JP6360349B2 - Cooling system - Google Patents

Description

  The present invention relates to a cooling system for cooling a room.

  A cooling system including a chiller that cools a room by heat exchange with outside air is known. In patent document 1, the cooling system which combined the heat pipe with the well-known chiller is disclosed. Specifically, in Patent Document 1, a heat pipe is disposed in front of a chiller evaporator that cools the air circulating in the room, and the air flowing through the evaporator is cooled in advance by the heat pipe. In Patent Document 1, the heat pipe has a heat absorption part disposed in front of the evaporator, a heat radiating part is exposed to the outside air, and releases the heat of the indoor air flowing to the evaporator to the outside air.

  Although not related to a cooling system including a chiller, Patent Document 2 discloses a technique for cooling outside air taken into a room by a heat pipe. In Patent Document 2, the heat pipe has a heat absorbing portion disposed in a portion for taking outside air into the room, and a heat radiating portion is buried in the ground, and radiates heat of the outside air taken into the room to the ground. The outside air taken into the room flows through the room and is then exhausted outside by the exhaust fan.

JP 2010-65912 A Japanese Patent Laid-Open No. 2001-41525

  In summer, the temperature of the room tends to rise, so that the heat energy to be released from the air circulating in the room and / or the air taken into the room increases. On the other hand, since the temperature of the outside air is high in summer, the cooling efficiency is lowered due to the chiller principle that releases heat energy to the outside air. As a result, the burden on the cooling system increases dramatically, and consequently power consumption increases dramatically.

  In the summer season, the power consumption of the cooling system reaches a peak in the time zone in which the temperature of the outside air reaches the highest daytime temperature or in the time zone before and after that. At this time, since the ratio of the power consumption of the cooling system to the total power consumption of various devices is relatively high, the total power consumption transmitted by the power plant tends to peak. This peak power consumption may exceed the power transmission capacity of the power plant, and as a result, measures such as planned power outages and factory holiday operations (shifting factory operation days between companies) may be required. .

  As described above, the increase in the burden on the cooling system in the summer is not limited to an increase in cost due to an increase in power consumption, but also causes various social problems due to an increase in peak power.

  Accordingly, it is desirable to provide a cooling system that can contribute to peak power cut.

A cooling system according to an aspect of the present invention includes a heat exchanger capable of cooling outside air flowing into a room, a heat absorption unit located in a flow path to the heat exchanger for outside air, and a heat radiation unit embedded in the ground. Or a heat pipe for a heat exchanger that touches groundwater.

  Suitably, the working fluid of the heat exchanger heat pipe has a boiling point of 25 ° C. or more and 35 ° C. or less under atmospheric pressure.

  Preferably, the cooling system further includes a pump capable of sending the working fluid of the heat radiating unit to the heat absorbing unit.

  Preferably, the cooling system circulates a refrigerant with the heat exchanger, circulates the cooling water between a condenser that cools the refrigerant with cooling water, and the condenser, and A cooling tower for air-cooling water, and a heat pipe for the cooling tower in which an endothermic part is located in a flow path to the cooling water in the cooling tower of outside air, and a heat radiating part is embedded in the ground or touches groundwater. Also have.

  Preferably, the cooling system includes a condenser that circulates a refrigerant with the heat exchanger, air-cools the refrigerant, a heat absorption part located in a flow path to the condenser of outside air, and a heat radiation part. And a condenser heat pipe embedded in the ground or in contact with groundwater.

  A cooling system according to an aspect of the present invention circulates a refrigerant between a heat exchanger capable of cooling at least one of outside air flowing into the room and air circulating in the room and the heat exchanger, and cools the refrigerant A condenser cooled by water, a cooling tower that circulates the cooling water between the condenser and air-cooling the cooling water, and an endothermic portion located in a flow path to the cooling water in the cooling tower of outside air The cooling tower heat pipe is embedded in the ground or touches groundwater.

