that absorbs the heat of vaporization from the passing gas by a non-woven fabric or the like, and by a partition wall that can exchange sensible heat. It is mainly comprised by the dry flow path which lowers the temperature of the gas which passes by carrying out sensible heat exchange between, and the ventilation means which ventilates gas to a wet flow path and a dry flow path. Then, when the water retained in the wet flow path evaporates, the sensible heat of the air passing through the wet flow path is taken away, and the sensible heat exchange is performed between the wet flow path and the dry flow path, thereby causing the dry flow. The air in the road is cooled. At this time, the absolute humidity of air does not increase at the inlet and outlet of the dry flow path.

Patent publication2005-513392

  Here, a case where air in a certain state (state “0” in FIG. 1) is introduced into both the dry flow path and the wet flow path of the indirect evaporative cooler is considered. In this case, the air introduced into the wet flow path is deprived of the heat of vaporization when the water retained in the wet flow path is vaporized, and theoretically once becomes the state of “A1” in FIG. . Next, the air in the wet flow path is heat-exchanged with the dry flow path, so that the evaporation of water is promoted while the temperature rises. Then, the state of air ideally shifts to the state “A2” in the upper right direction on the saturation curve.

  On the other hand, in the dry flow path, the temperature is lowered from the state of “0” to the state of “B2” with the absolute humidity being constant by taking heat from the wet flow path.

In FIG. 1, when the air in the “0” state is cooled in the dry flow path and cooled to the state “B2”, if the specific enthalpy deprived in the dry flow path is Δh _B , it is deprived in the dry flow path. The enthalpy H _B is calculated by H _B = Δh _B × F _B (where F _B is the flow rate of air passing through the dry flow path). Similarly, when the specific enthalpy robbed wet channel and the Delta] h _A, the enthalpy H _A rob wet passage, is _{H A = Δh A × F A} ( where F _A of air passing through the wet passage flow rate )It can be expressed as. According to the energy conservation law, H _A = H _B , and therefore Δh _A × F _A = Δh _B × F _B.

Therefore, it can be expressed as F _A : F _B = Δh _B : Δh _A.

Since Δh _A can ideally increase to Δh _{A (ideal)} , F _A can be reduced.

  However, the conventional indirect evaporative cooler mostly has a fixed air flow rate, and since excess air is sent to the wet flow path, the power of the blowing means is wasted accordingly. There was a problem.

The optimum ratio of F _A and F _B changes based on the state change of the air supplied to the dry flow path and the wet flow path, but the conventional one has the optimum ratio of F _A and F _B according to this change. The ratio was not adjusted.

Therefore, an object of the present invention is to provide an indirect evaporative cooler that can suppress energy consumption by adjusting the optimum ratio of F _A and F _B according to the state of air.

  In order to achieve the above object, the indirect evaporative cooler of the present invention is adjacent to the cooling unit by a cooling unit that lowers the dry bulb temperature of air that passes through the heat of vaporization, and a partition wall that can exchange sensible heat, An indirect evaporative cooler having a cooled part that lowers the dry bulb temperature of air passing through sensible heat exchange with the cooling part, wherein the air blown to the cooled part and the cooled part A flow ratio adjusting means for adjusting a flow ratio of the air, an air condition detector for detecting information necessary for calculating a specific enthalpy of air blown to the cooling part and the cooled part, and the air condition detector Control means for controlling the operation of the flow rate adjusting means so as to increase the efficiency of sensible heat exchange between the cooling part and the cooled part based on the information detected by And

In this case, the control means may be configured such that the cooling unit when the efficiency of sensible heat exchange between the cooling unit and the cooled unit is increased based on the information detected by the air condition detecting unit. The specific enthalpy Δh _A taken from the part and the specific enthalpy Δh _B taken by the cooled part by the cooled part are calculated, and the flow rate F _{A of} air passing through the cooled part and the flow rate of air passing through the cooled part The operation of the flow rate ratio adjusting means may be controlled so that the ratio of F _B is F _A : F _B = Δh _B : Δh _A.

  Further, another indirect vaporizer of the present invention includes a cooling unit that lowers the dry bulb temperature of air that passes through the use of heat of vaporization, the cooling unit adjacent to the cooling unit by a partition wall that can exchange sensible heat, and the cooling unit An indirect evaporative cooler having a cooled portion that lowers the dry bulb temperature of air passing through sensible heat exchange, and a blowing means that blows air to the cooling portion and the cooled portion, Flow rate ratio adjusting means for adjusting a flow rate ratio of air blown to the cooling part and the cooled part, and information necessary for calculating a specific enthalpy of air blown to the cooling part and the cooled part. An air state detection unit to detect, an air volume detection unit for detecting a flow rate of one or both of the air flowing into the cooling unit and the cooled part, and information detected by the air state detection unit and the air volume detection unit Based on the cooling section and Serial characterized by comprising a control means for controlling the operation of the flow rate adjusting means and the blower means as the efficiency of the sensible heat exchanger is increased between the object to be cooled.

