DE112013000685T5 - Cooling device and heat exchanger for sensible heat - Google Patents

Abstract

There is provided a sensible heat cooling device and exchanger in which design constraints on the heat exchanger can be reduced as compared to a conventional cooling device and a conventional heat-sensitive heat exchanger. This cooling device (1) comprises: an evaporation filter (10) which humidifies a primary-side air flow passing through it and thereby lowers its temperature; a sensible heat exchanger (13) that exchanges sensible heat between the primary-side airflow that has moved through the evaporative filter (10) and a secondary-side airflow that circulates in a control console (2); a fan (14) that outputs the primary-side airflow that has moved through the sensible heat exchanger (13) to the outside environment; and a fan (15) that circulates the secondary air flow between the control console (2) and the sensible heat exchanger (13).

Description

Technical area

The invention relates to a cooling device and a heat exchanger for sensible heat.

The present application is based on Japanese Patent Application No. 2012-012929 , filed by the applicant on January 25, 2012, the entire contents of which are hereby incorporated by reference in their entirety.

Technical background

There is known a conventional refrigeration apparatus having a sensible heat exchanger for exchanging sensible heat between a primary-side airflow and a secondary-side airflow circulating in a refrigeration object, and having a spray means for controlling the primary-side airflow by spraying water in to humidify a flow path thereof in the sensible heat exchanger (see, for example, Patent Literature 1).

In this cooling device, the cooling capacity is changed by changing a spray area of the spray, and a spray amount per unit area is kept constant to prevent the deposition of impurities in the sensible heat exchanger.

Document of the prior art

patent literature

• Patent Literature 1: JP-A 2002-206834

Summary of the invention

Problems to be solved by the invention

However, in order to achieve a predetermined cooling capacity in the conventional cooling apparatus, a sufficient area corresponding to the predetermined cooling capacity must be provided at an inlet of the flow path of the primary-side air path in the sensible heat exchanger because the cooling capacity is changed by changing the spray area, which limits the design of the sensible heat exchanger.

It is therefore an object of the invention to provide a sensible heat sink and heat exchanger which reduces the design limitations of the sensible heat exchanger as compared to conventional sensible heat sinks and heat exchangers.

Brief description of the drawings

1 FIG. 12 is a schematic view showing a configuration example of a cooling apparatus according to an embodiment of the present invention. FIG.

2 Fig. 12 is a schematic perspective view showing an example of a configuration of a sensible heat exchanger.

3 FIG. 12 is a schematic perspective view showing an example of a configuration of an evaporation filter. FIG.

4 FIG. 12 is a schematic perspective view showing an example of flow paths of the primary side air flow and the secondary side air flow in the cooling device. FIG.

5 FIG. 10 is a humidity diagram showing an example of a state change of the primary side air flow and the secondary side air flow in the cooling device. FIG.

6A Fig. 12 is a schematic perspective view showing a configuration example of the sensible heat exchanger.

6B Fig. 12 is a perspective view in cross section taken along line AA showing a configuration example of the sensible heat exchanger.

6C Fig. 12 is a cross-sectional view taken along line AA showing a configuration example of the sensible heat exchanger.

7A FIG. 15 is a perspective view for explaining a process of forming recesses in an aluminum sheet. FIG.

7B Fig. 16 is a perspective view for explaining the process of forming the recesses in the aluminum sheet.

7C Fig. 16 is a perspective view for explaining the process of forming the recesses in the aluminum sheet.

7D Fig. 16 is a perspective view for explaining the process of forming the recesses in the aluminum sheet.

8th FIG. 10 is a cross-sectional view for explaining the process of forming the recesses in the aluminum sheet. FIG.

9 Fig. 13 is a perspective view for explaining a process for manufacturing the heat exchangers.

Type of embodiment of the invention

(Configuration of the cooling device)

1 Fig. 10 is a schematic view showing a configuration example of a cooling device in the embodiment of the invention.

A cooling device 1 is used in the state in which it is attached to a control console 2 as an example of a cooling object, and has an evaporation filter 10 for lowering the temperature of introduced air by means of humidification, a water supply distributor 11 for supplying water to the evaporation filter 10 , a drain cup 12 for picking up water drops from the evaporation filter 10 and an exchanger 13 for sensible heat to exchange only sensible heat between the respective air in two mutually perpendicular paths without exchange of latent heat (moisture).

