JP2010071512A - Air conditioning heat source system using cooling tower - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a cooling system capable of preventing excessive dehumidification of a server room, achieving high reliability, saving energy and preventing uneven cooling. <P>SOLUTION: This air conditioning heat source system includes: a heat source system 10 for cooling cold water at least by energy of outside air out of the energy of outside air and energy of electricity etc.; an air conditioner 20 for performing heat exchange between cold water and return air by heat exchangers 21, 22 constituted to form two stages and using heat from the heat source system 10; and cold water pumps 11D<SB>2</SB>, 12D<SB>2</SB>for circulating heat source water between the heat exchangers 21, 22 and the heat source system 10. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to an air conditioning heat source system which is used for air conditioning for adjusting room temperature in a building and supplies a cooling medium after cooling.

  Air conditioning systems are used in various fields, for example, in data center server rooms. In the server room, racks for storing servers are installed vertically and horizontally. As the performance of IT (Information Technology) equipment increases, the energy consumption of the equipment increases. Even in the server room, it is expected that the thermal load of one rack for storing servers will be 20 to 30 kW. In the server room, floor blowing air conditioning is performed as air conditioning according to a thermal load such as a server (see, for example, Patent Document 1).

  This air conditioning system is shown in FIG. The air conditioning system includes an air conditioner 101, and the air conditioner 101 includes a cooling coil 102 and a blower 103. The cooling coil 102 is a direct expansion type and is connected to an outdoor unit 104 installed outside the server room M by a refrigerant pipe 105. The exhaust from the server 106 is air supplied from the opening 108 under the server 106 through the underfloor chamber 107 of the double floor and air blown into the equipment room M from the opening 109 of the floor F of the server room M. And mixed air.

  With such an air conditioning system, it is conceivable to use water as a heating medium because of the abundant variations of operation that aim at energy saving. In that case, a refrigerator and a pump that cools using electric energy are used instead of the outdoor unit 104, and water is used as a heat medium instead of the chlorofluorocarbon refrigerant. Recently, there is also a system that uses free cooling in winter to utilize natural energy (see, for example, Patent Document 2). As shown in FIG. 20, the cold water production system includes a cooling tower 121 that uses outside air, a heat exchanger 122, a refrigerator 123 that uses electric energy, and a heat exchanger 124 on the load side. . Furthermore, the cold water production system includes cooling water pumps 131 and 132 and valves 141 to 150. In this cold water production system, a load-side heat exchanger 124 corresponds to the cooling coil 102 in FIG. And it air-conditions with the cold water manufactured with the cooling tower 121 or the refrigerator 123. FIG.

When the chilled water production system of FIG. 20 is used in an air conditioning system, the valves 141 to 150 are opened and closed in the summer to form the flow paths FL101 and FL102 shown in FIG. The cooling water produced in the cooling tower 121 flows through the flow path FL101 and is used in the refrigerator 123. The cold water produced by the refrigerator 123 flows through the flow path FL102 and is supplied to the load-side heat exchanger 124. On the other hand, in the winter season, the valves 141 to 150 are opened and closed to form the flow paths FL103 and FL104 shown in FIG. The cooling water produced in the cooling tower 121 flows through the flow path FL103 and is sent to the heat exchanger 122. The cold water produced by the intermediate heat exchanger 122 flows through the flow path FL104 and is supplied to the heat exchanger 124 on the load side. In the case of using a closed cooling tower, the intermediate heat exchanger 122 is often omitted.
JP 2003-166729 A JP-A-6-249471

  However, the conventional system using the conventional cold water production system for the air conditioning system has the following problems. If, for example, 7 ° C. cold water is allowed to flow through the load-side heat exchanger 124 and the high-temperature return air circulating through the server room M, for example, 40 ° C. return air, is rapidly cooled, the server room is excessively dehumidified. In this case, it may be necessary to humidify the server room in order to prevent a failure due to charging.

  Moreover, the system which used the conventional cold water manufacturing system for the air conditioning system has the following subject. For example, in the server room of the data center, the server operates for 24 hours. Therefore, high reliability is required for the room temperature management of the server room. That is, when a conventional system is used to cool the server room, if the cooling tower 121, the intermediate heat exchanger 122, the refrigerator 123, or the like of the system breaks down, room temperature management is affected. The situation is the same in the high sensible heat load room other than the server room.

  Moreover, the system which used the conventional cold water manufacturing system for the air conditioning system has the following subject. In this system, the refrigerator 123 using electric energy is fully operated in the summer, and the electric energy consumption of the refrigerator 123 increases.

  Furthermore, a system using a conventional cold water production system for an air conditioning system has the following problems. When the return air is rapidly cooled, there is a possibility that the temperature distribution is uneven (cooling unevenness).

  The object of the present invention is to solve the above-mentioned problems, prevent excessive dehumidification of the server room, enable high reliability, save energy, and prevent the occurrence of uneven cooling. Is to provide.

  In order to solve the above-mentioned problems, the invention of claim 1 utilizes heat source means for cooling the heat source water with at least the former energy among the energy of outside air and electricity, and the heat from the heat source means. A two-stage heat exchanger, heat exchange means for exchanging heat between the heat source water and the return air from the air conditioning room, and water supply means for circulating the heat source water between the heat exchange means and the heat source means; And an air conditioning heat source system using a cooling tower.

  In the invention of claim 1, the heat source means cools the heat source water with the energy of the outside air and the energy such as electricity, or only with the energy of the outside air. The energy of outside air refers to the heat of outside air. In addition, energy such as electricity refers to energy excluding natural energy, or artificially generated and purified. The outside air heat exchanging means is a two-stage heat exchanger that uses heat from the heat source means, and exchanges heat between the return air circulating in the server room and the heat source water, for example. In this case, the heat exchanger having a two-stage configuration may be integrated or separated, and heat source water having different properties may flow along the return airflow. The water supply means circulates the heat source water between the heat exchange means and the heat source means.

  According to a second aspect of the present invention, in the air conditioning heat source system utilizing the cooling tower according to the first aspect, the heat source means transmits the first heat source device using the energy of the outside air and the energy of the outside air or electricity. And a second heat source device that is switched and used according to the temperature, and the heat source water is cooled using the first and second heat source devices.

  A third aspect of the present invention is the air conditioning heat source system using the cooling tower according to the second aspect, wherein the heat source means supplies the heat source water from the first heat source device to the heat exchanger before the heat exchange means. And supplying heat source water from the second heat source device to the heat exchanger in the subsequent stage.

  According to a fourth aspect of the present invention, in the air conditioning heat source system using the cooling tower according to the second aspect, the heat source means cools the heat source water cooled by the first heat source device by the second heat source device. The heat exchange means supplies heat source water from the second heat source device of the heat source means to the subsequent heat exchanger, and cold heat is taken away by the latter heat exchanger. Heat source water is supplied to the preceding heat exchanger.