In this case, the control means may be configured such that the cooling unit when the efficiency of sensible heat exchange between the cooling unit and the cooled unit is increased based on the information detected by the air condition detecting unit. The specific enthalpy Δh _A taken from the part and the specific enthalpy Δh _B taken by the cooled part by the cooled part are calculated, and the air flow rate F _B passing through the cooled part is constant and the air passing through the cooled part The operation of the flow rate ratio adjusting means and the blower means is controlled so that the ratio of the flow rate F _A of the air and the flow rate F _B of the air passing through the cooled part is F _A : F _B = Δh _B : Δh _A It ’s fine.

  Further, another indirect vaporization cooler of the present invention includes a cooling unit that lowers a dry bulb temperature of air that passes through vaporization heat, and a cooling wall that is adjacent to the cooling unit by a partition wall that can exchange sensible heat. A cooled portion that lowers the dry-bulb temperature of the air that passes through sensible heat exchange with the cooling portion, a cooling portion blowing means that blows air to the cooling portion, and a cooled portion that blows air to the cooled portion An indirect evaporative cooler having air blowing means, the air condition detecting unit detecting information necessary for calculating a specific enthalpy of air blown to the cooling unit and the cooled portion, and the cooling unit The efficiency of sensible heat exchange between the cooling unit and the cooled portion is increased based on the air volume detecting unit that detects the flow rate of the air blown by the blowing unit and the information detected by the air state detecting unit. Control for controlling the operation of the cooling unit blower Characterized by comprising a stage, a.

In this case, the control means may be configured such that the cooling unit when the efficiency of sensible heat exchange between the cooling unit and the cooled unit is increased based on the information detected by the air condition detecting unit. The specific enthalpy Δh _A taken from the part and the specific enthalpy Δh _B taken by the cooled part by the cooled part are calculated, and the flow rate F _{A of} air passing through the cooled part and the flow rate of air passing through the cooled part the ratio of F _{B is, F a: F B = Δh} B: may be controlling operation of the cooling unit blower means so that Delta] h _a.

  In addition, the cooling unit described above holds water in the interior and removes heat of vaporization from the passing air, and is adjacent to the wet flow path by a partition wall that can exchange sensible heat, and between the wet flow path. And a dry flow path that lowers the temperature of the air passing through the sensible heat exchange and supplies the air to the wet flow path.

  Moreover, the air condition detection unit described above can be configured by dry bulb temperature detection means for detecting the dry bulb temperature of air and humidity detection means for detecting the humidity of air.

Further, the control means described above has a dry bulb temperature of the air blown to the cooling unit as θ _0D , a wet bulb temperature as θ _0W , an absolute humidity as x ₀ , and a dry bulb temperature arrival rate of the cooling unit as K _A numerical set between 0 and 1 according to the characteristics and usage of the indirect evaporative cooling device), according to the characteristics and usage of the wet bulb arrival rate of the cooled portion K _{B (the} indirect evaporative cooling unit 0 to 3), Y% relative humidity of the air exhausted by the cooling unit (a value set between 70 and 100% depending on the characteristics and usage of the indirect vaporizer) Then, the specific enthalpy h _A deprived from the cooled part by the cooling unit, the dry bulb temperature of the air exhausted by the cooling unit is θ _0D − (1−K _A ) (θ _0D −θ _0W ), and the relative humidity Specific enthalpy where the cooled part is taken away by the cooled part The _B, the dry-bulb temperature of the air cooled part is exhaust _{θ 0D -K B (θ 0D -θ} 0W), it can be absolute humidity calculated as a _{x 0.}

Further, the control means described above is configured so that the cooling section takes away from the cooled section when the dry bulb temperature of the air blown to the cooling section is θ _0D , the wet bulb temperature is θ _0W , and the absolute humidity is x _0. The enthalpy Δh _A is calculated on the assumption that the dry bulb temperature of the air exhausted by the cooling unit is θ _0D and the relative humidity is 100%, and the specific enthalpy Δh _B taken by the cooling unit by the cooling unit is calculated. It may be calculated assuming that the dry bulb temperature of the air exhausted by the cooling unit is θ _{0 W} and the absolute humidity is x ₀ .

