JP3193430U - Cooling system - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a cooling device capable of reducing design restrictions of a heat exchanger. A cooling device 1 includes a vaporization filter 10, a sensible heat exchanger 13 having a primary side cylinder and a secondary side cylinder, and exchanging sensible heat between the primary side airflow and the secondary side airflow. It has a fan 14 that discharges the primary side airflow that has passed through the sensible heat exchanger to the outside, and a fan 15 that circulates the secondary side airflow. The thin aluminum plates are fixed at a predetermined pitch and have dimples that face each other and are provided in pairs with a predetermined height interval. [Selection diagram] Fig. 1

Description

  The present invention relates to a cooling device.

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

  As a conventional cooling device, water is sprayed on the flow path of the sensible heat exchanger that exchanges sensible heat between the primary airflow and the secondary airflow that circulates the object to be cooled, and the primary airflow passage of the sensible heat exchanger. There is known one having a spraying means for humidifying (see, for example, Patent Document 1).

  This cooling device changes the cooling capacity by changing the spray area of the spray means, and suppresses the accumulation of impurities in the sensible heat exchanger by making the spray amount per unit area constant.

JP 2002-206834 A

  However, according to the conventional cooling device, since the cooling capacity is changed by changing the spray area, in order to achieve the predetermined cooling capacity, the inlet of the flow path of the primary side airflow of the sensible heat exchanger is changed. As for the area, it is necessary to secure an area corresponding to the predetermined cooling capacity, which limits the design of the sensible heat exchanger.

  Accordingly, it is an object of the present invention to provide a cooling device that reduces the restrictions on the design of the sensible heat exchanger compared to conventional cooling devices.

  In order to achieve the above object, one aspect of the present invention provides the following cooling device.

[1] A vaporization filter that humidifies the primary airflow passing therethrough to lower the temperature, a primary side tube through which the primary airflow that has passed through the vaporization filter passes, and a secondary side through which the secondary airflow that circulates the cooling target passes. A sensible heat exchanger that exchanges sensible heat between the primary side airflow and the secondary side airflow by alternately overlapping the cylinders, and a primary side airflow that has passed through the sensible heat exchanger And a fan that circulates the secondary side airflow between the object to be cooled and the sensible heat exchanger, and the primary side cylinder and the secondary side cylinder of the sensible heat exchanger are The plurality of plate members are fixed so as to have a predetermined pitch at both ends thereof, and the plurality of plate members have convex shapes with a predetermined height provided in pairs on the plate members facing each other, and The cooling device provided with a pair of convex shapes having an interval in the direction of the predetermined height

[2] A vaporization filter that humidifies the passing primary-side airflow to lower the temperature, a primary-side tube through which the primary-side airflow that has passed through the vaporization filter passes, and a secondary-side through which the secondary-side airflow that circulates the cooling target passes. A sensible heat exchanger that exchanges sensible heat between the primary side airflow and the secondary side airflow by alternately overlapping the cylinders, and a primary side airflow that has passed through the sensible heat exchanger And a fan that circulates the secondary side airflow between the object to be cooled and the sensible heat exchanger, and the primary side cylinder and the secondary side cylinder of the sensible heat exchanger are The plate members are fixed to have a pitch of 1 to 3 mm at both ends of a plurality of plate members having a thickness of 0.05 mm to 0.3 mm, and the plurality of plate members are provided in pairs on the plate members facing each other. A cooling device having a convex shape of a height.

[3] A vaporization filter that humidifies the passing primary-side airflow to lower the temperature, a primary-side tube through which the primary-side airflow that has passed through the vaporization filter passes, and a secondary-side through which the secondary-side airflow that circulates the cooling target passes. A sensible heat exchanger that exchanges sensible heat between the primary side airflow and the secondary side airflow by alternately overlapping the cylinders, and a primary side airflow that has passed through the sensible heat exchanger And a fan that circulates the secondary side airflow between the object to be cooled and the sensible heat exchanger, and the primary side cylinder and the secondary side cylinder of the sensible heat exchanger are The plate members are fixed to have a pitch of 1 to 3 mm at both ends of a plurality of plate members having a thickness of 0.05 mm to 0.3 mm, and the plurality of plate members are provided in pairs on the plate members facing each other. And the pair of convex shapes has the predetermined height. Cooling device provided at a distance of direction.