  According to a fifth aspect of the present invention, in the air conditioning heat source system using the cooling tower according to any one of the second to fourth aspects, the second heat source device of the heat source means has an outdoor wet bulb temperature lower than a predetermined value. The heat source water is cooled using the energy of the outside air, and the heat source water is cooled using the energy of electricity or the like when the outside air wet bulb temperature is higher than a predetermined value.

  Invention of Claim 6 is an air-conditioning heat-source system using the cooling tower of any one of Claims 2-5, Comprising: As for the 2nd heat-source apparatus of the said heat-source means, the temperature of return air is low by a low load. When the temperature is low, the heat source water is cooled using the energy of outside air, and when the temperature of the return air is high due to a high load, the heat source water is cooled using energy such as electricity.

  A seventh aspect of the present invention is the air conditioning heat source system using a cooling tower according to any one of the second to sixth aspects, wherein the first and second heat source devices supply heat source water by sprinkling the supplied water. Switching between the closed type for cooling and the open type for cooling the heat source water by evaporation of the heat source water, the heat source water is cooled, and when water supply to at least one of the first and second heat source devices stops, the water supply is cut off. The heat source device is characterized in that the heat source water is cooled using hermetic cooling and energy such as electricity.

  According to the first aspect of the present invention, since the heat exchanger has a two-stage configuration for cooling the return air in the room or the like, the server room is prevented from being excessively dehumidified and charged compared to the case of the one-stage configuration. It is not necessary to humidify the server room in order to prevent failures due to In addition, since the energy of the outside air is also used when cooling the heat source water, the use of energy such as electricity is suppressed and energy saving is enabled. Furthermore, it is possible to prevent occurrence of temperature distribution bias (cooling unevenness) in the heat exchanged return air.

  According to the invention of claim 2, since the first heat source device that uses the energy of the outside air is always used, when the second heat source device uses energy such as electricity, the amount of use of this energy is suppressed. Enable. By providing two types of heat source devices, abundant operation modes can be enjoyed while preparing for failure.

  According to the invention of claim 3, the heat exchanger in the previous stage can precool the return air using the heat source water cooled by using the energy of the outside air. As a result, it is possible to prevent an uneven temperature distribution from occurring in the heat exchanged return air, and to reduce the burden on the heat exchanger in the subsequent stage, that is, the power consumption of the heat source device.

  According to the invention of claim 4, in the heat source means, the second heat source device cools the heat source water pre-cooled by the first heat source device. Thereby, when the second heat source device uses energy such as electricity, it is possible to suppress the amount of energy used. Moreover, in the heat exchange means, the heat source water that has been deprived of the cold heat by the latter heat exchanger is used by the former heat exchanger to precool the return air, so that the heat source water can be effectively utilized.

  According to the invention of claim 5, the energy for cooling the heat source water is switched based on the outside air wet bulb temperature. Thus, for example, when the outside air wet bulb temperature is set to 12 ° C., the heat source water is cooled using the energy of the outside air for about half of the year in Tokyo and for a longer period in Hokkaido. It is possible to set the second heat source device.

  According to the invention of claim 6, when the heat source water is cooled using the energy of the outside air, the heat source water is immediately cooled using the energy such as electricity when the load is changed from a low load to a high load. On the contrary, when the load is changed from a high load to a low load, the heat source water is cooled using the energy of the outside air, so that it is possible to cope with a change in the load.

  According to the invention of claim 7, since the cooled heat source water is supplied to the heat exchanging means even when the water supply to at least one of the first heat source device and the second heat source device stops, the air conditioning using the cooling tower The reliability of the heat source system can be increased.

  Next, embodiments of the present invention will be described in detail with reference to the drawings. In the following embodiments, the case where air conditioning is performed on the server room of the data center is taken as an example.

(Embodiment 1)
An air conditioning heat source system utilizing a cooling tower according to this embodiment is shown in FIGS. As shown in FIG. 1, this cooling tower-based air conditioning heat source system includes a heat source facility 10 for producing cold water (heat source water) used for air conditioning of the server room M, and an air conditioner 20 installed in the server room M. The air conditioner 20 includes heat exchangers 21 and 22 and a blower 23. In this embodiment, constituent elements of the server room M that are considered to be the same as or the same as those in FIG. 19 described above are denoted by the same reference numerals, and description thereof is omitted.

  As shown in FIG. 2, the heat source facility 10 mainly includes heat source devices 11 and 12 and valves 13A to 13D and 14A to 14D. The valves 13A to 13D and 14A to 14D are automatic control valves or manual valves. The heat source device 11 and the heat exchanger 21 are connected to each other by a supply pipe 15A that supplies cooled cold water and a return pipe 15B that returns the cold water from which the cold has been removed. A valve 13A that opens and closes the flow of cold water supplied after cooling is attached to the supply pipe 15A, and a valve 13B that opens and closes the flow of returning cold water is attached to the return pipe 15B.

  Similarly, the heat source device 12 and the heat exchanger 22 are connected by a supply line 16A and a return line 16B. A valve 14A is attached to the supply pipeline 16A, and a valve 14B is attached to the return pipeline 16B.

  Further, a branch line 15C for flowing cold water supplied from the heat source device 11 is connected between the supply line 15A upstream of the valve 13A and the supply line 16A downstream of the valve 14A. . A valve 14C for opening and closing the supplied cold water is attached to the branch pipe line 15C. A branch pipe 15D for flowing cold water that has been deprived of cold heat is connected to the return pipe 15B on the upstream side of the valve 13B and the return pipe 16B on the downstream side of the valve 14B. A valve 13D for opening and closing the returning cold water is attached to the branch line 15D.

  Similarly, a branch line 16C is connected between the supply line 16A on the upstream side of the valve 14A and the supply line 15A on the downstream side of the valve 13A. A valve 13C is attached to the branch line 16C. A branch line 16D is connected between the return line 16B on the upstream side of the valve 14B and the return line 15B on the downstream side of the valve 13B. A valve 14D is attached to the branch pipe line 16D.

  The valve 13C and the branch pipe line 16C, and the valve 13D and the branch pipe line 15D are used when switching according to the conditions of the heat source device 11. Similarly, the valve 14C and the branch conduit 15C, and the valve 14D and the branch conduit 16D are used when switching according to the conditions of the heat source device 12.