Further, the control means described above has a specific enthalpy that the cooling unit takes away from the cooled portion when the dry bulb temperature of the air blown to the cooling unit is θ _{0 W} , the dew point temperature is θ _{0 dp} , and the absolute humidity is x _0. Δh _A is calculated on the assumption that the dry bulb temperature of the air exhausted by the cooling unit is θ _{0 W} and the relative humidity is 100%, and the specific enthalpy Δh _B taken by the cooling unit by the cooling unit is It may be calculated on the _assumption that the dry bulb temperature of the air exhausted by the section is θ _{0 dp} and the absolute humidity is x ₀ .

  Since the present invention adjusts the optimal ratio of the air volume supplied to the cooling part and the cooled part according to the air state, energy consumption can be suppressed.

  As shown in FIG. 2, the indirect vaporizer of the present invention is adjacent to the cooling unit 1 by a cooling unit 1 that lowers the dry bulb temperature of air that passes through vaporization heat, and a partition wall that can exchange sensible heat, Indirect vaporization comprising: a cooled portion 2 for lowering the dry bulb temperature of air passing through sensible heat exchange with the cooling portion 1; and a blowing means 3 for blowing air to the cooled portion 1 and the cooled portion 2. It is a cooler, the flow rate ratio adjusting means 4 for adjusting the flow rate ratio of the air blown to the cooling part 1 and the cooled part 2, and the specific enthalpy of the air blown to the cooling part 1 and the cooled part 2 is calculated. Based on the information detected by the air condition detector 5 and the air condition detector 5 that detects the information necessary to do so, the efficiency of sensible heat exchange between the cooling part 1 and the cooled part 2 is increased. And the control means 100 for controlling the operation of the flow rate ratio adjusting means 4.

  The cooling unit 1 has a tubular wet flow channel having a water retention capability made of a nonwoven fabric or the like that easily absorbs moisture on the inner surface. When air passes through the wet flow path, the water held in the nonwoven fabric is vaporized, and the heat of vaporization is taken away from the air, so that the temperature of the passing air can be lowered. In this case, it is theoretically possible to cool the air to the wet bulb temperature of the incoming air.

  Further, as shown in FIG. 3, the cooling unit 1 is adjacent to the wet flow channel 11 by holding a water inside and removing the heat of vaporization from the passing air and a partition wall capable of sensible heat exchange, A sensible heat exchange with the wet flow path 11 can be used to lower the temperature of the air passing therethrough and also include a dry flow path 12 that supplies the air to the wet flow path. In this case, it is theoretically possible to cool the air to the dew point temperature of the incoming air. The partition wall may have any thermal conductivity, but may be formed of a metal such as aluminum or copper.

  The portion to be cooled 2 is a tubular dry flow channel adjacent to the cooling portion 1 and is separated from the cooling portion 1 by a partition wall that can exchange sensible heat. The partition wall may be any material as long as it has good thermal conductivity, but can be formed of a metal such as aluminum or copper, for example. Thereby, since sensible heat exchange can be performed with the air passing through the cooling unit 1, the temperature can be lowered without increasing the absolute humidity of the air passing through the cooled part 2 (dry flow path). it can.

  In addition, if the flow path of the cooling part 1 and the flow path of the cooled part 2 are formed in a direction facing each other and the air flows in these two flow paths are opposed, the air can be efficiently cooled.

  The blowing means 3 may be anything as long as it can blow air to the cooling section 1 and the cooled section 2. For example, a fan capable of adjusting the air volume by controlling the frequency is used. Can be used. By providing this fan in the flow path connected to the cooling part 1 and the cooled part 2, air can be blown to both the cooling part 1 and the cooled part 2 with one fan. Further, the air blowing means 3 is electrically connected to the control means 100, and the amount of air blown is controlled by a command from the control means 100.

  The flow rate ratio adjusting unit 4 adjusts the flow rate ratio of the air blown by the air blowing unit 3 to the cooling unit 1 and the cooled unit 2. For example, at least one of the flow paths following the cooling unit 1 or the cooled unit 2. On the other hand, a damper that changes the flow rate of the air by adjusting the opening is preferably provided in the flow path following the cooling unit 1. Further, the flow rate adjusting means 4 is electrically connected to the control means 100, and the flow rate ratio of the air sent to the cooling part 1 and the cooled part 2 is controlled by a command from the control means 100.

  The air condition detection unit 5 may be any device that detects information necessary for calculating the specific enthalpy of the air blown to the cooling unit 1 and the cooled unit 2. For example, if any two values of dry bulb temperature, wet bulb temperature, dew point temperature, relative humidity, and absolute humidity can be detected, not only the specific enthalpy of air but also dry bulb temperature, wet bulb temperature, All of dew point temperature, relative humidity, and absolute humidity can be obtained. Accordingly, the air condition detection unit 5 detects dry bulb temperature detection means for detecting the dry bulb temperature of air, wet bulb temperature detection means for detecting the wet bulb temperature of air (for example, a wet bulb sensor), and detects the dew point temperature of air. Dew point temperature detecting means (for example, a dew point sensor) to be used, humidity detecting means for detecting the relative humidity or absolute humidity of air may be used. In particular, the combination of the dry bulb temperature detecting means and the humidity detecting means is simple.