[4] The cooling device according to any one of [1] to [3], wherein the sensible heat exchanger is disposed such that a flow path of the primary side tube is along a vertical direction.

  According to the first and fourth aspects of the present invention, it is possible to reduce the restriction on the design of the sensible heat exchanger as compared with the conventional cooling device.

FIG. 1 is a diagram showing a schematic configuration example of a cooling device according to an embodiment of the present invention. FIG. 2 is a schematic perspective view showing an example of the configuration of the sensible heat exchanger. FIG. 3 is a schematic perspective view showing an example of the configuration of the vaporization filter. FIG. 4 is a schematic perspective view illustrating an example of a flow path of the primary airflow and the secondary airflow of the cooling device. FIG. 5 is a moist air diagram illustrating an example of a state change of the primary airflow and the secondary airflow of the cooling device. FIG. 6A is a schematic perspective view illustrating a configuration example of a sensible heat exchanger. FIG. 6B is a cross-sectional perspective view taken along the line AA showing the configuration example of the sensible heat exchanger. FIG. 6C is a cross-sectional view taken along line AA showing a configuration example of the sensible heat exchanger. FIG. 7A is a perspective view for explaining a step of forming dimples on an aluminum thin plate. FIG. 7B is a perspective view for explaining a step of forming dimples on the aluminum thin plate. FIG. 7C is a perspective view for explaining a step of forming dimples on the aluminum thin plate. FIG. 7D is a perspective view for explaining a step of forming dimples on the aluminum thin plate. FIG. 8 is a cross-sectional view for explaining a process of forming dimples on an aluminum thin plate. FIG. 9 is a perspective view for explaining a manufacturing process of the sensible heat exchanger.

(Configuration of cooling device)
FIG. 1 is a diagram showing a schematic configuration example of a cooling device according to an embodiment of the present invention.

  The cooling device 1 is used by being attached to a control panel 2 as an example of a cooling target, and a vaporizing filter 10 that humidifies input air to lower the temperature, and a water supply header 11 that supplies water to the vaporizing filter 10. And a drain pan 12 that receives water droplets of the vaporization filter 10 and a sensible heat exchanger 13 that exchanges only sensible heat without exchanging mutual latent heat (moisture) from two orthogonal air paths.

  In addition, the cooling device 1 takes out the air in the control panel 2 and the fan 14 that generates an airflow (hereinafter referred to as “primary airflow”) that passes through the vaporization filter 10 and the sensible heat exchanger 13. And a fan 15 that generates an airflow (hereinafter referred to as “secondary airflow”) that sends air that has passed through the control panel 2 into the control panel 2.

  In addition, arrangement | positioning of the fans 14 and 15 is an example, and it is good also as another arrangement | positioning.

  The cooling device 1 has a control unit (not shown), and controls the flow rate of the primary airflow by changing the rotation speed of the fan 14 and the flow rate of the secondary airflow by changing the rotation speed of the fan 15. To do.

The water supply header 11 is supplied with water from an external water source W _ext via an electromagnetic valve 11a that adjusts the amount of water supply according to an external signal.

  Further, the drain pan 12 has a float switch 12a that outputs a signal based on the water level of the drain pan 12, and controls the electromagnetic valve 11a by the output signal of the float switch 12a to control the amount of water supplied from the water supply header 11 to the vaporization filter 10. Control.

  FIG. 2 is a schematic perspective view showing an example of the configuration of the sensible heat exchanger 13.

Sensible heat exchanger 13 includes a primary cylinder 13a which passes the primary air flow F _1, a structure superimposed alternately so as to be orthogonal to the secondary side cylinder 13b of the secondary-side stream F ₂ passes. Note that the airflow passage direction of the primary side tube 13a and the airflow passage direction of the secondary side tube 13b are not limited to being orthogonal to each other, but may be any different angle.