The heat source facility 10 has two operation modes by switching the valves 13A to 13D and the valves 14A to 14D. One is a normal operation mode. In the normal operation mode, the valves 13A to 13D are
Valve 13A, valve 13B... Open valve 13C, valve 13D. In addition, the valves 14A to 14D
Valves 14A, 14B ... Open Valves 14C, 14D ... Closed. Thereby, the cooled cold water from the heat source device 11 is supplied to the heat exchanger 21 of the air conditioner 20, and the cold water from which the cold heat has been removed by the heat exchanger 21 returns to the heat source device 11. Similarly, the cooled cold water from the heat source device 12 is supplied to the heat exchanger 22 of the air conditioner 20, and the cold water deprived of the cold heat by the heat exchanger 22 returns to the heat source device 12.

The remaining operation mode by the heat source facility 10 is a backup operation mode. This operation mode is for responding to the malfunction of the heat source device 11 and the heat source device 12, and switching between opening and closing of the valves 13A to 13D and the valves 14A to 14D is performed according to the malfunction of each device. For example, when the heat source device 12 breaks down and the supply of cold water is stopped,
Valve 14A, valve 14B ... closed Valve 14C, valve 14D ... opened. By doing so, the cooled cold water from the heat source device 11 is also supplied to the heat exchanger 22.

As shown in FIG. 3, the heat source device 11 mainly includes a cooling tower 11A, an intermediate heat exchanger 11B, a refrigerator 11C, chilled water pumps 11D ₁ and 11D ₂ , and valves 11E _{1 to} 11E ₄ . Furthermore, the refrigerator 11C is provided with a condenser 11C ₁ and the evaporator 11C _2. The valves 11E _{1 to} 11E ₄ are automatic control valves or manual valves.

  The cooling tower 11A is a device using free cooling that cools the cooling water (heat source water) from which the cold heat from the air conditioner 20 has been removed by outside air. In general, the cooling tower includes an open type and a closed type. As shown in FIG. 4A, the open-type cooling tower sprays the cooling water from which the cooling heat has been removed to the filler, which is a synthetic resin sheet. At this time, by applying wind to the filler, a part of the cooling water is evaporated to cool the cooling water. On the other hand, as shown in FIG. 4B, the closed cooling tower flows cooling water from which cooling heat has been removed to the cooling coil. The cooling coil is sprayed with makeup water supplied from the outside and circulated by a pump, and further blows air on the cooling coil. Thereby, makeup water evaporates and a cooling coil is cooled, and cooling water is cooled. In this embodiment, intermediate heat exchangers 11B and 12B are employed and an open type is shown as the cooling tower 11A.

  The intermediate heat exchanger 11 </ b> B is a device that performs heat exchange between the cooling water from the cooling tower 11 </ b> A and the cold water returned from the air conditioner 20. Here, the refrigerator 11C is an electric type and is a reciprocating compression type. Of course, an energy source other than electricity, such as an absorption refrigerator or a cold / hot water generator in which the drive source or gas is gas, steam, or oil, can be used.

Between the cooling tower 11A and the intermediate heat exchanger 11B is connected by a supply conduit 11F ₁ for flowing a cooling water cooled by the cooling tower 11A. A cold water pump 11D ₁ is attached to the supply line 11F ₁ , and a valve 11E ₁ is attached to the downstream side of the cold water pump 11D ₁ . The intermediate heat exchanger 11B, cold is connected return line 11F ₂ for flowing a cooling water deprived, the tip of the return line 11F ₂ is guided to the cooling tower 11A. Between the supply line 11F ₁ on the upstream side of the valve 11E ₁ and the condenser 11C _1, the branch line 11F ₃ are connected. The branch line 11F _3, and the valve 11E ₂ is attached. Between the return line 11F ₂ and the condenser 11C _1, branch line 11F ₄ is connected.

A supply conduit 11F ₅ for flowing cooled cold water is connected to the intermediate heat exchanger 11B. A supply conduit 11F ₅ is chilled water pump 11D ₂ is attached. Downstream supply line of chilled water pump 11D ₂ 11F ₅ is connected to the supply line 15A. Further, in the intermediate heat exchanger 11B, the return line 11F ₆ for flowing cold water cold heat deprived is connected. Return line 11F ₆ is connected to the return line 15B.

Between the supply conduit 11F ₅ on the upstream side of the cold water pump 11D ₂ and the evaporator 11C ₂ are branched passages 11F ₇ for flowing the cooled cold water is connected. A branch pipe 11F ₈ for flowing cold water deprived of cold heat is connected between the return pipe 11F ₆ and the evaporator 11C _2, and a valve 11E ₄ is attached to the branch pipe 11F _8. Yes.

  The heat source device 11 having such a configuration has two operation modes according to a low temperature season and a high temperature season, such as winter and summer. In this embodiment, the outdoor air temperature is 12 ° C. as the boundary of the outdoor air temperature, a season higher than the outdoor air wet bulb temperature 12 ° C. is defined as the summer, and a season lower than the outdoor air wet bulb temperature 12 ° C. is defined as the cold season.

When the heat source device 11 enters the cold season operation mode, the valves 11E _{1 to} 11E ₄ are
Valve 11E ₁ , Valve 11E ₃ ... Open Valve 11E ₂ , Valve 11E ₄ ... Closed Chilled water pump 11D ₁ ... On Chilled water pump 11D ₂ ... Turned on. Thus, as shown in FIG. 5, the cooling water from the cooling tower 11A is flowed through channel FL11 by chilled water pumps 11D _1, cold water from the air conditioner 20 is flowing through the channel FL12 by chilled water pumps 11D _2. In the intermediate heat exchanger 11 </ b> B, heat exchange between the cooled cooling water from the cooling tower 11 </ b> A and the cold water deprived of the cold by the air conditioner 20 is performed, and the cooled cold water is supplied to the air conditioner 20. That is, in the cold season operation mode, the heat source device 11 manufactures cold water by cooling the cold water from which the cold air has been taken away by the air conditioner 20 by free cooling using the cold heat (natural energy) of the outside air.

  For example, when the surface area of the filler is large or the density of the filler is high, the temperature of the cooling water discharged from the outlet of the cooling tower 11A is reduced when the outside air wet bulb temperature of the outside air decreases as shown in FIG. Decrease significantly. Specifically, when the outdoor wet bulb temperature is 27 ° C. and the load factor is 100, the temperature of the cooling water returned to the cooling tower 11A is 32 ° C., and the temperature of the cooling water discharged from the cooling tower 11A is 28 ° C. On the other hand, when the outside air wet bulb temperature is 5 ° C., the temperature of the cooling water returned to the cooling tower 11A is 18 ° C., and the temperature of the cooling water discharged from the cooling tower 11A is 8.5 ° C. The cooling tower 11A using free cooling produces cooling water in this way both in the cold season and in the summer, and is particularly effective in the cold season.