In addition, the cooling device has 1 a fan 14 for generating a flow of air passing through the vaporization filter 10 and then through the exchanger 13 for sensible heat (hereinafter referred to as "primary side airflow") and a fan 15 for generating a flow of air by removing air from the control console 2 and by sending the air through the exchanger 13 for sensible heat has moved back to the control console 2 (hereinafter referred to as "secondary-side airflow").

It should be noted that the arrangement of the fan 14 and 15 just one example forms and another arrangement can be adopted.

The cooling device 1 Also has a control unit, not shown, which controls the flow rate of the primary-side air flow by changing the speed and the like of the fan 14 controls and also the flow rate of the secondary-side air flow by changing the speed and the like of the fan 15 controls.

The water supply distributor 11 receives a water supply from an external water source W _ext via a solenoid valve 11a that adjusts the amount of water supply in accordance with an external signal.

Meanwhile, has the emptying shell 12 a float switch 12a based on the water level of the emptying tray 12 outputs a signal. The solenoid valve 11a is by an output signal of the float switch 12a controlled, reducing the water supply from the water supply manifold 11 to the evaporation filter 10 is controlled.

2 Fig. 12 is a schematic perspective view showing an example of a configuration of the exchanger 13 for sensible heat shows.

The exchanger 13 for sensible heat has a structure in the primary-side pipes 13a as passages of primary-side air flows F ₁ and secondary pipes 13b as passages of secondary air flows F ₂ alternately overlap so that they are perpendicular to each other. It should be noted that an angle between the air flow direction of the primary side pipe 13a and that in the secondary side pipe 13b is formed, is not limited to a right angle, but may be any other angle.

The primary-side pipe 13a and the secondary side pipe 13b For example, they have a pitch (width) of 2 mm at a plate thickness of 0.2 mm and may be formed by bending a panel or attaching flat bars having a thickness equal to the pitch between a plurality of panels at both edges. In this case, the plates could be warped when the air flows through the primary side pipe 13a and the secondary side pipe 13b move, because the plates are thin. In such a case, a plurality of convex shapes having a height to maintain a gap between the plates may be provided on the plates to suppress the warping. The convex shape also aims at increasing the heat transfer area as well as improving the heat exchange efficiency by an effect of increasing the heat transfer upon overflow.

The size of the exchanger 13 for sensible heat is for example: height 320 mm × width 320 mm × depth 160 mm. That is, the heat transfer area is 8.09 m ² on the primary side and also on the secondary side.

The primary-side pipe 13a and the secondary side pipe 13b are formed of a material having a high specific thermal conductivity such as aluminum or copper, moreover, the flow paths of the primary-side air flow F ₁ and the secondary-side air flow F _{2 are} airtight. The primary-side air flow F ₁ and the secondary-side air flow F ₂ , extending through the exchanger 13 for sensible heat, they only exchange sensible heat without exchanging latent heat (humidity). Therefore, the absolute humidity does not change at the inlet and the outlet, only the temperature changes.

It is assumed here that the velocity of the air currents flowing through the primary side pipe 13a and the secondary side pipe 13b move, about 2 m / s amount and that one air-side average specific thermal conductivity of 0.05 kW / m ² · K, which is comparable to a gas-liquid finned tube, is achieved. Then, when the ratio of the primary to the secondary effective heat transfer area is 1, an expected total heat transfer coefficient is 1 ÷ (1 / 0.05 + 1 / 0.05) = 25 W / m ² · K.

Therefore, when the average temperature difference of the secondary side to the primary side is 5k, an effective heat transfer area required to achieve a cooling capacity of, for example, 1000W is 1000W ÷ 25W / m ² .K ö 5k = 8m ² . That is, the above-mentioned heat transfer area of 8.09 m ² satisfies this condition.

3 FIG. 12 is a schematic perspective view showing an example of a configuration of the evaporation filter. FIG 10 shows.

The evaporation filter 10 has a filter medium 100 which is formed by weaving moisture highly absorbent / releasing fibers to a net to allow the flow of the primary-side air flow F ₁ . The filter medium 100 Constantly maintains a wet condition by removing it from the water supply manifold 11 receives a water supply. In addition, the evaporation filter has 10 a size of for example: height 80 mm × width 320 mm × depth 150 and is with an inlet side vent hole 10a and an exhaust side vent hole 10b Mistake. It should be noted that it is possible to use, for example, a humidifying filter medium for the moisture of high-absorbency / releasing fibers described by Ueno Industry Co., Ltd. and the like is available.