  The dry bulb temperature detecting means detects the temperature of the air supplied by the air blowing means 3 to the cooling unit 1 and the cooled part 2, and for example, a thermocouple can be used. Further, the temperature detection means is electrically connected to the control means 100, and the detected information is transmitted to the control means 100.

  The humidity detecting means detects the relative humidity or absolute humidity of the air supplied from the air blowing means 3 to the cooling section 1 and the cooled section 2, and includes, for example, a polymer film humidity sensor, a ceramic humidity sensor, and an electrolyte humidity sensor. An electric hygrometer can be used. Further, the humidity detection means is electrically connected to the control means 100, and the detected information is transmitted to the control means 100.

  The control means 100 controls the operation of the flow rate ratio adjusting means 4 so that the efficiency of the sensible heat exchange between the cooling part 1 and the cooled part 2 is increased based on the information detected by the air condition detecting part 5. For example, a computer or the like can be used.

  Moreover, you may provide the air volume detection means, for example, a flowmeter etc. which detects the flow volume of any one or both of the air which flows in into the cooling part 1 and the to-be-cooled part 2. FIG. In this case, the air volume detection means is electrically connected to the control means 100, and the detected information is transmitted to the control means 100. Thereby, since the flow volume of the air which the ventilation means 3 blows can be controlled based on the information which the air volume detection means detected, the sensible heat exchange between the cooling part 1 and the to-be-cooled part 2 of the sensible heat exchange Efficiency can be improved, or the flow rate of the air to be cooled 2 can be made constant. In addition, as shown in FIG. 4, if the flow ratio characteristic curve according to the opening degree of the damper (flow rate ratio adjusting means 4) is stored in a database in advance, measurement of the flow rate of the air flowing into the cooling unit 1 becomes unnecessary. As a result, the number of parts as a device is reduced and the reliability is improved. Further, when the air blowing means 3 is a fan, as shown in FIG. 5, it is possible to predetermine the frequency of the fan depending on the opening degree of the damper (flow rate ratio adjusting means 4). As a result, the frequency of the fan can be detected and the air flow rate can be calculated from the detected frequency, which eliminates the need to measure the flow rate of the air flowing into the cooled portion 2 and further reduces the number of parts as a device. Can do.

  Next, an example of a method in which the control unit 100 controls the operations of the flow rate ratio adjusting unit 4 and the air blowing unit 3 based on information detected by the temperature detecting unit, the humidity detecting unit, and the air volume detecting unit will be described.

First, when sensible heat exchange is performed between the cooling unit 1 and the cooled part 2 via the partition wall, the specific enthalpy deprived by the cooling part 1 is Δh _A , and the specific enthalpy deprived by the cooled part 2 is Δh _B , If the flow rate of air in the cooling unit 1 is F _A and the flow rate of air in the cooled part 2 is F _B ,
Δh _A × F _A = Δh _B × F _B
Holds. From now on, the flow ratio is
F _A : F _B = Δh _{B B} : Δh _A
It becomes. That is, the flow rate ratio between the air flow rate F _A of the cooling unit 1 and the air flow rate F _B of the cooled portion 2 is determined by the values of Δh _A and Δh _B.

The specific enthalpy h of air is the constant pressure specific heat of dry air (0% humidity) C _pa (kJ / kg · K), the constant pressure specific heat of steam C _pw (kJ / kg · K), and the dry bulb temperature t (° C), evaporating heat of water at 0 ° C is r (kJ / kg), and absolute humidity is x (kg / kg (DA)).
h = C _pa · t + (C _pw · t + r) · x
It can be expressed as. Here, the constant pressure specific heat C _{pa of} dry air, the constant pressure specific heat C _{pw of} water vapor, and the evaporation heat r of water at 0 ° C. are constants. Therefore, if the dry bulb temperature and absolute humidity of the air are known, the specific enthalpy h of the air Can be requested.

The values of the specific enthalpy Δh _A taken by the cooling unit 1 and the specific enthalpy Δh _B taken by the cooled portion 2 are the specific enthalpy of the air at the inlet of the cooling portion 1 as h _A0 , the specific enthalpy at the outlet as h _A2 , and the cooled portion If the specific enthalpy of air at the entrance of 2 is h _B0 and the specific enthalpy of the exit is h _B2 ,
Δh _A = h _A2 −h _A0
Δh _B = h _B0 -h _B2
It becomes.