When the heat source device 11 is in the summer operation mode, the valves 11E _{1 to} 11E ₄ are
Valve 11E _1, valve 11E 3 _... Close Valve 11E _2, a state of the valve 11E 4 _... open chilled water pump 11D 1 _... on chilled water pump 11D 2 _... On. Thus, as shown in FIG. 7, the cooling water from the cooling tower 11A is flowed through channel FL13 by chilled water pumps 11D _1, cold water from the air conditioner 20 is flowing through the channel FL14 by chilled water pumps 11D _2. Cooled in the cooling tower 11A coolant is used to cool the condenser 11C ₁ of the refrigerator 11C, it cooled cold water is supplied to the air conditioner 20 by the evaporator 11C _2. That is, in the summer operation mode, cold water is cooled using cooling water and electric energy to produce cold water.

The heat source device 12 is the same as the heat source device 11. In other words, the heat source unit 12, the cooling tower 12A, the intermediate heat exchanger 12B, refrigerator 12C, chilled water pump _12D 1, 12D _2, mainly includes a valve _12E 1 _{~12E 4,} refrigerator 12C includes a condenser 12C ₁ and an evaporator 12C _2. The cooling tower 12A to the chilled water pumps 12D ₁ and 12D ₂ and the valves 12E _{1 to} 12E ₄ include a supply line 12F ₁ , a return line 12F ₂ , a branch line 12F ₃ , 12F ₄ , a supply line 12F ₅ , and a return line. The pipes 12F ₆ and the branch pipes 12F ₇ and 12F ₈ are connected to each other.

  The air conditioner 20 includes two-stage heat exchangers 21 and 22 and a blower 23 as shown in FIG. The blower 23 blows air. Thereby, the return air which the air in the server room M flows toward the heat exchanger 22 from the heat exchanger 21 generate | occur | produces. The heat exchanger 21 lowers the return air temperature Tep1 of the server room M to the temperature Tep2, and the heat exchanger 22 lowers the return air temperature Tep2 from the heat exchanger 21 to the temperature Tep3. Further, the return air at the temperature Tep3 from the heat exchanger 22 is supplied to the underfloor chamber 107 of the double floor of the server room M. The reason why the heat exchange structure of the air conditioner 20 is configured in two stages is to prevent excessive dehumidification of the server room M and to prevent uneven cooling. When the heat exchange structure of the air conditioner 20 is a one-stage configuration, when low-temperature cold water is sent to the heat exchanger and the high-temperature return air in the server room M is rapidly cooled, the server room M is excessively dehumidified, In addition, the temperature distribution is uneven (cooling unevenness) with respect to the return air. On the other hand, when the heat exchange structure of the air conditioner 20 has a two-stage configuration, the high-temperature return air in the server room M is cooled in order, so that excessive dehumidification of the server room M is prevented and cooling unevenness is generated. Can be prevented.

  The two-stage heat exchangers 21 and 22 can be used for the air conditioner 20 either as an integral type or as a separate type. That is, cold water having different properties may flow along the return airflow in the server room M.

  Next, the operation of the air conditioning heat source system using the cooling tower according to this embodiment will be described. When the heat source device 11 and the heat source device 12 are normal, the heat source device 11 is connected to the heat exchanger 21 of the air conditioner 20 in a normal operation mode in which the valves 13A and 13B are opened and the valves 13C and 13D are closed. At the same time, the heat source device 11 is always operated in the cold season operation mode throughout the four seasons. That is, as shown in FIG. 8, the heat source device 11 manufactures cold water by free cooling, and supplies the cold water to the heat exchanger 21 of the air conditioner 20 through the flow path FL21.

  Further, the valves 14A and 14B are opened and the valves 14C and 14D are closed by the normal operation mode, and the heat source device 12 is connected to the heat exchanger 22 of the air conditioner 20. At the same time, the heat source device 12 is operated in the cold season operation mode or the summer operation mode according to the temperature of the outside air. That is, the air conditioner 20 produces cold water by free cooling in the cold season, supplies cold water to the heat exchanger 22 of the air conditioner 20 through the flow path FL22, and produces cold water by the cooling water and the refrigerator 12C in the summer. To the heat exchanger 22.

  Even in the cold season, when the temperature of the return air rises due to a high load, cold water is produced in the summer operation mode. Even in summer, when the return air temperature is low due to low load, cold water is produced in the cold season operation mode.

  In the air conditioner 20, the high-temperature return air from the server room M is sent to the heat exchanger 21 by the blower 23. The heat exchanger 21 performs heat exchange between the cold water from the heat source device 11 and the return air, and cools the high-temperature return air in the server room M in advance. The return air pre-cooled by the heat exchanger 21 is further cooled by the subsequent heat exchanger 22. That is, the high-temperature return air in the server room M is cooled in stages by the heat exchangers 21 and 22 having the two-stage configuration of the air conditioner 20.

  For example, in the cold season, when the outside air wet bulb temperature is 12 ° C., the cooling tower 11A of the heat source device 11 supplies 17 ° C. cooling water to the intermediate heat exchanger 11B. The intermediate heat exchanger 11B performs heat exchange between the 23 ° C. cold water from the heat exchanger 21 of the air conditioner 20 and the 17 ° C. cooling water to produce 19 ° C. cold water. At the same time, the temperature of the cooling water deprived of cold heat rises from 17 ° C to 21 ° C. The cooling water that has been deprived of cold heat and reaches 21 ° C. is cooled again to 17 ° C. by the cooling tower 11A that cools using outside air of 12 ° C.

  The 19 ° C. cold water produced by the intermediate heat exchanger 11 </ b> B is supplied to the heat exchanger 21 of the air conditioner 20. The heat exchanger 21 exchanges heat between 35 ° C. return air in the server room M and 19 ° C. cold water, and sends 23.5 ° C. return air to the heat exchanger 22. At the same time, the cold water whose temperature has risen to 23 ° C. by the heat exchange of the heat exchanger 21 is returned to the intermediate heat exchanger 11B of the heat source device 11.

  On the other hand, when the outside air wet bulb temperature is 12 ° C., the cooling tower 12A of the heat source device 12 supplies 17 ° C. cooling water to the intermediate heat exchanger 12B. The intermediate heat exchanger 12B exchanges heat between 20 ° C. cold water from the heat exchanger 22 of the air conditioner 20 and 17 ° C. cooling water to produce 19 ° C. cold water. At the same time, the temperature of the cooling water deprived of cold heat rises from 17 ° C to 18 ° C. The cooling water that has been deprived of cold heat and has reached 18 ° C. is cooled again to 17 ° C. by the cooling tower 12A that cools using outside air at 12 ° C.