  A cooling system according to one aspect of the present invention circulates a refrigerant between a heat exchanger capable of cooling at least one of outside air flowing into a room and air circulating in the room and the heat exchanger, and air-cools the refrigerant. And a heat-absorbing part located in the flow path to the condenser of the outside air, and a heat-dissipating part embedded in the ground or in contact with groundwater.

  According to said structure, peak electric power can be cut.

The schematic diagram which shows schematic structure of the cooling system which concerns on the 1st Embodiment of this invention. The schematic diagram which shows the structure of the principal part of the cooling system of FIG. 3A is a schematic diagram showing an example of a heat pipe of the cooling system of FIG. 1, and FIG. 3B is a cross-sectional view taken along line IIIb-IIIb of FIG. The figure explaining the effect of the cooling system of FIG. The schematic diagram of the structure of the principal part of the cooling system which concerns on the 2nd Embodiment of this invention. Fig.6 (a)-FIG.6 (c) are the schematic diagrams which show the 1st modification of a heat pipe. The schematic diagram which shows the 2nd modification of a heat pipe. The schematic diagram which shows the 3rd modification of a heat pipe.

  Hereinafter, embodiments and modifications of the present invention will be described with reference to the drawings. In the second and subsequent embodiments, the same or similar configurations as those already described may be denoted by the same reference numerals as those already described, and the description may be omitted. .

<First Embodiment>
FIG. 1 is a schematic diagram showing a schematic configuration of a cooling system 1 according to the first embodiment of the present invention.

  The cooling system 1 is configured as a system that cools the air in the target room 103 of the building 101. The cooling system 1 may be configured as a part of an air conditioning system capable of performing both cooling and heating, or may be combined with an air purification system that purifies the air in the target room 103. .

  The building 101 is, for example, a factory, a building, a store, a warehouse, or a general house. The building 101 may have a plurality of target rooms 103 that are cooled by the single cooling system 1, or may have only one target room 103. The target room 103 may be any room, for example, a clean room.

  In FIG. 1, in the cooling system 1, all or part of the portion illustrated between the outline of the building 101 and the target room 103 may be disposed outside the building 101. It may be arranged inside the target chamber 103. In FIG. 1, the outline of the building 101 and the target room 103 are separately illustrated, but these may be integrated.

  The cooling system 1 includes, for example, a chiller body 3 that cools air using a refrigerant, and a cooling tower 5 that cools cooling water that cools the refrigerant in the chiller body 3. In addition, the cooling system 1 includes, for example, an outside air duct 7 for guiding outside air to the chiller body 3, an air supply duct 9 that supplies air cooled by the chiller body 3 into the target chamber 103, It has the return air duct 11 which recirculates air to the chiller main body 3, and the exhaust duct 13 for discharging | emitting the air in the object chamber 103 outside. The configurations of the chiller body 3, the cooling tower 5, and various ducts may be the same as known configurations.

  The chiller body 3 is disposed inside the building 101 and outside the target room 103, for example. The cooling tower 5 is arrange | positioned outside the building 101, for example. In FIG. 1, the cooling tower 5 is arranged on the roof of the building 101, but the cooling tower 5 is arranged at an appropriate height (for example, on the ground) on the side of the building 101. May be.

  The number of various ducts, the mounting position (opening position of the end portion and the entire routing position), material, shape, dimensions, and the like may be appropriately set according to various circumstances such as the configuration of the building 101. The various ducts can be variously modified in addition to the configuration schematically shown in FIG. For example, the outside air duct 7 and the air supply duct 9 may be shared on the chiller body 3 side. For example, the return air duct 11 and the exhaust duct 13 may be shared on the target chamber 103 side. For example, the return air duct 11 may be omitted.

  The cooling system 1 further includes a heat exchanger heat pipe 15 for preliminarily cooling outside air flowing into the chiller body 3 and a cooling tower heat pipe 17 for precooling outside air flowing into the cooling tower 5. Yes. The cooling system 1 is characterized by having these heat pipes.