That is, if the dry bulb temperature and the absolute humidity of the air flowing into the cooling unit 1 and the air discharged from the cooling unit 1 are determined, the specific enthalpy Δh _A deprived by the cooling unit 1 can be obtained and flows into the cooled unit 2 If the dry bulb temperature and the absolute humidity of the air and the air discharged from the cooling unit 1 are determined, the specific enthalpy Δh _B deprived by the cooled unit 2 can be obtained.

When the air condition is “0”, the dry bulb temperature is θ _0D (° C.), the relative humidity is φ ₀ (%), and the saturated water vapor pressure when the dry bulb temperature is θ _0D (° C.) is P _S ( KPa)
P _S = 101.325 × exp {11.97-3997.3 / (θ _0D +234)} Expression (1)

From the relative humidity φ ₀ (%), when the water vapor partial pressure in the state “0” is P ₀ (KPa),
φ ₀ = (P ₀ / P _S ) × 100 (2)
Than,
P ₀ = φ ₀ · P _S / 100 (3)

When the wet bulb temperature in state “0” is θ _{0 W} (° C.),
θ _0W = {38η−44.68 + 1245.5 / (η + 11.063) ・ ・ ・ Formula (4)
here,
η = ln {(P ₀ + 101.325 × θ _0D /1510)/101.325} (5)
Thereby, the wet bulb temperature in the state “0” can be calculated.

If the dew point temperature in state “0” is θ _0dp (° C.),
θ _0dp = [3997.6 / {11.97−ln (P ₀ /101.325)}−234] Equation (6)
Thereby, the dew point temperature in the state “0” can be calculated.

If the absolute humidity in the state “0” is x ₀ (kg / kg (DA)),
x ₀ = 0.622 × P ₀ /(101.325−P ₀ ) (7)
Thereby, the absolute humidity in the state “0” can be calculated.

Thus, by measuring the dry bulb temperature of a certain air state “0” by θ _0D (° C.) and the relative humidity φ ₀ (%) by the equations (1) to (7), the wet bulb temperature θ _{0 W} (° C.), dew point temperature θ _{0 dp} (° C.), and absolute humidity x ₀ (kg / kg (DA)) can be calculated.

Further, the values of the air diagram are made into a database and stored in the control means 100, and the wet bulb temperature θ _0W (° C. is measured by measuring the dry bulb temperature θ _0D (° C.) and the relative humidity φ ₀ (%). ), Dew point temperature θ _{0 dp} (° C.), and absolute humidity x ₀ (kg / kg (DA)) may be obtained.

Here, in the indirect evaporative cooler, the coolable limit of the cooled air is theoretically determined. This is because, in the case of the indirect vaporizer shown in FIG. 2, the temperature of the air passing through the cooling unit 1 can be lowered only to the wet bulb temperature θ _{0 W} (° C.). In this case, the temperature of the air passing through the cooling unit 1 can be lowered only to the dew point temperature θ _0dp (° C.). Theoretically, the cooling to the coolable limit is the time when the efficiency of the sensible heat exchange between the cooling part 1 and the cooled part 2 is the highest. Therefore, by calculating the specific enthalpies Δh _A and Δh _B at the time when cooling is possible, it is possible to set an optimal flow rate ratio between the flow rate of air blown to the cooling unit 1 and the flow rate of air blown to the cooled portion 2. it can.

For example, in the case of the indirect vaporizer shown in FIG. 2, the coolable limit is theoretically the wet bulb temperature of the air sent to the cooling unit 1. When the dry bulb temperature of the air blown to the cooling section 1 and the cooled section 2 by the blowing means 3 is θ _0D (° C.), the absolute humidity is x ₀ (kg / kg (DA)), and the wet bulb temperature θ _0W (° C.). From FIG. 1, the state of the air discharged from the cooled part 2 (the state of “B2” in FIG. 1) has a dry bulb temperature of θ _{0 W} (° C.) and an absolute humidity of x ₀ (kg / kg (DA)). ) Further, the state of the air discharged from the cooled portion 2 (state of “A2” in FIG. 6) has a dry bulb temperature of θ _0D (° C.) and a relative humidity of 100%. Therefore, the air condition detecting unit 5 detects the dry bulb temperature of the air sent to the cooling unit 1 and the cooled unit 2 as θ _0D (° C.) and the relative humidity φ ₀ (%), and the cooling unit 1 and the cooled unit are detected. 2 entrance the specific enthalpy of the air h _0, the cooling unit 1 of the outlet of the specific enthalpy h _A2, by calculating the specific enthalpy h _B2 of the outlet of the cooling unit 2, and the specific enthalpy Delta] h _a snatch in the cooling unit 1 The value of the specific enthalpy Δh _B taken away by the cooled portion 2 can be obtained. That is, an optimal flow rate ratio between the flow rate of air blown to the cooling unit 1 and the flow rate of air blown to the cooled portion 2 can be set.