  The 19 ° C. cold water produced by the intermediate heat exchanger 12B is supplied to the heat exchanger 22 of the air conditioner 20. The heat exchanger 22 performs heat exchange between 23.5 ° C. return air from the heat exchanger 21 and 19 ° C. cold water, and sends the 20 ° C. return air to the underfloor chamber 107 of the server room M. At the same time, the cold water whose temperature has risen to 20 ° C. by the heat exchange of the heat exchanger 22 is returned again to the intermediate heat exchanger 12B of the heat source device 12.

  By the way, in the summer, when the outdoor wet bulb temperature is 27 ° C., the cooling tower 11A of the heat source device 11 supplies 29 ° C. cooling water to the intermediate heat exchanger 11B. The intermediate heat exchanger 11B performs heat exchange between the 37 ° C. chilled water from the heat exchanger 21 of the air conditioner 20 and the 29 ° C. cooling water to produce 32 ° C. chilled water. At the same time, the temperature of the cooling water deprived of cold heat rises from 29 ° C to 34 ° C. The cooling water that has been deprived of cold heat and has reached 34 ° C. is cooled again to 29 ° C. by the cooling tower 11A that cools using outside air at 27 ° C.

  The 32 ° C. cold water produced by the intermediate heat exchanger 11B is supplied to the heat exchanger 21 of the air conditioner 20. The heat exchanger 21 performs heat exchange between 40 ° C. return air in the server room M and 32 ° C. cold water. The cold water whose temperature has risen to 34 ° C. by this heat exchange is returned again to the intermediate heat exchanger 11B of the heat source device 11.

On the other hand, when the outside air wet-bulb temperature is 27 ° C., cooling tower 12A of the heat source apparatus 12 supplies the 29 ° C. cooling water to the condenser 12C ₁ of the refrigerator 12C. Condenser 12C _1, in order to cool the heat generated when liquefying refrigerant, use of this cooling water. The refrigerator 12 </ _b > C supplies the 17 ° C. cold water produced by the evaporator 12 </ _b > C ₂ to the heat exchanger 22 of the air conditioner 20. The heat exchanger 22 performs heat exchange between the precooled return air from the heat exchanger 21 and 17 ° C. cold water, and sends the 20 ° C. return air to the underfloor chamber 107 of the server room M. At the same time, the cold water whose temperature has risen to 20 ° C. by the heat exchange of the heat exchanger 22 is returned again to the intermediate heat exchanger 11B of the heat source device 11.

  By the way, when a malfunction occurs in one of the heat source device 11 and the heat source device 12 of the heat source facility 10, the valves 13A to 13D and the valves 14A to 14D are switched to perform the backup operation mode. If the heat source facility 10 includes a single heat source device and this device fails, the supply of cold water may stop. However, the heat source facility 10 includes the heat source device 11 and the heat source device 12 and continuously supplies cold water by entering the backup operation mode.

  Thus, according to this embodiment, the heat exchanger 21 is provided in front of the heat exchanger 22 of the air conditioner 20 to cool the return air in the server room M by precooling the high-temperature return air in the server room M. In doing so, excessive dehumidification of the server room M can be prevented.

  Moreover, according to this embodiment, since the heat source equipment 10 includes the heat source device 11 and the heat source device 12 to form a redundant system, even if a failure occurs in the heat source device 11 or the heat source device 12, a backup operation is performed. Depending on the mode, countermeasures are taken in accordance with the malfunction of the heat source device. Thereby, supply of the cold water with respect to the air conditioner 20 does not stop. Therefore, the reliability of the room temperature management of the server room can be improved.

  Moreover, according to this embodiment, the heat source device 11 cools the cold water returned from the heat exchanger 21 of the air conditioner 20 by free cooling. The latter heat source device 12 is operated in the cold season operation mode or the summer operation mode. However, in the summer, the heat exchanger 22 cools the return air precooled by the heat exchanger 21 of the air conditioner 20, so that heat exchange is performed. The rise in the temperature of the cold water from which cold heat has been taken away by the vessel 22 can be kept low. Thereby, the electrical energy consumed in the case of manufacture of the cold water by the heat source device 12 can be suppressed, and energy can be saved.

  For example, when the outdoor wet bulb temperature is distributed as shown in FIG. 9 (Tokyo case), when the cold season operation mode is used at 12 ° C. or lower, the heat source device 12 is used as the cold season operation mode. The possible period is ½ of a year, and energy saving is possible. In areas such as Hokkaido, setting the boundary between the cold season operation mode and the summer season operation mode to 12 ° C further increases the period of use of the heat source device 12 as the cold season operation mode, resulting in significant energy savings. Is possible.

  Further, according to this embodiment, even in the cold season, when the temperature of the return air rises due to a high load, cold water is produced in the summer operation mode, and even in the summer, the return is caused by a low load. When the temperature of the atmosphere is low, cold water is produced in the cold season operation mode, so it is possible to cope with changes in load.

  Furthermore, according to this embodiment, the heat exchanger 21 is provided in the front stage of the heat exchanger 22 of the air conditioner 20, and the high temperature return air in the server room M is precooled, whereby the temperature distribution is uneven (cooling unevenness). Can be prevented from occurring.

(Embodiment 2)
In the first embodiment, the return air in the server room M is cooled by one air conditioner 20. However, the number of racks that store servers may increase. In this embodiment, in order to cope with such a situation, as shown in FIG. 10, n air conditioners 20 _{1 to} 20 _n are used. In this embodiment, components that are the same as or the same as those in the first embodiment described above are denoted by the same reference numerals, and description thereof is omitted. The air conditioners 20 _{1 to} 20 _n are the same as the air conditioner 20 of the first embodiment.

Further, in this embodiment, in order to control the supply of cold water from the heat source unit 11 and the heat source unit 12, the valve _{13A 1 ~13D} 1 and valve _{14A 1 ~14D} 1, ···, valve _{13A n ~13D} n And valves 14A _{n to} 14D _n are used. These valves are the same as the valves 13A to 13D and the valves 14A to 14D of the first embodiment.

Thus, according to this embodiment, by increasing or decreasing the air conditioner 20 ₁ to 20 _n, it is possible to correspond to changes in the rack of the number of servers chamber M. Even if the heat source device 11 or the heat source device 12 breaks down, the valves 13A _{1 to} 13D ₁ and the valves 14A _{1 to} 14D ₁ ,..., The valves 13A _{n to} 13D _n and the valves 14A _{n to} 14D _n are switched. Thus, similar to the first embodiment, it is possible to easily cope with the problem.

(Embodiment 3)
In this embodiment, as shown in FIG. 11, the heat source devices 11 and 12 of the first embodiment use both the closed and open cooling towers 11A ₁₁ and 12A ₁₁ . In this embodiment, components that are the same as or the same as those in the first embodiment described above are denoted by the same reference numerals, and description thereof is omitted.