  As an example, the pitch (width) of the primary side cylinder 13a and the secondary side cylinder 13b is 2 mm, the plate thickness is 0.2 mm, and may be formed by bending a plate material, or at both ends between a plurality of plate materials. A square member having a pitch thickness may be provided and bonded. Also, since the plate thickness is thin, the plate material may bend when the airflow is passed through the primary side tube 13a and the secondary side tube 13b. A plurality of them may be provided to suppress deflection. In addition, the convex shape increases the heat transfer area, and also has the purpose of improving the heat exchange efficiency due to the heat transfer promoting effect due to overflow.

As an example, the size of the sensible heat exchanger 13 is 320 mm long × 320 mm wide × 160 mm deep. That is, the heat transfer area on both the primary side and the secondary side is 8.09 m ² .

Primary cylinder 13a and secondary cylinder 13b is formed with a good thermal conductivity such as aluminum or copper material, the flow path of the primary side stream F ₁ and the secondary-side air flow F ₂ is hermetically. Since the primary airflow F ₁ and the secondary airflow F ₂ passing through the sensible heat exchanger 13 exchange only sensible heat without replacing latent heat (moisture), the absolute humidity varies depending on the input and output. Without it, only the temperature will change.

Here, the wind speed of the airflow passing through the primary side cylinder 13a and the secondary side cylinder 13b is about 2 m / s, and an air-side average thermal conductivity of 0.05 kw / m ² · k comparable to that of a gas-liquid fin tube is achieved. Assuming that the effective primary / secondary heat transfer area ratio is 1, the expected heat transfer rate is 1 / (1 / 0.05 + 1 / 0.05) = 25 W / m ² · k.

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

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

The vaporization filter 10 includes a filter medium 100 in which high moisture absorption / release fibers are knitted in a mesh shape so that the primary airflow F ₁ passes through. The filter medium 100 is supplied with water from the water supply header 11 and always maintains a wet state. . Moreover, the vaporization filter 10 has a size of 80 mm in length, 320 mm in width, and 150 mm in depth, for example, and has an input side vent 10a and an output side vent 10b. In addition, the humidifier filter medium of Ueno Kogyo etc. can be used as an example of a high moisture absorption / release fiber.

Here, the humidity rises at the input and the output of the vaporizing filter 10 primary stream F ₁ passing through, the temperature is lowered, no change in specific enthalpy of the input and output.

(Cooling device operation)
Below, the operation example of the cooling device 1 is demonstrated, referring each figure.

  FIG. 4 is a schematic perspective view illustrating an example of a flow path of the primary airflow and the secondary airflow of the cooling device 1.

First, when turning on the power of the cooling device 1, a control unit (not shown) controls the fan 14 and 15, causing the primary air flow F ₁ and the secondary-side air flow F _2. As an example, the air volume of the primary air flow _{F 1} and the secondary-side air flow _{F 2} is set to ^3m 3 / min.

  Further, the control unit controls the electromagnetic valve 11 a of the water supply header 11 and starts water supply to the vaporization filter 10. The amount of water supply is adjusted by controlling the solenoid valve 11 a based on the water level of the drain pan 12 by a float switch 12 a provided in the drain pan 12.

First, the primary airflow F ₁ passes through the vaporization filter 10. State _{S 11} of the input of the primary-side air flow _{F 1} of vaporized filter 10, as an example, the ambient temperature 35 ° C., when the relative humidity of 40%, the specific enthalpy is 17kcal / kg.

The primary-side state S ₁₂ at the output of the air flow F ₁ of vaporized filter 10 is determined from the psychrometric chart shown below.

  FIG. 5 is a moist air diagram illustrating an example of a state change of the primary airflow and the secondary airflow of the cooling device 1.

Since the specific enthalpy 17 kcal / kg does not change in the state S ₁₂ of the primary airflow F ₁ after passing through the vaporization filter 10 with respect to the state S ₁₁ , as an example, the temperature S is 26.5 ° C. and the relative humidity is 80%. To.