Here, at the outlet of the primary-side air flow F ₁ , extending through the evaporation filter 10 moves, the humidity is higher and the temperature lower than at the inlet. However, there is no change in the specific enthalpy at the inlet and at the outlet.

(Operation of the cooling device)

Now, referring to each drawing, an exemplary operation of the cooling device will be described 1 described.

4 FIG. 12 is a schematic perspective view showing an example of flow paths of the primary side air flow and the secondary side air flow in the cooling device. FIG 1 shows.

When first the cooling device 1 is turned on, the unillustrated control unit controls the fan 14 and 15 to produce the primary-side airflow F ₁ and the secondary-side airflow F ₂ . The flow rate of the primary-side air flow F ₁ and the secondary-side air flow F ₂ is, for example, 3 m ³ / min.

In addition, the control unit controls the solenoid valve 11a of the water supply manifold 11 to the water supply to the evaporation filter 10 to start. At this time, the amount of water supply is controlled by controlling the solenoid valve 11a using the float switch 12a holding the emptying cup 12 is provided, based on the water level of the drain pan 12 set.

The primary-side air flow F ₁ initially moves through the evaporation filter 10 , A state S _{11 of} the primary-side air flow F ₁ at the inlet to the evaporation filter 10 is, for example, a specific enthalpy of 17 kcal / kg at an ambient temperature of 35 ° C and a relative humidity of 40%.

Meanwhile, a state S _{12 of} the primary-side air flow F ₁ at the outlet from the evaporation filter becomes 10 derived from the humidity chart below.

5 FIG. 10 is a humidity diagram showing an example of a state change of the primary side air flow and the secondary side air flow in the cooling device. FIG 1 shows.

The state of S ₁₂ of the primary-side air flow F ₁ after passing through the evaporative filter 10 is, for example, the temperature of 26.5 ° C and a relative humidity of 80%, since the specific enthalpy of 17 kcal / kg of the state S ₁₁ does not change.

Here, the absolute humidity in state S _{11 is} equal to 0.014 kg / kg, the absolute humidity in state S _{12 is} equal to 0.0175 kg / kg, the air flow rate is equal to 3 m ³ / min and the specific volume in state S _{11 is the} same 0.892 m ³ / kg. Therefore, the water supply is in the evaporation filter 10 per hour required to achieve the above-mentioned state S ₁₂ , (0.0175-0.0140) kg / kg × 3 m ³ / min × 60 min × 0.892 m ³ / kg = 0.71 kg / H.

It should be noted that the amount of water required per month for the water supply is 0.71 kg / hr x 24 hr x 30 days = 511 L, which is about 150 to 200 Japanese yen expressed in terms of the general water fee.

The primary-side air flow F ₁ then moves through the primary-side pipe 13a the exchanger 13 for sensible heat. Meanwhile, the secondary-side air flow F ₂ moves through the secondary pipe 13b the exchanger 13 for sensible heat.

The primary-side air flow F ₁ at the inlet of the exchanger 13 for sensible heat is in state S ₁₂ . Therefore, when the temperature in the state S _{13 of} the primary-side air flow F ₁ at the outlet is 45 ° C, the relative humidity is 28% because the absolute humidity is 0.0175 kg / kg. In addition, a difference in specific enthalpy between the state S ₁₂ and the state S _{13 is} equal to 17 kcal / kg - 21.5 kcal / kg = -4.5 kcal / kg.

The primary-side air flow F ₁ and the secondary-side air flow F ₂ exchange only sensible heat without changing the respective change of the absolute humidity. Due to this replacement, the difference in specific enthalpy between a state S _{22 of} the secondary air flow F ₂ at the outlet and the state S _{21 of} the secondary air flow F ₂ at the inlet is +4.5 kcal / kg, which equals the difference of the specific enthalpy between the state S ₁₂ and the state S ₁₃ is.

Therefore, when the state S _{21 of} the secondary-side air flow F ₂ in the exchanger 13 for sensible heat is the temperature of 50 ° C and the relative humidity of 18%, the state S _{22 of} the secondary air flow F _{2 is} the temperature of 31.5 ° C and the relative humidity of 47%.

The specific enthalpy in state S ₂₁ is 20.6 kcal / kg, the specific enthalpy in state S ₂₂ is 16.1 kcal / kg, the air flow rate is 3 m ³ / min and the specific volume in state S ₂₁ is 0.934 m ³ / kg. Therefore, based on the comparison between the state S ₂₂ and the state S _21, a cooling capacity of the cooling device 1 of (20.6 - 16.1) kcal / kg x 3 m ³ / min x 60 min ÷ 0.934 m ³ / kg ÷ 0.86 kcal / W ≈ 1000 W.