The cooling tower 11A ₁₁ includes a heat exchanger 11B ₁₁ . This cooling tower 11A ₁₁ is shown in FIG. The cooling tower 11A ₁₁ mainly includes a fan 11A ₁₁₁ and a sprinkling pipe 11A ₁₁₂ . Then, the watering position of sprinkling pipe _{11A 112,} heat exchanger _{11B 11} is installed. The cooling tower 11A ₁₁ causes the cooling water deprived of cold heat to flow to the heat exchanger 11B ₁₁ or to the water spray pipe 11A ₁₁₂ .

When cooling water is allowed to flow through the heat exchanger 11B ₁₁ , the cooling tower 11A ₁₁ sprays makeup water W supplemented from the outside onto the heat exchanger 11B ₁₁ by a pump (not shown). At this time, the fan 11A ₁₁₁ rotates, the heat exchanger 11B ₁₁ is cooled, and the cooling water is cooled. The cooling tower 11 </ b> A ₁₁ always stores an appropriate amount of makeup water W in the container U. Even if water supply from the outside is stopped by this appropriate amount of make-up water W, the cooling tower 11A ₁₁ can cool the heat exchanger 11B ₁₁ for a predetermined time in the same manner as before the water break. Even if the makeup water W runs out, the heat exchanger 11B ₁₁ can be cooled by the fan 11A ₁₁₁ of the cooling tower 11A ₁₁ . Such cooling is hermetic cooling using free cooling.

On the other hand, the cooling tower 11A ₁₁ stops spraying the makeup water W when the cooling water is allowed to flow through the sprinkler pipe 11A ₁₁₂ . The cooling tower 11 </ b> A ₁₁ sprays the cooling water from which the cold energy has been removed from the water spray pipe 11 </ b> A ₁₁₂ . At this time, the fan 11A ₁₁₁ rotates, a part of the cooling water evaporates, and the cooling water is cooled. Further, the cooling tower 11A ₁₁ takes in an amount of makeup water W corresponding to the evaporated cooling water. Such cooling is open-type cooling using free cooling.

Cold water pumps 11D ₁ and 11D ₂ and valves 11E _{11 to} 11E ₁₅ are connected to the cooling tower 11A ₁₁ and the heat exchanger 11B ₁₁ . That is, the heat exchanger _{11B 11} includes a return line _{11F 12} and the supply conduit _{11F 11} is connected. A cold water pump 11D ₂ is connected to the supply pipeline 11F ₁₁ . A supply conduit _{11F 11} on the upstream side of the cold water pump 11D _2, between the evaporator 11C ₂ are connected by branch conduit _{11F 13,} the valve _{11E 15} is connected to the branch line _{11F 13.}

The return line _{11F 12,} valve _{11E 13} is connected between the downstream side of the return line _{11F 12} of the valve _{11E 13} and the evaporator 11C ₂ are connected by a branch pipe _{11F 14.}

On the other hand, the container U (hereinafter simply referred to as "cooling tower _{11A 11")} of the cooling tower _{11A 11} between the condenser 11C ₁ and are connected by a circulation line _{11F 15,} the circulation line _{11F 15,} chilled water pumps 11D ₁ and valve 11E ₁₄ are connected. A circulation pipeline 11F ₁₅ upstream of the cold water pump 11D ₁ and a supply pipeline 11F ₁₁ upstream of the cold water pump 11D ₂ are connected by a branch pipeline 11F ₁₆ .

The condenser 11C _1, is connected circulation line _{11F 17,} the tip of the circulation pipe _{11F 17} is connected to the sprinkling pipe _{11A 112} by interposing a valve _{11E 11.} Between the circulation pipe _{11F 17} and heat exchanger _{11B 11} on the downstream side of the valve _{11E 11} is connected by a branch conduit _{11F 18,} the branch pipe _{11F 18,} the valve _{11E 12} is connected.

The heat source device 11 having such a configuration includes a cold season operation mode that is used in the season when the outdoor air wet bulb temperature is lower than 12 ° C, a summer season operation mode that is used during the season when the outdoor wet bulb temperature is higher than 12 ° C, and the cooling tower 11A. There are three operation modes: a water stop operation mode that is used when ₁₁ makeup waters W are stopped.

When the heat source device 11 enters the cold season operation mode, the cooling tower 11A11 is switched to hermetic cooling. At the same time, the heat source device 11 includes valves 11E11 to 11E15 and cold water pumps 11D1 and 11D2.
Valve 11E11, Valve 11E12 ... Closed Valve 11E13 ... Opened Valve 11E14, Valve 11E15 ... Closed Cold water pump 11D1 ... Off Cold water pump 11D2 ... Turned on. Accordingly, as shown in FIG. 13, the cold water from the heat exchanger 11B11 of the cooling tower 11A11 flows through the flow path FL31 by the cold water pump 11D2 and is supplied to the heat exchanger 21 of the air conditioner 20. That is, the heat source device 11 manufactures cold water using free cooling in the cold season operation mode.

When the heat source device 11 enters the summer operation mode, the cooling tower 11A11 is switched to open-type cooling. At the same time, the heat source device 11 includes valves 11E11 to 11E15 and cold water pumps 11D1 and 11D2.
Valve 11E11 ... Open Valve 11E12, Valve 11E13 ... Close Valve 11E14, Valve 11E15 ... Open Cold water pump 11D1 ... On Cold water pump 11D2 ... Turn on. Thereby, as shown in FIG. 14, the cooling water from the cooling tower 11A11 flows through the flow path FL32 by the cold water pump 11D1, and is used for cooling the condenser 11C1 of the refrigerator 11C. At the same time, the cold water cooled by the evaporator 11C2 of the refrigerator 11C flows through the flow path FL33 by the cold water pump 11D2 and is supplied to the heat exchanger 21 of the air conditioner 20. That is, in the summer operation mode, cold water is produced using free cooling and electric energy.

The heat source device 11 switches the cooling tower 11 </ b> A <b> 11 to hermetic cooling when in the water cutoff operation mode. At the same time, the heat source device 11 includes valves 11E11 to 11E15 and cold water pumps 11D1 and 11D2.
Valve 11E11 ... Closed Valve 11E12 ... Opened Valve 11E13 ... Closed Valve 11E14, Valve 11E15 ... Opened Chilled water pump 11D1 ... On Chilled water pump 11D2 ... Turned on. Thereby, as shown in FIG. 15, the cooling water from the heat exchanger 11B11 of the cooling tower 11A11 flows through the flow path FL34 by the cold water pump 11D1, and is used for cooling the condenser 11C1 of the refrigerator 11C. At this time, the replenishment water W of the cooling tower 11A11 is cut off, but the cooling tower 11A11 always stores an appropriate amount of the replenishment water W. With this appropriate amount of make-up water W, the cooling tower 11A11 can cool the heat exchanger 11B11 in the same manner as before the water shutoff for a predetermined time. Even if the makeup water W runs out, the heat exchanger 11B11 can be cooled by the fan 11A111 of the cooling tower 11A11. Thereby, the heat source device 11 can cope with water outage due to an earthquake or the like.