Here, the amount of water supplied per hour to the vaporization filter 10 necessary to achieve the state _{S 12} described above, the absolute humidity of the state _{S 11} is 0.014 kg / kg, the absolute humidity of the state _{S 12} is 0. 0175kg / kg, since the air volume is ^3m 3 / min, the specific volume of the state _{S 11} is ^{0.892m 3 / kg, (0.0175-0.0140)} kg / kg × 3m 3 / min × 60min ÷ 0. 892 m ³ /kg=0.71 kg / h.

  The amount of water required for water supply is 0.71 kg / h × 24 h × 30 day = 511 l per month. If this is converted into a general water bill, it will be about 150-200 yen.

Next, the primary air flow F ₁ passes through the primary cylinder 13 a of the sensible heat exchanger 13. Further, the secondary air flow F ₂ passes through the secondary cylinder 13 b of the sensible heat exchanger 13.

Since the primary side input of the air flow _{F 1} of the sensible heat exchanger 13 is in the state _{S 12,} if the state _{S 13} at the output of the primary side stream _{F 1} is a temperature 45 ° C., absolute humidity in 0.0175kg / kg Therefore, the relative humidity is 28%. In addition, the difference in specific enthalpy between the states _{S 12} and the state _{S 13} is 17kcal / kg-21.5kcal / kg = -4.5kcal / kg.

The primary airflow F ₁ and the secondary airflow F ₂ each exchange only sensible heat without changing the absolute humidity. This exchange, the difference in specific enthalpy of the state S ₂₂ at the output of the secondary-side air flow F ₂ and the difference in specific enthalpy between the states S ₂₁ of the input of the secondary air flow F ₂ is the state S ₁₂ and state S ₁₃ Is equal to +4.5 kcal / kg.

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

By comparing the states _{S 22} and the state _{S 21,} the cooling capacity of the cooling device 1, the specific enthalpy is 20.6kcal / kg of states _{S 21,} the specific enthalpy of the state _{S 22} is 16.1kcal / kg, the air volume 3m ³ / min, since the specific volume of the state _{S 21} is ^{0.934m 3 / kg, (20.6-16.1)} kcal / kg × 3m 3 /min×60min÷0.934m 3 / kg ÷ 0. 86 kcal / W≈1000 W.

Here, the size of the internal load of the control panel 2 is that the average temperature in the control panel 2 is 40.75 ° C., the surface area of the case exterior of the control panel 2 is 5 m ² , and the heat passage rate of the case exterior is 5 W / Assuming m ² · K, 1000 W + (40.75-35) K × 5 m ² × 5 W / m ² · K = 1144 W.

The average temperature in the control panel 2 when the cooling device 1 is not operated is 35 ° C. + 1144 W ÷ 5 m ² ÷ 5 W / m ² · K = 81 ° C.

(Effect of embodiment)
According to the above-described embodiment, since it is not necessary to spray water directly on the sensible heat exchanger 13, the design restriction of the sensible heat exchanger 13 can be reduced, and the primary side tube 13a of the sensible heat exchanger 13 can be reduced. As an example, the pitch of the secondary cylinder 13b can be set to 2 mm, and a sufficient heat transfer area can be ensured. As a result, a sufficient cooling capacity (1000 W) can be achieved.

Further, since only the fan needs to be driven, as an example, the power consumption is about 66 W, and the cooling capacity is 1000 W (OA 35 ° C.-40%, RA 50 ° C.-18%), so that the energy consumption efficiency 15.2 It is. On the other hand, a cooling device that sends air cooled by a compressor-type cooling method into a case such as a control panel and cools the temperature inside the case requires electric power of 670 W to operate the compressor, and has a cooling capacity of 1000 W ( OA35 ℃ -40%, RA35 ℃ -40%), the energy consumption efficiency is 1.5, which can greatly improve the energy consumption efficiency compared to the energy consumption efficiency 6 which is the best value of home appliances it can. Incidentally, as the temperature of the state S ₂₁ is high, the humidity of S ₁₁ is improved lower the cooling capacity.