For example, in the case of the indirect vaporizer shown in FIG. 3, the coolable limit is theoretically the dew point temperature of the air blown to the cooling unit 1. When the dry-bulb temperature of the air blown to the cooling part 1 and the cooled part 2 by the blowing means 3 is θ _0D (° C.) and the dew point temperature θ _0dp (° C.), the air discharged from the cooled part 2 is shown in FIG. In the state (state of “B2” in FIG. 6), the dry bulb temperature is θ 0 _dp (° C.) and the relative humidity is 100%. Further, the state of the air discharged from the cooled portion 2 (state of “A2” in FIG. 6) has a dry bulb temperature of θ _0D (° C.) and a relative humidity of 100%. Therefore, the air condition detecting unit 5 detects the dry bulb temperature of the air sent to the cooling unit 1 and the cooled unit 2 as θ _0D (° C.) and the relative humidity φ ₀ (%), and the cooling unit 1 and the cooled unit are detected. 2 entrance the specific enthalpy of the air h _0, the cooling unit 1 of the outlet of the specific enthalpy h _A2, by calculating the specific enthalpy h _B2 of the outlet of the cooling unit 2, and the specific enthalpy Delta] h _a snatch in the cooling unit 1 The value of the specific enthalpy Δh _B taken away by the cooled portion 2 can be obtained. That is, an optimal flow rate ratio between the flow rate of air blown to the cooling unit 1 and the flow rate of air blown to the cooled portion 2 can be set.

But in reality, it is not possible to lower the temperature to coolable limit, and the temperature that can be actually reached _θ 1act _(℃), of the cooling unit 2 the wet bulb arrival rate K _B,
K _B = (θ _0D −θ _1act ) / (θ _0D −θ _0W )
Defined as
_{θ 1act = θ 0D -K B (} θ 0D -θ 0W)
It becomes. Thus, the specific enthalpy _{h B2} of the outlet of the cooling unit 2 dry-bulb temperature _θ 1act (℃), may be obtained as an absolute humidity _{x 0.} The value of K _B is a numerical value that is appropriately set according to the characteristics and usage of the device can be changed, for example, between 0-3.

Also in the cooling unit 1, the exhausted air is actually exhausted at a temperature lower than the dry bulb temperature θ _0D (° C.) of the air flowing into the cooling unit 1. Therefore, if the temperature θ _2act (° C.) that can actually be reached is reached, the wet bulb temperature attainment rate K _A of the cooling unit 1 is
1−K _A = (θ _0D −θ _2act ) / (θ _0D −θ _0W )
Because
θ _2act = θ _0D − (1−K _A ) (θ _0D −θ _0W )
It becomes.

Also in the cooling unit 1, in reality, the exhausted air cannot have a relative humidity of 100%. Therefore, the actual relative humidity is Y%. Accordingly, the specific enthalpy h _A2 at the outlet of the cooling unit 1 may be obtained as the dry bulb temperature θ _2act (° C.) and the relative humidity Y%. Incidentally, K _A is a numerical value that is appropriately set according to the characteristics and usage of the device can be changed, for example, between 0-1. Further, the value of Y is also a numerical value that is appropriately set according to the characteristics of the apparatus and the usage situation, and can be changed between 70% and 100%, for example.

Thereby, the flow rate ratio adjusting means 4 and the air blowing means 3 can be adjusted by using the same method as in the case of an ideal indirect evaporative cooler using K _A , K _B and Y.

In the above description, the case where the air in the same state is blown to the cooling unit 1 and the cooled part 2 has been described. However, the present invention is not limited to this, and the dry bulb temperature is θ _0D (° C.) in the cooling part 1 and the cooled part 2. ) And relative humidity φ ₀ (%) may be blown. In this case, the difference in specific enthalpy between the air flowing in and the air exhausting may be calculated for each.

  Of course, any control method other than the above can be used as long as the operation of the flow rate ratio adjusting means can be controlled so that the efficiency of the sensible heat exchange between the cooling section 1 and the cooled section 2 is increased. is there.