Provided that the surface content of the outer housing of the control console 2 is equal to 5 m ² and the total heat transfer coefficient of the outer casing is 5 W / m ² · K, the level of the internal load in the control panel is equal to 1000 W + (40.75-35) K × 5 m ² × 5 W / m ² · K = 1144 W, where the average temperature in the control panel 2 is equal to 40.75 ° C.

Meanwhile, the average temperature in the control console is 2 then when the cooling device 1 not in use, equal to 35 ° C + 1144 W ÷ 5 m ² ÷ 5 W ² · K = 81 ° C.

(Effects of the Embodiment)

In the embodiment described above, it is possible to control the design limitations of the exchanger 13 for reducing sensible heat, since it is not necessary to add water directly to the exchanger 13 to spray for sensible heat. Therefore, the step size of the primary-side pipe 13a and the secondary-side pipe 13b the exchanger 13 for sensible heat, for example, be set to 2 mm. In addition, it is possible to provide a sufficient heat transfer area, as a result of which it is possible to obtain a sufficient cooling capacity (1000 W).

In addition, the power consumption is about 66 W, for example, since only the fans need to be driven, taking into account a cooling capacity of 1000 W (OA 35 ° C-40%, RA 50 ° C-80%) in the calculation of energy consumption efficiency 15.2 is. In contrast, in a cooling device in which air cooled by a compressor cooling method is sent into a housing of control panels and the like to lower the temperature in the housing, the power required to operate the compressor is reduced. 670 W, moreover, the energy consumption efficiency is 1.5 when the cooling capacity of 1000 W (OA 35 ° C-40%, RA 35 ° C-40%) is taken into consideration. In addition, the best energy consumption efficiency is for home appliances 6 , Compared to this information, the energy consumption efficiency can be significantly improved. It should be noted that the higher the temperature in the state S ₂₁ and the lower the humidity in the state S ₁₁ , the more the cooling capacity is improved.

In addition, since the cooling side (primary side) and the cooled side (secondary side) are hermetically sealed because z. For example, the air moving through the cooling side and the air moving through the cooled side are hermetically sealed without being mixed, it is not necessary to control the air purity of the external environment of the control panel 2 to take into account the air purity in the control panel 2 to maintain. It should be noted that the secondary side can be separated from other sections and made airtight. In this regard, "hermetically compressed" and "airtight" include the case where air is drawn in from outside except for the separated portions to adjust the pressure level in the separated portions or to maintain life of animals and plants.

In addition, since a compressor and the like are not required, it is possible to reduce the weight and configuration in comparison with conventional cooling devices simplify. In addition, rainwater and the like can be used as the water supplied to the evaporation filter, which makes it possible to reduce the required operating cost.

(Example)

The following is with reference to the 6A to 6C . 7A to 7D . 8th and 9 an example of the cooling device of the invention, in particular the tangible heat exchanger, described in detail.

6A Fig. 12 is a schematic perspective view showing a configuration example of the sensible heat exchanger.

As in 6A is shown is a heat exchanger 13A for sensible heat in the example by stacking a plurality of aluminum sheets 131 formed at a predetermined distance. Here, the exchanger has 13A for sensible heat several wells 130 that maintain the distance.

Alternatively, instead of the aluminum sheets 131 Resin or paper plates with good specific thermal conductivity can be used.

6B is a perspective view in cross section along the line AA, which is a configuration example of the exchanger 13A for sensible heat shows.

The aluminum sheet 131 has depressions 130t which are dome-shaped to project vertically upward in the drawing, and depressions 130b , which are dome-shaped and project vertically downwards. In addition, the depressions 130t and the depressions 130b formed at positions between adjacent aluminum sheets 131 each facing each other.

The shape of the depressions 130 is preferably dome-shaped to prevent the aluminum sheet 131 during the pressing work of the aluminum sheet 131 which will be described later, ruptures or breaks, but they may have other shapes unless the problem of cracks or breaks during the pressing work does not occur.

6C is a cross-sectional view along the line AA, which is a configuration example of the exchanger 13A for sensible heat shows.