  FIG. 2 is a schematic diagram illustrating a configuration of a main part of the cooling system 1.

  The chiller body 3 has a refrigerant flow path 19 through which a refrigerant (for example, chlorofluorocarbon) circulates. Various devices are arranged in the refrigerant flow path 19. For example, an evaporator 21 for exchanging heat between the air sent to the chiller body 3 and the refrigerant flowing through the refrigerant flow path 19, and a compressor 23 for compressing the refrigerant whose temperature has increased in the evaporator 21; The condenser 25 cools and condenses the compressed refrigerant, and the expansion valve 27 condenses and flows the refrigerant flowing to the evaporator 21 at a low pressure.

  The air flowing into the chiller body 3 from the outside air duct 7 and / or the return air duct 11 is cooled by exchanging heat with the refrigerant in the evaporator 21. The cooled air flows from the chiller body 3 into the air supply duct 9.

  In the example of FIG. 2, the chiller main body 3 has a fan on the side of the air supply duct 9 of the evaporator 21 in order to generate an air flow from the outside air duct 7 and / or the return air duct 11 to the air supply duct 9. 29 and an electric motor (not shown) that drives the fan 29. Such a fan may be provided at an appropriate position of the outside air duct 7, the air supply duct 9 and / or the return air duct 11 in addition to or instead of the chiller body 3.

  Cooling water is circulated between the condenser 25 of the chiller body 3 and the cooling tower 5 via the cooling water flow path 31. In the condenser 25, heat exchange is performed between the refrigerant flowing through the refrigerant flow path 19 and the cooling water flowing through the cooling water flow path 31 to cool the refrigerant. The cooling tower 5 air-cools the cooling water flowing from the condenser 25. The flow of the cooling water in the cooling water channel 31 is realized by, for example, a pump 33 provided at an appropriate position of the cooling water channel 31.

  The cooling tower 5 includes, for example, a container 35, a sprinkler 37 that sprinkles cooling water from the condenser 25 in the container 35, a fan 39 for taking outside air into the container 35, and a fan 39 that drives the fan 39. The electric motor shown in the figure, and the filler 41 that makes it easy to touch the cooling water sprayed in the container 35 and the introduced outside air.

  In the container 35, for example, an intake port 35p for taking in outside air is formed on the side surface. The lower part of the container 35 is a water tank 35 a that receives cooling water falling from the water sprinkling part 37 via the filler 41. The fan 39 is disposed, for example, in the vicinity of an opening provided above the container 35.

  Therefore, when the fan 39 is driven, outside air is taken into the container 35 from the intake port 35p, and then flows upward in the container 35. At this time, the outside air flowing upward and the cooling water falling from the sprinkling portion 37 come into contact with each other in the filler 41, heat exchange is performed between the cooling water and the outside air, and the cooling water is cooled.

  The cooling system 1 includes a control device 43 that controls the operation of each unit and a power supply device 45 that supplies power to each unit in order to realize the operations of the chiller body 3 and the cooling tower 5 as described above. . In addition, although the control apparatus 43 is shown by 1 block in FIG. 2, you may be comprised from the several control apparatus arrange | positioned at each part. The same applies to the power supply device 45.

  For example, based on the temperature detected by the temperature sensor 47 provided at an appropriate position in the target chamber 103, the control device 43 controls the cooling system 1 so that the temperature in the target chamber 103 converges to a predetermined target temperature. The operation of each part is feedback controlled. The power supply device 45 supplies power corresponding to the control command of the control device 43 to each part of the cooling system 1.

  FIG. 3A is a schematic diagram showing the configuration of the heat exchanger heat pipe 15, more specifically, a view seen from the left side of FIG. 2.

  The heat exchanger heat pipe 15 includes a heat absorbing portion 15a that takes heat away from the surroundings and a heat radiating portion 15b that releases heat to the surroundings. The heat absorbing part 15a and the heat radiating part 15b are connected to each other. A working fluid 105 is sealed in the heat exchanger heat pipe 15. The heat exchanger heat pipe 15 is depressurized to an appropriate pressure lower than the atmospheric pressure as necessary.