  Also, the cooling side (primary side) and the cooled side (secondary side) are hermetically separated, that is, the air passing through the cooling side and the air passing through the cooled side are separated without mixing. Therefore, it is not necessary to consider the air cleanliness outside the control panel 2 in order to maintain the air cleanliness within the control panel 2. The secondary side may be separated from other spaces and hermetically sealed. In “airtight separation” and “airtight”, external air other than the separated space is used for the purpose of adjusting the pressure level of the separated space or maintaining the life of animals and plants. Including the case of capturing.

  Further, since a compressor or the like is not required, the weight can be reduced as compared with the conventional cooling device, and the configuration can be simplified. Moreover, rain water etc. can also be used for the quality of the water supplied to the vaporization filter 10, and the cost required for driving can be reduced.

[Example]
Hereinafter, an embodiment of the cooling device of the present invention will be specifically described with reference to FIGS. 6A to 6C, FIGS. 7A to 7D, FIGS.

  FIG. 6A is a schematic perspective view illustrating a configuration example of a sensible heat exchanger.

  As shown in FIG. 6A, the sensible heat exchanger 13A of the embodiment is configured by stacking a plurality of aluminum thin plates 131 at predetermined intervals. The sensible heat exchanger 13A has a plurality of dimples 130 in order to maintain the interval.

  Instead of the aluminum thin plate 131, a resin plate material or a paper plate material having good thermal conductivity may be used.

  FIG. 6B is a cross-sectional perspective view taken along the line AA showing the configuration example of the sensible heat exchanger 13A.

  The aluminum thin plate 131 has a dimple 130t formed in a dome shape in the vertical upward direction of the drawing and a dimple 130b formed in a dome shape in the vertical downward direction. Further, the dimples 130t and the dimples 130b are formed so as to face each other between the adjacent aluminum thin plates 131.

  The shape of the dimple 130 is desirably a dome shape so that the aluminum thin plate 131 is not cracked or torn when the aluminum thin plate 131 is pressed as will be described later. Other shapes may be used as long as the problem of cracking and tearing does not occur.

  FIG. 6C is a cross-sectional view taken along a line AA showing a configuration example of the sensible heat exchanger 13A.

Aluminum sheet 131 has a thickness _{T l,} the height of the dimples 130t and 130b _{H l,} the interval between the dimples 130t and 130b is the distance _{W l,} from end to dimple 130t or 130b is formed in _{W e} The In the present embodiment, the above-described dimensions are H _l = 1 mm, T _l = 0.1 mm, W _l = 20 mm, and W _e = 20 mm. Incidentally, _{T 1} can be appropriately changed between the 0.05-0.3Mm.

The flat bar 133 has a thickness T _f and a width W _f and is bonded to the aluminum thin plate 131 by an adhesive 132. As the adhesive 132, a resin adhesive having water resistance and heat resistance can be used. In this embodiment, a double-sided adhesive tape in which a nonwoven fabric is impregnated with a pressure sensitive adhesive is used. Instead of the adhesive 132, the aluminum thin plate and the flat bar 133 may be fixed by soldering or brazing. The amount of the adhesive 132 is adjusted so that the thickness becomes _Tb . In the examples, the dimensions described above are T _f = 2 mm, W _f = 10 mm, and T _b = 0.12 mm.

As described above, when the aluminum thin plates 131 are bonded to the flat bar 133 with the adhesive 132, the distance between the facing dimples 130t and 130b is C. In the present embodiment, the above-described dimension is C = 0.24 mm. Further, the pitch P of the aluminum thin plate 131 is P = T ₁ + T _b + T _f + T _b = 0.1 + 0.12 + 2 + 0.12 = 2.34 mm. In addition, P can be suitably changed between 1-3 mm. Moreover, all the above-mentioned dimensions can be appropriately changed according to the design.

(Manufacturing process of sensible heat exchanger 13A)
The manufacturing process of the sensible heat exchanger 13A will be described below with reference to FIGS.

  7A to 7D are perspective views for explaining a process of forming the dimple 130 on the aluminum thin plate 131.