The aluminum sheet 131 has a thickness T _L , further the recesses 130t and 130b formed in such a way that its height is equal to H _L , a distance between the recess 130t and the depression 130b is equal to W _L and a distance from the edge of the recess 130t or 130b is equal to W _e . In the example, the dimensions H _L = 1 mm, T _L = 0.1 mm, W _L = 20 mm and W _e = 20 mm. It should be noted that T _L can be suitably changed in the range of 0.05 to 0.3 mm.

flat bars 133 with a thickness T _f and a width W _f adhere to the aluminum sheets 131 through an adhesive 132 , As an adhesive 132 For example, a resin-based adhesive having water-resistant properties and a variable heat resistance may be used, in the example, a double-sided adhesive tape formed by impregnating a non-woven fabric with a pressure-sensitive adhesive. Alternatively, the flat bars 133 on the aluminum sheet 131 by soldering or brazing instead of using the adhesive 132 be attached. The amount of glue 132 is set so that its thickness is equal to T _b . In the example, these dimensions are T _f = 2 mm, W _f = 10 mm and T _b = 0.12 mm.

When the flat bars 133 on the aluminum sheet 131 through the glue 132 As described above, the wells are 130t and 130b facing each other, wherein the distance between them is equal to C. In the example, this dimension is C = 0.24 mm. In addition, a pitch P of the aluminum sheets 131 P = T _L + T _b , T _f + T _b = 0.1 + 0.12 + 2 + 0.12 = 2.34 mm. It should be noted that P can be suitably changed in a range of 1 to 3 mm. In addition, all the above-mentioned dimensions can be suitably changed according to the design.

(Process for making the exchanger 13A for sensible heat)

The process of making the exchanger 13A for sensible heat is now referring to the 7 to 9 described.

The 7A to 7D Fig. 15 are perspective views for explaining a process of forming the pits 130 on the aluminum sheet 131 ,

First, as in 7A shown is a lower stamp 131 ₁ , which has holes to dome-shaped depressions 130 prepared with a height of 1 mm, in addition, is an aluminum sheet 131 as a workpiece material on the lower punch 131 ₁ arranged. Subsequently, a rubber layer 131 ₂ on the aluminum layer 131 arranged to prevent tearing during the process. Then a punch receiving plate 131 ₃ , the holes with a diameter of 9 mm for the inclusion of later-described punches 131 ₄ , arranged on it.

Next, as in 7B shown is the stamp 131 ₄ with a diameter of 11 mm in the holes of the punch receiving plate 131 ₃ pressed, causing the wells 130t or 130b be formed.

8th Fig. 10 is a cross-sectional view for explaining the process of forming the pits 130 on the aluminum sheet 131 ,

The stamp holder plate 131 ₃ limits the press amount of the stamp 131 ₄ , which thereby the aluminum sheet 131 deform only by 1 mm in the normal direction of the plate surface. The deformed sections of the aluminum sheet 131 are further by the lower punch 131 ₁ dome-shaped.

After that, the lower punch 131 ₁ , the rubber layer 131 ₂ , the punch recording plate 131 ₃ and the stamp 131 ₄ , removing the pits 130t or 130b be formed.

Next, as in 7C shown is the lower punch 131 ₁ prepared and becomes the aluminum sheet 131 that either the wells 131T or the depressions 130b owns, on the lower stamp 131 ₁ arranged. Subsequently, a rubber layer 131 ₅ , the holes at positions that the wells 130t or 130b on the aluminum layer 131 Also, the punch receiving plate is placed thereon to prevent cracking during the process 131 ₃ arranged thereon.

Next, as in 7D shown is the stamp 131 ₄ in the holes of the punch receiving plate 131 ₃ , from the holes for the previously formed depressions 130t or 130b are different, pressed, thereby the pits 130b or 130t to build.

9 FIG. 15 is a perspective view for explaining a process for manufacturing the exchanger. FIG 13A for sensible heat.

There are several aluminum sheets 131 on which the wells 130t and 130b are formed, stacked, leaving the wells 130t the wells 130b are facing. Subsequently, on two mutually facing edges of the aluminum sheets 131 in every gap between the several aluminum sheets 131 the flat bars 133 arranged so that they are alternately perpendicular to each other, the aluminum sheets 131 are arranged between them.

In the exchanger 13A for sensible heat of the example are the wells 130t and 130b dome-shaped, have no edge and face each other, whereby compared to the case in which recesses are provided on only one of two paired plates, the height is reduced. This suppresses a deformation amount of the aluminum sheet 131 at the time of forming the pits 130t and 130b and reduces defects such as cracks or breaks of the aluminum sheet 131 during the process, thereby improving the yield.