  As is well known, the heat absorbing portion 15a evaporates the working fluid 105 in the inside thereof and takes heat away from the surroundings. As the working fluid 105 evaporates, the pressure on the heat absorbing portion 15a side is relatively higher than the pressure on the heat radiating portion 15b side, and the evaporated working fluid 105 flows to the heat radiating portion 15b. The heat radiating part 15 b radiates heat to the surroundings and condenses the working fluid 105. The condensed hydraulic fluid 105 is supplied to the heat absorption part 15a by an appropriate method.

  The heat absorption part 15a is arrange | positioned before the external air duct 7, for example. The heat radiation part 15b is embedded in the ground, for example. The embedding depth is, for example, 1 m or more. The temperature of the ground is less changed than that of the atmosphere. That is, the underground temperature is lower than the atmospheric temperature in the summer and higher than the atmospheric temperature in the winter. For example, the underground temperature at a depth of 1 m or more is maintained at about 20 ° C. even when the atmospheric temperature exceeds 35 ° C. Therefore, in the summer, the heat exchanger heat pipe 15 can take heat from the outside air flowing into the outside air duct 7 at the heat absorbing portion 15a and release the heat into the ground at the heat radiating portion 15b.

  The working fluid 105 is, for example, a liquid that boils at a relatively low temperature. For example, under the atmospheric pressure, the boiling point of the hydraulic fluid 105 is lower than the boiling point of water (100 ° C.), and more preferably 25 ° C. or more and 35 ° C. or less. By using a low boiling point liquid as the working fluid 105, the efficiency of evaporating the working fluid 105 by the heat of the outside air in the heat absorbing portion 15a can be increased without increasing the degree of vacuum inside the heat exchanger heat pipe 15.

As such a low boiling point hydraulic fluid 105, for example, “DR-2” manufactured by EI DuPont de Nemours & Company (USA DuPont) may be used. “DR-2” is a kind of hydrofluoroolefin (Hydro Fluoro Olefin), and the structural formula is CF ₃ CH═CHCF ₃ . The boiling point of “DR-2” under atmospheric pressure is 33.4 ° C. In the experiment of the present inventor, “DR-2” boiled at about 29 ° C. under a pressure at which water boiled at 60 ° C. to 70 ° C. In addition, as the low boiling point hydraulic fluid 105, a low boiling point solvent used as a cleaning liquid may be used.

  The heat exchanger heat pipe 15 is, for example, configured to extend in an annular shape as a whole, and can recirculate the working fluid 105. In other words, the heat exchanger heat pipe 15 includes a forward path 15c that connects one end of the heat absorbing portion 15a and one end of the heat radiating portion 15b, and a return path 15d that connects the other end of the heat absorbing portion 15a and the other end of the heat radiating portion 15b. And have. As shown by the arrows in FIG. 3 (a), the liquid working fluid 105 is supplied from the heat radiating portion 15b to the heat absorbing portion 15a via the forward path 15c and evaporated from the heat absorbing portion 15a to the heat radiating portion 15b via the return path 15d. Liquid 105 flows.

  A pump 49 for sending the liquid working fluid 105 condensed in the heat radiating portion 15b to the heat absorbing portion 15a and a motor (not shown) for driving the pump 49 are provided on the heat radiating portion 15b side of the forward path 15c. ing. In addition, a check valve 51 is provided in the forward path 15c to allow the flow from the heat radiating portion 15b to the heat absorbing portion 15a and to prevent the flow in the opposite direction in order to prevent the back flow of the liquid working fluid 105. May be.

  The heat absorption part 15a is branched into a plurality, for example. In other words, the heat absorption part 15a has a plurality of branch paths 15aa having one end and the other end connected to one end and the other end of the heat dissipation part 15b via the forward path 15c and the return path 15d. The plurality of branch paths 15aa extend, for example, vertically in parallel with each other and face the open end of the outside air duct 7.