  On the other hand, the cold water cooled by the evaporator 11C2 of the refrigerator 11C of the heat source device 11 flows through the flow path FL35 by the cold water pump 11D2 and is supplied to the heat exchanger 21 of the air conditioner 20. That is, in the water cutoff operation mode, cold water is manufactured using free cooling and electric energy.

  The heat source device 12 is the same as the heat source device 11. That is, the heat source device 12 mainly includes a cooling tower 12A11, a heat exchanger 12B11, a refrigerator 12C, chilled water pumps 12D1 and 12D2, and valves 12E11 to 12E15. The refrigerator 12C includes a condenser 12C1 and an evaporator 12C2. ing. And the heat exchanger 12B11, the refrigerator 12C, the chilled water pumps 12D1, 12D2, the valves 12E11 to 12E15, the condenser 12C1 and the evaporator 12C2 of the refrigerator 12C are a supply pipeline 12F11, a return pipeline 12F12, a branch pipeline 12F13, 12F14, circulation pipeline 12F15, branch pipeline 12F16, circulation pipeline 12F17 and branch pipeline 11F18 are connected to each other.

  Similar to the heat source device 11, the heat source device 12 having such a configuration has three operation modes of a cold season operation mode, a summer season operation mode, and a water cutoff operation mode.

According to this embodiment, as in the first embodiment, excessive dehumidification of the server room M is prevented, high reliability for air conditioning of the server room M is established by a redundant system, and outside air heat is used. The load on the heat source device can be reduced and temperature unevenness can be prevented. Furthermore, according to this embodiment, even if the supplementary water W for the cooling towers 11A ₁₁ and 12A ₁₁ is shut off, the cold water is supplied to the air conditioner 20 by operating the heat source devices 11 and 12 in the water shutoff operation mode. It can be done continuously. Thereby, the reliability of an air-conditioning heat source system can be improved.

(Embodiment 4)
In this embodiment, the heat source facility 10 shown in FIG. 16 is used instead of the heat source facility 10 of the third embodiment. In this embodiment, components that are the same as or the same as those of the third embodiment described above are denoted by the same reference numerals, and the description thereof is omitted. The heat source facility 10 includes a heat source device 11 and the same heat source device 12 as in the third embodiment.

The heat source device 11 includes a cooling tower 11A ₁₁ , a heat exchanger 11B _11, and a cold water pump 11D ₂ . A heat exchanger _{11B 11} of the cooling tower _{11A 11} is conduit _{11F 22} supply and return pipe _{11F 21} is connected. The return line _{11F 22,} chilled water pump 11D ₂ are connected. The supply pipeline 11F ₂₁ and the return pipeline 11F ₂₂ are connected to the supply pipeline 15A and the return pipeline 15B, respectively. In the heat source device 11 having such a structure, the cooling tower 11A ₁₁ is always operated in the cold season operation mode throughout the four seasons.

According to this embodiment, as in the first embodiment, excessive dehumidification of the server room M is prevented, a high reliability for the air conditioning of the server room is established by a redundant system, and a heat source by using outside air heat The load on the device can be reduced and temperature unevenness can be prevented. Furthermore, according to this embodiment, even if the replenishment water W for the cooling towers 11A ₁₁ and 12A ₁₁ is shut off, the cold water for the air conditioner 20 is operated by operating the heat source device 11 and the heat source device 12 in the water shutoff operation mode. Supply can be continued. Thereby, the reliability of an air-conditioning heat source system can be improved. Furthermore, since the heat source device 11 is always operated in the cold season operation mode, it is possible to further enhance the energy saving effect.

(Embodiment 5)
In this embodiment, the heat source equipment 10 shown in FIG. 17 is used instead of the heat source equipment 10 of the first embodiment. In this embodiment, components that are the same as or the same as those in the first embodiment described above are denoted by the same reference numerals, and description thereof is omitted. The heat source facility 10 includes heat source devices 11 and 12. The heat source device 12 and the heat exchanger 22 are connected by a supply line 17A, and the heat exchanger 22 and the heat exchanger 21 are connected by a supply line 17B. The heat exchanger 21 and the heat source device 11 are connected by a return pipeline 17C, and the heat source device 11 and the heat source device 12 are connected by a return pipeline 17D.

The heat source unit 11, as shown in FIG. 18, the cooling tower 11A, the intermediate heat exchanger 11B, and mainly includes a cold water pump 11D _1. That is, the heat source device 11 has a configuration in which the refrigerator 11C, the cold water pump 11D ₂ , and the valves 11E _{1 to} 11E ₄ are omitted from the heat source device 11 of the first embodiment. Thereby, the heat source device 11 always cools the cooling water by free cooling throughout the four seasons.

  In the heat source device 11 of the heat source facility 10, the cold water that has flowed through the return pipe 17C and has been deprived of the cold by the air conditioner 20 is heat-exchanged by the cooling water cooled by the cooling tower 11A and the intermediate heat exchanger 11B. Thereby, the cold water from which the cold energy has been taken away by the air conditioner 20 is pre-cooled by the heat source device 11. The precooled cold water flows to the heat source device 12 through the return pipe 17D. In the heat source device 12, as in the first embodiment, the precooled cold water from the heat source device 11 is cooled in the cold season operation mode or the summer season operation mode and supplied to the supply line 17A.

Next, the operation of the air conditioning heat source system using the cooling tower according to this embodiment will be described. The cold water from which the cold air has been taken away by the air conditioner 20 is returned to the heat source device 11 by the cold water pump 11D ₂ of the heat source device 12. The heat source device 11 pre-cools the cold water from the air conditioner 20 by free cooling and sends it to the heat source device 12. The heat source device 12 cools the cold water from the heat source device 11 and supplies it to the air conditioner 20 in the cold season operation mode or the summer season operation mode according to the temperature of the outside air.

  In the air conditioner 20, cold water from the heat source device 12 is heat-exchanged with the return air pre-cooled by the heat exchanger 21 and the heat exchanger 22. Thereby, the return air cooled in advance by the heat exchanger 21 is further cooled. The cold water from which the cold heat has been taken away by the heat exchanger 21 is supplied to the heat exchanger 21. The heat exchanger 21 cools the high-temperature return air in the server room M using cold water from which cold heat has been removed.