  In the above description, a common fan (air blowing means 3) is used for the cooling part 1 and the cooled part 2, and the air blowing means 3 blows air to the cooling part 1 and the cooled part 2 by a damper (flow rate ratio adjusting means 4). Although the case where the flow rate ratio of the air to be adjusted has been described, as shown in FIG. The flow rate ratio of the air sent to the cooling unit 1 and the cooled part 2 is adjusted by blowing air to the cooling part 1 and the cooled part 2 using the blowing means 32) and adjusting the air volume of each fan. Of course it is also possible. In this case, the two fans (the cooling unit blowing unit 31 and the cooled unit blowing unit 32) are electrically connected to the control unit 100, and according to a command from the control unit 100 in the same manner as described above. The air volume is controlled. In addition, the air volume of the fan (cooled section air blowing means 32) that blows air to the cooled section 2 is kept constant, and only the air volume of the fan (cooling section air blowing means 31) that blows air to the cooling section 1 is controlled. 1 and the flow rate ratio of the air blown to the cooled part 2 may be adjusted. When two fans are used, the flow rate ratio adjusting means 4 need not be used.

  Moreover, you may provide suitably the dehumidification means etc. which dehumidify the air sent to the cooling part 1 or the to-be-cooled part 2. FIG.

It is an air diagram which shows the change of the specific enthalpy in the indirect vaporization cooler of this invention. It is the schematic which shows the indirect vaporization cooler of this invention. It is the schematic which shows another indirect vaporization cooler of this invention. It is a graph which shows the flow rate characteristic characteristic curve by the opening degree of a damper (flow rate ratio adjustment means 4). It is a graph which shows the frequency of the fan by the opening degree of a damper (flow rate ratio adjustment means 4). It is an air diagram which shows the change of the specific enthalpy in another indirect vaporization cooler of this invention. It is the schematic which shows another indirect vaporization cooler of this invention.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Cooling part 2 Cooled part 3 Blowing means 4 Flow rate ratio adjusting means 5 Air state detecting means 11 Wet flow path 12 Dry flow path 31 Cooling part blowing means 32 Cooled part blowing means 51 Air condition detecting means 52 Air condition detecting means 100 Control means

Claims (11)