  FIG. 3B is a cross-sectional view taken along line IIIb-IIIb in FIG.

  Each branch passage 15aa has a structure in which a capillary structure portion 15ac that generates a capillary force is formed on the inner wall surface of the tubular member 15ab, like a normal heat pipe. The capillary structure portion 15ac may be a net-like (wick) or a groove-like (groove). The capillary structure portion 15ac may be formed by processing the inner wall surface of the tubular member 15ab, or may be configured by providing another member on the inner wall surface of the tubular member 15ab. As shown by the arrows in FIG. 3B, the liquid working liquid 105 quickly forms a liquid film on the inner wall surface of the branch path 15aa by capillary force.

  3A and 3B, the configuration of the heat exchanger heat pipe 15 has been described, but the configuration of the cooling tower heat pipe 17 is also the same. Generally speaking, the difference between the heat exchanger heat pipe 15 and the cooling tower heat pipe 17 is only the mounting position. That is, in the heat pipe 17 for the cooling tower, the heat absorption part 17a is positioned before the intake port 35p of the cooling tower 5 (FIG. 2). It is the same as the heat radiating portion 15b of the heat exchanger heat pipe 15 that a heat radiating portion (not shown) of the cooling tower heat pipe 17 is buried in the ground. Of course, in actual application, various dimensions, specific shapes, and the like may be different from each other.

  As described above, in the cooling system 1 of the present embodiment, the evaporator 21 (heat exchanger) capable of cooling the outside air flowing into the room and the heat absorption unit 15a are located in the flow path to the outside air evaporator 21, and the heat radiation unit 15b has a heat exchanger heat pipe 15 embedded in the ground.

  Therefore, the outside air flowing through the evaporator 21 can be cooled in advance by the heat exchanger heat pipe 15. As a result, the burden on the chiller body 3 can be reduced and the peak power in summer can be cut. In addition, the power consumption required for cooling can be reduced overall. Furthermore, since the cooling system 1 can be realized by adding a heat exchanger heat pipe 15 or the like to the existing chiller, the installation cost is low.

  FIG. 4 is a schematic diagram for explaining the effect of reducing the power consumption of the cooling system 1. In this figure, the horizontal axis indicates summer days, and the vertical axis indicates the maximum temperature of each day and the power consumption of each day. The line graph indicated by the upper solid line L1 indicates the maximum temperature. The lower bar graph shows power consumption.

  In Japan's summer season, the maximum temperature is often 30 ° C or higher, sometimes reaching 35 ° C to 37 ° C. In addition, as schematically shown in FIG. 4, according to the inventor's investigation, there is a relatively strong correlation between the maximum temperature and the power consumption. Tend to be larger.

  Here, when the outside air flowing through the evaporator 21 is cooled in advance by the heat exchanger heat pipe 15 as in the cooling system 1 of the present embodiment, the outside air is substantially outside for the evaporator 21 as indicated by a dotted line L2. The temperature will drop. For example, according to the experiment of the present inventor and the like, it is estimated that the outside air of 35 ° C. to 37 ° C. can be cooled to 30 ° C. to 33 ° C. by the heat pipe 15 for heat exchanger. And as shown with the dotted line L3 which cross | intersects a lower bar graph, the part above the dotted line L3 among power consumption can be cut. The economic effect of this cut in power consumption increases as the building 101 increases.

  In the present embodiment, the working fluid 105 of the heat exchanger heat pipe 15 has a boiling point of 25 ° C. or more and 35 ° C. or less under atmospheric pressure.

  Accordingly, since the working fluid 105 boils at a relatively low temperature, as described above, the temperature of the outdoor air in summer (for example, 30) can be effectively obtained without increasing the degree of vacuum of the heat exchanger heat pipe 15. The hydraulic fluid 105 can be evaporated at a temperature higher than or equal to. If the boiling point is too low, it becomes difficult to condense the hydraulic fluid 105 at an underground temperature (for example, about 20 ° C.), but such inconvenience is also reduced. As a result, the ease of realization of the cooling system 1 of the present embodiment is improved.