First, as shown in FIG. 7A, prepared lower mold 131 ₁ having a hole for forming a domed dimple 130 height 1 mm, the aluminum thin plate 131 serving as the workpiece on the lower mold 131 ₁ Overlapping. Further, overlapping rubber sheets 131 ₂ for cracking prevention during processing on an aluminum thin plate 131, further overlaying press type receiving plate 131 ₃ having a pore diameter 9mm undergoing pressing die 131 ₄ described later.

Next, as shown in FIG 7B, to form a dimple 130t or 130b by the hole of the push-type receiving plate 131 ₃ presses the push-type 131 ₄ diameter 11 mm.

  FIG. 8 is a cross-sectional view for explaining a process of forming the dimple 130 on the aluminum thin plate 131.

Pressing die 131 _4, by being limited to push-in amount by press-type receiving plate 131 _3, deforming only 1mm aluminum sheet 131 in the normal direction of the plate surface. Moreover the lower die 131 _1, the shape after deformation of the aluminum sheet 131 is made to be domed.

Thereafter, the lower die 131 _1, the rubber sheet 131 _2, dimples 130t or 130b by removing the pressing die receiving plate 131 ₃ and the push-type 131 ₄ are formed.

Next, as shown in FIG. 7C, prepared lower mold 131 _1, overlaying aluminum thin plate 131 which one is formed dimples 130t or 130b on the lower mold 131 _1. Further, overlapping rubber sheets 131 ₅ having a hole at a position corresponding to the dimples 130t or 130b for cracking prevention during processing on an aluminum thin plate 131, further overlaying press type receiving plate 131 _3.

Next, as shown in FIG. 7D, to form the dimple 130b or 130t by pressing the push-type 131 ₄ in a hole other than the dimples 130t or 130b of the push-type receiving plate 131 ₃ holes.

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

  A plurality of aluminum thin plates 131 on which the dimples 130t and 130b are formed are stacked so that the dimples 130t and 130b face each other. Further, the flat bars 133 are disposed between the plurality of aluminum thin plates 131 and at the end portions of the aluminum thin plates 131, and are disposed in directions orthogonal to each other between the adjacent aluminum thin plates 131.

  The sensible heat exchanger 13A according to the present embodiment is higher in height than the case where the dimples 130t and 130b are formed in a dome shape without edges and the dimples 130t and 130b are opposed to each other so that the dimples are provided only on one plate. Therefore, the deformation amount of the aluminum thin plate 131 can be suppressed during the processing of the dimples 130t and 130b, and the problem that the aluminum thin plate 131 is cracked or broken during the processing is reduced, and the yield is improved.

  Further, since the dimples 130 are uniformly arranged on the aluminum thin plate 131, the aluminum thin plate 131 is not easily distorted, and the end portions of the plurality of aluminum thin plates 131 are less likely to be uneven, and as a result, the plurality of aluminum thin plates 131 are arranged. The process of cutting and aligning the ends of the film becomes unnecessary.

Furthermore, when passed through a primary air flow F ₁ and the secondary-side air flow F ₂ between the aluminum sheet 131 corresponding to the primary side cylinder 13a and the secondary-side tube 13b, the primary air flow F ₁ and the secondary-side air current F _{Even when} the wind pressure of ₂ varies, the facing dimples 130t and 130b suppress the deflection of the aluminum thin plate 131.

  Further, since the opposing dimples 130t and 130b suppress the deflection of the aluminum thin plate 131 as described above, an aluminum thin plate 131 having a thickness of 0.05 to 0.3 mm can be used, and the pitch P between the aluminum thin plates 131 can be set. It can be reduced to about 1-3 mm.

  Moreover, since the pitch P between the aluminum thin plates 131 is reduced to about 1-3 mm as described above, a large heat transfer area can be secured with a sensible heat exchanger having a small volume.