As well as the depressions 130 on the aluminum sheet 131 are arranged uniformly, is a distortion of the aluminum sheet 131 less likely, so the edges of the several aluminum sheets 131 less likely to be misaligned, which results in a process of trimming the edges of the multiple aluminum sheets 131 eliminated.

In addition, when the primary-side air flows F ₁ and the secondary-side air flows F ₂ through the gaps between the aluminum sheets 131 that the primary-side pipes 13a and the secondary-side pipes 13b correspond, move, suppress the pits 130t and 130b facing each other, twisting the aluminum sheets 131 even if the air pressure of the primary-side air flow F ₁ and the secondary-side air flow F ₂ changes.

In addition, as described above, the depressions 130t and 130b facing each other, twisting the aluminum sheets 131 Can prevent an aluminum sheet 131 can be used with a thickness of 0.05 to 0.3 mm and can be the pitch P of the aluminum sheets 131 be reduced to about 1 to 3 mm.

In addition, since the pitch P of the aluminum sheets 131 is reduced to about 1 to 3 mm as described above, it is possible to provide a large heat transfer area in a small heat exchangers for sensible heat.

Meanwhile, it is necessary to provide moisture condensation water since the humidity of the primary-side air flow F _1, which extends through the primary-side tube 13a moved, almost saturated. Therefore, the exchanger 13 for sensible heat so that the primary-side airflow F ₁ moves in a vertical direction and moisture-condensing water falls down in a vertical direction due to its own weight. This confirms that water is between the aluminum sheets 131 remains and the external environment of the exchanger 13 for tactile heat is expelled by the air pressure, if the pitch P of the aluminum sheets 131 is too small, but when the pitch P is equal to 2 mm, the moisture condensation water falls down in a vertical direction due to its own weight.

Other Embodiments

It should be noted that the invention should not be limited to the embodiment and that various types of modifications can be implemented without departing from the spirit of the invention. For example, the cooling object is not limited to the control console and may be formed by server racks, storage, garages and lounges.

(Industrial Applicability)

The sensible heat sink and heat exchanger of the invention can reduce design limitations on the sensible heat exchanger as compared to conventional refrigeration and sensory heat exchangers, and are therefore industrially useful.

LIST OF REFERENCE NUMBERS

1

cooling device

2

control panel

10

Evaporation filter

10a

inlet-side vent hole

10b

exhaust side vent hole

11

Water supply distributor

11a

solenoid valve

12

drain shell

12a

float switch

13

Exchanger for sensible heat

13A

Exchanger for sensible heat

13a

primary-side pipe

13b

Secondary pipe

14

Fan

15

Fan

100

filter media

130, 130b, 130t

deepening

131

aluminum sheet

132

adhesive

133

flat bar

131 ₁

lower stamp

131 ₂

rubber sheet

131 ₃

Punch holder plate

131 ₄

stamp

131 ₅

rubber sheet

Claims (6)

Cooling device comprising: an evaporation filter which humidifies a primary-side air flow passing through it and thus lowers its temperature; a sensible heat exchanger in which a primary-side pipe as a passage for the primary-side air flow that has moved through the evaporation filter is arranged to communicate with a secondary-side pipe that circulates a passage of the secondary-side air flow circulating in a cooling object; overlaps to exchange sensible heat between the primary-side airflow and the secondary-side airflow, with mutually facing plates having pairs of convexities having a height defining a distance between the plates forming the primary-side tube and the secondary-side tube; maintains; a fan that discharges the primary-side airflow that has moved through the sensible heat exchanger to the outside; and a fan that circulates the secondary airflow between the cooling object and the sensible heat exchanger. The cooling device according to claim 1, wherein the convex shape of the sensible heat exchanger is dome-shaped. A cooling device according to claim 1 or 2, wherein the convexities of the sensible heat exchanger are evenly distributed on the plate. The cooling device according to any one of claims 1 to 3, wherein the external environment to which the primary side airflow is discharged is hermetically separated from the cooling object to be cooled by the secondary side airflow. Cooling device according to one of claims 1 to 4, wherein the cooling object to be cooled by the secondary-side air flow is airtight. Exchanger for sensible heat, which includes: a primary-side pipe that forms a passage for a primary-side airflow that has moved through the evaporation filter, and a secondary-side pipe that forms a passage for a secondary-side airflow that circulates in a cooling object that is arranged to overlap with each other to exchange sensible heat between the primary-side airflow and the secondary-side airflow; and Pairs of convex shapes having a height maintaining a distance between plates forming the primary-side tube and the secondary-side tube, and provided on the facing plates.

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