  In contrast to the present embodiment, the technique of Patent Document 1 condenses the working fluid at the temperature of the outdoor air in summer. Therefore, in patent document 1, it is thought that the boiling point of a hydraulic fluid is high compared with this embodiment. The technique of Patent Document 2 is used not only in summer, but also in winter. In summer, the working fluid is condensed at an underground temperature (about 20 ° C.). It is evaporated at about 20 ° C. as in summer. It is unclear in Patent Document 2 what kind of boiling point hydraulic fluid is preferably used to realize such an action.

  Moreover, in this embodiment, the cooling system 1 has the pump 49 which can send out the hydraulic fluid 105 of the thermal radiation part 15b to the thermal absorption part 15a.

  Therefore, for example, as in the most well-known wick-type heat pipe, the hydraulic fluid 105 is quickly and at a long distance compared to the case where the hydraulic fluid is supplied from the heat radiating portion to the heat absorbing portion by capillary force. 15a can be supplied. As a result, for example, even if the heat dissipating part 15b is disposed in the ground, the heat absorbing part 15a is disposed at a position away from the ground (such as a high place) without delaying the evaporation of the working fluid 105 in the heat absorbing part 15a The hydraulic fluid 105 can be supplied to the heat absorption part 15a. As a result, the freedom degree of arrangement | positioning of each part of the cooling system 1 improves, and the application of this invention with respect to the existing cooling system is also facilitated.

  Moreover, in this embodiment, the cooling system 1 circulates the coolant between the evaporator 21, circulates the coolant between the condenser 25 that cools the coolant with the coolant, and the condenser 25, and cools the coolant. The cooling tower 5 for cooling the air and the heat absorption part 17a (FIG. 2) are located in the flow path to the cooling water in the cooling tower 5 of the outside air, and the heat radiation part (not shown; refer to the heat radiation part 15b) is in the ground And a cooling tower heat pipe 17 embedded therein.

  Therefore, the outside air flowing into the cooling tower 5 can be cooled in advance by the cooling tower heat pipe 17. As a result, the burden on the cooling tower 5 can be reduced and the peak power in summer can be cut. In addition, the power consumption required for cooling can be reduced overall. Furthermore, since the cooling system 1 can be realized by adding a cooling tower heat pipe 17 or the like to the existing chiller, the installation cost is low.

<Second Embodiment>
FIG. 5 is a schematic diagram illustrating a configuration of a main part of the cooling system 201 according to the second embodiment.

  The cooling system 201 is different from the cooling system 1 of the first embodiment in that the chiller is air-cooled. That is, the chiller 203 of the cooling system 201 has substantially the same configuration as the chiller body 3 of the first embodiment, but in the condenser 225, the refrigerant flowing through the refrigerant flow path 19 is cooled by air. The chiller 203 includes, for example, a fan 239 that blows air to the condenser 225 and an electric motor (not shown) that drives the fan 239.

  And in the cooling system 201, it replaces with the heat pipe 17 for cooling towers of 1st Embodiment, and the heat pipe 217 for condensers for cooling the external air which flows into the condenser 225 is provided. The condenser heat pipe 217 has, for example, the same configuration as the heat exchanger heat pipe 15 described with reference to FIG. 3, and the heat absorption part 217 a is a flow path to the condenser 225 of outside air (for example, a position before the fan 239). ) And a heat radiating section (not shown) (see the heat radiating section 15b in FIG. 3) is buried in the ground.

  Even in the cooling system 201 having such a configuration, the same effects as those of the cooling system 1 of the first embodiment are exhibited. For example, cutting of peak power is expected.

<Modification of heat pipe>
Below, the modification of a heat pipe is demonstrated. In addition, although it demonstrates taking the case of the heat pipe for heat exchangers, it is the same also about the heat pipe for cooling towers and the heat pipe for condensers.