  For example, when the temperature of the chilled water from the heat source device 12 is 17 ° C., the heat exchanger 22 cools the return air from the heat exchanger 21, and the heat exchanger 21 further cools the heat by the heat exchanger 22. The hot return air in the server room M is cooled by using the cold water that has been taken away. Thereby, the heat exchanger 21 returns the 37 ° C. cold water from which the cold energy has been removed to the heat source device 11.

  Thus, according to this embodiment, the heat exchanger 21 is provided in the front stage of the heat exchanger 22, and the heat exchanger 21 returns the high temperature of the server room M using the cold water that has been consumed by the heat exchanger 22. Precool yourself. Thereby, when the return air of the server room M is cooled, it is possible to prevent the server room M from being excessively dehumidified. Further, high reliability can be established for the air conditioning of the server room by the redundant system.

  Moreover, according to this embodiment, the heat source device 11 precools the cold water returned from the heat exchanger 21 of the air conditioner 20 by free cooling. The latter heat source device 12 is operated in the cold season operation mode or the summer operation mode. In particular, in the summer operation mode, the chiller 12C cools the cold water pre-cooled by the heat exchanger 21, so that the cold water generated by the heat source device 12 is cooled. It is possible to reduce the electric energy consumed during the manufacturing process and to save energy.

  Moreover, according to this embodiment, since the heat exchanger 21 of the air conditioner 20 precools the high-temperature return air using the cold water that has been consumed by the heat exchanger 22, it is possible to effectively use the cold water. To do.

  Furthermore, according to this embodiment, the heat exchanger 21 is provided in the front stage of the heat exchanger 22, and the heat exchanger 21 returns the high temperature of the server room M using the cold water that has been consumed by the heat exchanger 22. By precooling the air, temperature unevenness can be prevented.

  The embodiment of the present invention has been described in detail above, but the specific configuration is not limited to this embodiment, and even if there is a design change or the like without departing from the gist of the present invention, Included in the invention. For example, in each embodiment, the server room M of the data center is air-conditioned, but the present invention can be used for various facilities such as a semiconductor clean room. Moreover, although the switching of the pipeline is performed by the switching valve means, the switching may be performed by a combination of a small pump and a check valve for each pipeline. In this case, the check valve is opened when the pump is operating, and the heat medium is circulated, and the check valve is closed when the pump is stopped.

1 is a configuration diagram illustrating a configuration of an air conditioning heat source system using a cooling tower according to Embodiment 1. FIG. It is a block diagram which shows the structure of an air conditioner and a heat source system. It is a block diagram which shows the structure of a heat source apparatus. FIG. 4A is a diagram for explaining the operation of the open type cooling tower, and FIG. 4B is a diagram for explaining the operation of the closed type cooling tower. . It is explanatory drawing explaining a cold season operation mode. It is explanatory drawing explaining the outlet water temperature of a cooling tower. It is explanatory drawing explaining a summer driving | operation mode. It is explanatory drawing explaining the mode of opening and closing of each valve | bulb. It is a graph which shows the outdoor outdoor wet bulb temperature distribution. It is a block diagram which shows the structure of the air conditioner and heat source system by Embodiment 2. FIG. 6 is a configuration diagram showing a configuration of a heat source device according to a third embodiment. FIG. 6 is a schematic diagram showing an outline of a configuration of a cooling tower according to a third embodiment. 10 is an explanatory diagram for explaining a cold season operation mode according to Embodiment 3. FIG. FIG. 10 is an explanatory diagram for explaining a summer operation mode according to a third embodiment. It is explanatory drawing explaining the water cutoff operation mode by Embodiment 3. FIG. FIG. 6 is a configuration diagram illustrating a configuration of a heat source system according to a fourth embodiment. It is a block diagram which shows the structure of the air conditioner and heat source system by Embodiment 5. FIG. 10 is a configuration diagram showing a configuration of a heat source device according to a fifth embodiment. It is explanatory drawing explaining the conventional air conditioning system. It is explanatory drawing explaining the air conditioning system using free cooling. It is explanatory drawing explaining the air conditioning of the summer using free cooling. It is explanatory drawing explaining the air conditioning of the winter season using free cooling.

Explanation of symbols

10 Heat source equipment (heat source means)
11 Heat source device (first heat source device)
11D ₂ cold water pump (water supply means)
12 Heat source device (second heat source device)
12D ₂ cold water pump (water supply means)
20 Air conditioner (heat exchange means)
21 Heat exchanger (front heat exchanger)
22 Heat exchanger (the latter heat exchanger)

Claims (7)

Heat source means for cooling the heat source water with at least the former energy of the energy of the outside air and the energy such as electricity,
A heat exchanger having a two-stage configuration using heat from the heat source means, heat exchange means for exchanging heat between the heat source water and the return air from the air conditioning room;
Water supply means for circulating the heat source water between the heat exchange means and the heat source means;
An air-conditioning heat source system using a cooling tower. The heat source means includes a first heat source device that uses the energy of the outside air, and a second heat source device that switches between and uses the energy of the outside air or energy such as electricity according to the outside air temperature. The heat source water is cooled using the heat source device of 2;
The air conditioning heat source system using a cooling tower according to claim 1. The heat source means supplies heat source water from the first heat source device to the heat exchanger upstream of the heat exchange means, and supplies heat source water from the second heat source device to the heat exchanger downstream. To
The air conditioning heat source system using a cooling tower according to claim 2. The heat source means supplies the heat source water cooled by the first heat source device to the heat exchange means after being cooled by the second heat source device,
The heat exchanging means supplies the heat source water from the second heat source device of the heat source means to the subsequent heat exchanger, and the heat source water deprived of the cold by the latter heat exchanger is used for the heat exchanging of the previous stage. Supply to the vessel,
The air conditioning heat source system using a cooling tower according to claim 2. The second heat source device of the heat source means cools the heat source water using the energy of the outside air when the outside air wet bulb temperature is lower than a predetermined value, and if the outside air wet bulb temperature is higher than the predetermined value, the energy such as electricity To cool the heat source water,
The air conditioning heat source system using a cooling tower according to any one of claims 2 to 4. When the temperature of the return air is low due to a low load, the second heat source device of the heat source means cools the heat source water using the energy of the outside air, and when the temperature of the return air is high due to a high load, the energy such as electricity To cool the heat source water,
The air conditioning heat source system using a cooling tower according to any one of claims 2 to 5. The first and second heat source devices are switched between a closed type that cools the heat source water by sprinkling the supplied water and an open type that cools the heat source water by evaporation of the heat source water to cool the heat source water,
When the supply of water to at least one of the first and second heat source devices stops, the heat source device that has been shut off cools the heat source water using hermetic cooling and energy such as electricity,
The air conditioning heat source system using a cooling tower according to any one of claims 2 to 6.

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