The primary-side air flow F ₁ passing through the primary-side tube 13a since humidity is close to saturation, it is necessary to process the condensed water, sensible heat exchanger as the primary air flow F ₁ passes vertically The vessel 13 was arranged so that the condensed water dropped in the vertical direction under its own weight. At this time, if the pitch P between the aluminum thin plates 131 is too small, water stays between the aluminum thin plates 131 and is blown out of the sensible heat exchanger 13 by the wind pressure, but when the pitch P is 2 mm. It was confirmed that the condensed water falls vertically due to its own weight.

[Other embodiments]
In addition, this invention is not limited to the said embodiment, A various deformation | transformation is possible in the range which does not deviate from the meaning of this invention. For example, the cooling target is not limited to the control panel, but can be applied to a server rack, a storage, a warehouse, a living room, and the like.

  The cooling device of the present invention is industrially useful because it can reduce the design limit of the sensible heat exchanger compared to the conventional cooling device.

DESCRIPTION OF SYMBOLS 1 Cooling device 2 Control panel 10 Evaporation filter 10a Input side vent 10b Output side vent 11 Water supply header 11a Solenoid valve 12 Drain pan 12a Float switch 13 Sensible heat exchanger 13A Sensible heat exchanger 13a Primary side cylinder 13b Secondary side cylinder 14 Fan 15 Fan 100 Filter medium 130, 130b, 130t Dimple 131 Aluminum thin plate 132 Adhesive 133 Flat bar 131 ₁ Lower die 131 ₂ Rubber sheet 131 ₃ Push die receiving plate 131 ₄ Push die 131 ₅ Rubber sheet

Claims (4)

A vaporization filter that humidifies the passing primary air stream and lowers the temperature;
The primary side airflow and the second side airflow passing through the vaporization filter and the secondary side tube passing the secondary side airflow circulating through the object to be cooled are alternately stacked. A sensible heat exchanger that exchanges sensible heat with the secondary airflow;
A fan that discharges the primary airflow that has passed through the sensible heat exchanger to the outside;
A fan that circulates the secondary airflow between the object to be cooled and the sensible heat exchanger;
The primary side tube and the secondary side tube of the sensible heat exchanger are fixed so as to have a predetermined pitch at both ends of a plurality of plate members,
The plurality of plate members have a convex shape with a predetermined height provided in pairs on the plate members facing each other,
The pair of convex shapes is a cooling device provided with an interval in the direction of the predetermined height. A vaporization filter that humidifies the passing primary air stream and lowers the temperature;
The primary side airflow and the second side airflow passing through the vaporization filter and the secondary side tube passing the secondary side airflow circulating through the object to be cooled are alternately stacked. A sensible heat exchanger that exchanges sensible heat with the secondary airflow;
A fan that discharges the primary airflow that has passed through the sensible heat exchanger to the outside;
A fan that circulates the secondary airflow between the object to be cooled and the sensible heat exchanger;
The primary side tube and the secondary side tube of the sensible heat exchanger are fixed so as to have a pitch of 1 to 3 mm at both ends of a plurality of plate members having a thickness of 0.05 mm to 0.3 mm,
The plurality of plate members is a cooling device having a convex shape with a predetermined height provided in pairs on the plate members facing each other. A vaporization filter that humidifies the passing primary air stream and lowers the temperature;
The primary side airflow and the second side airflow passing through the vaporization filter and the secondary side tube passing the secondary side airflow circulating through the object to be cooled are alternately stacked. A sensible heat exchanger that exchanges sensible heat with the secondary airflow;
A fan that discharges the primary airflow that has passed through the sensible heat exchanger to the outside;
A fan that circulates the secondary airflow between the object to be cooled and the sensible heat exchanger;
The primary side tube and the secondary side tube of the sensible heat exchanger are fixed so as to have a pitch of 1 to 3 mm at both ends of a plurality of plate members having a thickness of 0.05 mm to 0.3 mm,
The plurality of plate members have a convex shape with a predetermined height provided in pairs on the plate members facing each other,
The pair of convex shapes is a cooling device provided with an interval in the direction of the predetermined height. The cooling device according to any one of claims 1 to 3, wherein the sensible heat exchanger is disposed such that a flow path of the primary side tube is along a vertical direction.

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