(First modification)
Fig.6 (a)-FIG.6 (c) are the schematic diagrams which show the heat pipe 151 for heat exchangers which concerns on a 1st modification. Specifically, FIG. 6A is a schematic view of the heat exchanger heat pipe 151 viewed from the side of the outside air duct 7, and FIG. 6B is a heat exchanger heat pipe from the opening direction of the outside air duct 7. FIG. 6C is a schematic view of 151, and FIG. 6C is a cross-sectional view (partially omitted) taken along line VIc-VIc in FIG.

  The heat exchanger heat pipe 151 is constituted by a wick type heat pipe that is most well known. That is, as shown in FIG. 6C, the heat exchanger heat pipe 151 has a structure in which a capillary structure portion 151c such as a wick is provided on the inner wall of the tubular member 151d.

  Further, the heat exchanger heat pipe 151 is configured, for example, so as to extend linearly as a whole. The heat exchanger heat pipe 151 is arranged with the longitudinal direction set in the vertical direction, the heat absorption part 151a constituted by the one end side part is arranged between the hands of the outside air duct 7, and the heat radiation part constituted by the other end side part. 151b is buried in the ground. For example, a plurality of heat exchanger heat pipes 151 are provided, and are provided in parallel to each other.

  Also in the heat exchanger heat pipe 151 having such a configuration, as in the heat exchanger heat pipe 15 of the embodiment, the heat of the outside air can be radiated into the ground, and thus the burden on the chiller body 3 can be reduced. .

(Second modification)
FIG. 7 is a cross-sectional view showing a heat exchanger heat pipe 153 according to a second modification.

  The heat exchanger heat pipe 153 has a plurality of fins 153f on the outer peripheral surfaces of the heat absorbing portion 153a and the heat radiating portion 153b. In this way, by increasing the surface areas of the heat absorbing part 153a and the heat radiating part 153b, heat absorption from the outside air and heat radiation to the ground are efficiently performed. In FIG. 7, the wick type heat pipe similar to the first modification is taken as an example. However, in the pump type heat pipe similar to the embodiment, the heat absorption parts such as the fins 153f and the heat radiation parts A shape for increasing the surface area may be employed.

(Third Modification)
FIG. 8 is a cross-sectional view illustrating a heat exchanger heat pipe 151 according to a third modification.

  In this modification, the heat radiating portion 151b is in contact with groundwater. In summer, the temperature of groundwater is often lower than the temperature of the ground, and it is considered that the temperature of the outside air can be lowered more effectively. In FIG. 8, the wick type heat pipe similar to the first modification is taken as an example, but in the pump type heat pipe similar to the embodiment, the heat radiating portion may be disposed so as to touch the groundwater. .

  The present invention is not limited to the above embodiments and modifications, and may be implemented in various aspects.

  The interior of the room is not limited to that constituted by buildings. For example, the inside of the room may be inside a display shelf for displaying food, inside a refrigerator (a relatively small thing that cannot be said to be a building), or inside a case of a large computer. It may be in a chamber of a manufacturing apparatus or an experimental apparatus.

  The duct can be omitted as appropriate. For example, the portion of the chiller where the housing opening for taking in outside air is provided may be exposed outside the room, and the outside air duct may be omitted. Further, for example, a portion of the chiller in which a housing opening for discharging the air after cooling is provided may be exposed indoors and the air supply duct may be omitted.

  A heat pipe is not limited to what supplies a hydraulic fluid from a thermal radiation part to a thermal absorption part with a pump, and a wick type thing. For example, the heat pipe may be of an automatic excitation type or may supply hydraulic fluid from the heat radiating unit to the heat absorbing unit using bubbles.