A cooling unit that lowers the dry-bulb temperature of the air that passes by using heat of vaporization, and a partition that can exchange sensible heat, is adjacent to the cooling unit, and exchanges sensible heat with the cooling unit. An indirect evaporative cooler having a cooled part for lowering the dry bulb temperature,
A flow ratio adjusting means for adjusting a flow ratio of air blown to the cooling section and the cooled section;
An air condition detection unit for detecting information necessary to calculate a specific enthalpy of air blown to the cooling unit and the cooled unit;
Control means for controlling the operation of the flow rate adjusting means so as to increase the efficiency of sensible heat exchange between the cooling part and the cooled part based on the information detected by the air condition detecting part,
An indirect evaporative cooler characterized by comprising: Based on the information detected by the air condition detection unit, the control unit takes the cooling unit from the cooled unit when the efficiency of sensible heat exchange between the cooling unit and the cooled unit is increased. The specific enthalpy Δh _A and the specific enthalpy Δh _B taken by the cooled part are calculated by calculating the specific enthalpy Δh _A and the flow rate F _{A of} air passing through the cooled part and the flow rate F _B of air passing through the cooled part. The indirect evaporative cooler according to claim 1, wherein the operation of the flow rate ratio adjusting unit is controlled so that the ratio is F _A : F _B = Δh _B : Δh _A. A cooling unit that lowers the dry-bulb temperature of the air that passes by using heat of vaporization, and a partition that can exchange sensible heat, is adjacent to the cooling unit, and exchanges sensible heat with the cooling unit. An indirect evaporative cooler having a cooled part that lowers the dry bulb temperature, and a blowing means that blows air to the cooling part and the cooled part,
A flow ratio adjusting means for adjusting a flow ratio of air blown to the cooling section and the cooled section;
An air condition detection unit for detecting information necessary to calculate a specific enthalpy of air blown to the cooling unit and the cooled unit;
An air volume detecting means for detecting a flow rate of one or both of the air flowing into the cooling section and the cooled section; and
Based on the information detected by the air condition detecting unit and the air volume detecting unit, the flow rate ratio adjusting unit and the air blowing unit are configured to increase the efficiency of sensible heat exchange between the cooling unit and the cooled unit. Control means for controlling the operation;
An indirect evaporative cooler characterized by comprising: Based on the information detected by the air condition detection unit, the control unit takes the cooling unit from the cooled unit when the efficiency of sensible heat exchange between the cooling unit and the cooled unit is increased. and specific enthalpy Delta] h _a, wherein the cooled portion calculates the deprived ratio enthalpy Delta] h _B by the cooling section, the flow rate F of air the flow rate F _B of the air passing through the object to be cooled passes through a constant and the cooling unit The operation of the flow rate ratio adjusting means and the air blowing means is controlled so that the ratio of the flow rate F _B of air passing through the cooled portion _A and F _A : F _B = Δh _B : Δh _A The indirect vaporizer according to claim 3. A cooling unit that lowers the dry-bulb temperature of the air that passes by using heat of vaporization, and a partition that can exchange sensible heat, is adjacent to the cooling unit, and exchanges sensible heat with the cooling unit. An indirect evaporative cooler having a cooled part for lowering a dry bulb temperature, a cooling part blowing means for blowing air to the cooling part, and a cooled part blowing means for blowing air to the cooled part,
An air condition detection unit for detecting information necessary to calculate a specific enthalpy of air blown to the cooling unit and the cooled unit;
An air volume detecting means for detecting a flow rate of air blown by the cooling unit air blowing means;
Based on the information detected by the air condition detection unit, a control unit that controls the operation of the cooling unit blowing unit so that the efficiency of sensible heat exchange between the cooling unit and the cooled unit is increased,
An indirect evaporative cooler characterized by comprising: Based on the information detected by the air condition detection unit, the control unit takes the cooling unit from the cooled unit when the efficiency of sensible heat exchange between the cooling unit and the cooled unit is increased. The specific enthalpy Δh _A and the specific enthalpy Δh _B taken by the cooled part are calculated by calculating the specific enthalpy Δh _A and the flow rate F _{A of} air passing through the cooled part and the flow rate F _B of air passing through the cooled part. The indirect evaporative cooler according to claim 5, wherein the operation of the cooling unit blower is controlled so that the ratio is F _A : F _B = Δh _B : Δh _A.   The cooling section holds water in the interior and removes heat of vaporization from the passing air, and a sensible heat between the wet flow path and the wet flow path adjacent to the wet flow path by partition walls capable of sensible heat exchange. The indirect evaporative cooler according to any one of claims 1 to 6, further comprising: a dry flow path that lowers the temperature of the air passing through the replacement and supplies the air to the wet flow path. .   The said air condition detection part consists of dry-bulb temperature detection means to detect the dry-bulb temperature of air, and humidity detection means to detect the humidity of air, The any one of Claim 1 thru | or 6 characterized by the above-mentioned. Indirect evaporative cooler. The control means is configured such that the dry bulb temperature of the air blown to the cooling unit is θ _0D , the wet bulb temperature is θ _0W , the absolute humidity is x ₀ , and the dry bulb temperature arrival rate of the cooling unit is K _A (the indirect evaporative cooling). The numerical value set between 0 and 1 according to the characteristics and use conditions of the cooler), and the wet bulb temperature attainment rate of the part to be cooled is K _B (0 to 3 according to the characteristics and use conditions of the indirect vaporizer) And the relative humidity of the air exhausted by the cooling unit is Y% (a numerical value set between 70% and 100% depending on the characteristics and usage of the indirect vaporizer) The specific enthalpy Δh _{A taken} by the cooling unit from the cooled part is expressed as follows: the dry bulb temperature of the air exhausted by the cooling unit is θ _0D − (1−K _A ) (θ _0D −θ _0W ), and the relative humidity is Y%. And the specific enthalpy Δh _B where the cooled part is taken away by the cooling part, The air cooled part is evacuated dry-bulb temperature _{θ 0D -K B (θ 0D -θ} 0W), in any one of claims 1 to 6, characterized in that the absolute humidity is calculated as a x ₀ The indirect vaporizer described. The control means has a specific enthalpy Δh _{A that the} cooling section takes away from the cooled section when the dry bulb temperature of the air blown to the cooling section is θ _0D , the wet bulb temperature is θ _0W , and the absolute humidity is x _0. Is calculated on the assumption that the dry bulb temperature of the air exhausted by the cooling unit is θ _0D and the relative humidity is 100%, and the specific enthalpy Δh _B that the cooled unit is deprived by the cooled unit is calculated by the cooled unit The indirect evaporative cooler according to any one of claims 1 to 6, wherein the indirect evaporative cooler is calculated on the assumption that the dry bulb temperature of exhausted air is θ _{0 W} and the absolute humidity is x ₀ . The control means sets the specific enthalpy Δh _A that the cooling unit takes from the cooled part when the dry bulb temperature of the air blown to the cooling unit is θ _{0 W} , the dew point temperature is θ _{0 dp} , and the absolute humidity is x _0. , The dry bulb temperature of the air exhausted by the cooling unit is calculated as θ _{0 W} and the relative humidity is 100%, and the specific enthalpy Δh _B taken by the cooling unit by the cooling unit is calculated by the cooling unit The indirect evaporative cooler according to claim 7, wherein the calculation is performed assuming that the dry-bulb temperature of the air is θ _{0 dp} and the absolute humidity is x ₀ .

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