  The position of the heat absorption part of the heat exchanger heat pipe may be any position where the heat exchanger heat pipe is in contact with the outside air flowing through the heat exchanger (evaporator) (in the flow path to the outside air evaporator). It is not limited to this side. For example, the position of the heat absorption part may be an end part (suction port) of the outside air duct, or may be an appropriate position inside the outside air duct. Further, for example, in the case where an external duct is provided or not provided, the position of the heat absorption part may be before the housing opening of the chiller for taking in outside air, It may be a position, or may be a position inside the housing with respect to the housing opening. However, application of the present invention to an existing cooling system for buildings is easy as long as it is in front of the outside air duct.

  Similarly, the arrangement position of the heat absorption part of the cooling tower heat pipe is the position where the cooling tower heat pipe touches the outside air flowing to the cooling water in the cooling tower (in the flow path of the outside air to the cooling water in the cooling tower). What is necessary is not limited to the front of the intake. For example, the position of the heat absorption part may be the position of the intake port, or may be a position on the inner side of the cooling tower than the intake port. However, application of the present invention to an existing cooling system is easy if it is before the intake port.

  Similarly, the arrangement position of the heat absorption part of the condenser heat pipe may be a position where the condenser heat pipe comes into contact with the outside air flowing in the condenser (in the flow path to the condenser of the outside air), and takes in the outside air of the chiller. It is not limited to the front of the housing opening for. For example, the position of the heat absorption part may be the position of the housing opening, or the position of the chiller inside the housing relative to the housing opening. However, the present invention can be easily applied to an existing cooling system as long as it is before the housing opening of the chiller.

  In the embodiment, the case where both the heat pipe for the heat exchanger and the heat pipe for the cooling tower are provided, and the case where both the heat pipe for the heat exchanger and the heat pipe for the condenser are provided are exemplified, but the heat pipe for the heat exchanger Only the heat pipe for the cooling tower or only the heat pipe for the condenser may be provided. In addition, these heat pipes have the same feature compared with the prior art in that the heat of the outside air flowing through the chiller is radiated to the ground or groundwater.

  In a cooling system having a heat exchanger heat pipe, the chiller may be one that cools only the outside air taken into the room (one that does not have a function of cooling the air circulating in the room). In a cooling system in which only the cooling tower heat pipe or only the condenser heat pipe is provided, the chiller cools only the air circulating in the room (the function of taking outside air into the room or the outside air taken into the room). It may have no cooling function).

  Various known configurations may be adopted as the configuration of the chiller body and cooling tower of the water-cooled chiller, and the configuration of the air-cooled chiller. For example, FIG. 2 illustrates an example of the cooling tower in which the cooling water directly touches the outside air (open type), and the cooling water and the outside air flow in opposite directions (counter flow type). May not be directly touched (sealed type), or cooling water and outside air may flow in directions orthogonal to each other (cross flow type).

  DESCRIPTION OF SYMBOLS 1 ... Cooling system, 21 ... Evaporator (heat exchanger), 15 ... 15a ... Heat absorption part of heat pipe for heat exchangers, 15b ... Radiation part.

Claims (3)

A heat exchanger capable of cooling the outside air flowing into the room,
A heat pipe for a heat exchanger in which a heat absorption part is located in a flow path to the heat exchanger of outside air, and a heat radiation part is embedded in the ground or touches groundwater;
A condenser for circulating a refrigerant between the heat exchanger and cooling the refrigerant with cooling water;
A cooling tower for circulating the cooling water between the condenser and air-cooling the cooling water;
A heat pipe for the cooling tower, wherein the heat absorption part is located in a flow path to the cooling water in the cooling tower of the outside air, and the heat radiating part is buried in the ground or touches the ground water,
Having a cooling system. The cooling system according to claim 1, wherein the hydraulic fluid of the heat exchanger heat pipe has a boiling point of 25 ° C. or more and 35 ° C. or less under atmospheric pressure. Cooling system according to claim 1 or 2 further comprising a deliverable pump hydraulic fluid of the heat radiating portion of the heat exchanger heat pipe to the heat absorbing portion of the heat exchanger heat pipe.

Images