JP2010223487A - Air conditioning system in building where many heat generating apparatuses are installed - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To solve a problem wherein in a conventional air conditioning system in a data center etc., since a value of a use temperature difference is not extremely large, the air conditioning system requires large air blowing amount, increase in the size of air conditioning equipment and large carrying power, leading to increase in running cost. <P>SOLUTION: In this air conditioning system in a building where many heat generating apparatuses are installed, an air conditioning air passage 5 is constituted so that air conditioning air from an air conditioner 6 is made to pass through the plurality of heat generating apparatuses 2a, 2b, 2c in series, an air return route 11 is constituted from the downstream side from the air conditioning air passage 5 to the air conditioner 6 and a control means for controlling the air conditioning air from the air conditioner 6 is constituted so that the temperature of the air conditioning air on the upstream side of the heat generating apparatus 2c located on the most downstream side becomes an upper limit temperature, in the building where the many heat generating apparatuses are installed. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to an air conditioning system in a building in which a large number of heat generating devices are installed, such as a large-scale server room or data center.

  In a large-scale server room or data center, in order to stably operate a large number of servers mounted in a server rack or the like, an air conditioning system that efficiently and reliably cools a server that is a heat generating device is necessary.

  In a conventional data center, for example, a server rack equipped with a server such as a blade server is installed on a free access floor with a height of about 600 mm, and conditioned air from the air conditioner passes through the space below the free access floor. Floor blowing type air conditioning systems that cool the servers by supplying them to the server rack are the mainstream.

  For example, in the air conditioning system described in Patent Document 1, the conditioned air from the air conditioner a is blown to the under floor space of the free access floor c of the server room b as shown in FIG. The server f is blown into each server rack d from the air outlets e formed in the lower part of the plurality of server racks d arranged in a row to cool the server f, and the conditioned air heated thereby is supplied to the upper part of the server rack d. It is made to discharge | emit and return to the air conditioner a through upper ceiling vicinity. Further, in the air conditioning system described in Patent Document 2, an air conditioner room g is formed adjacent to a server room b in which server racks d mounted with servers are installed vertically and horizontally as shown in FIG. After the conditioned air is blown into the under floor space of the free access floor c, the air is blown out from the outlet e configured on the side of each server rack d, and flows into the server rack d from the side to cool the server. The heated conditioned air is discharged from the side opposite to the server rack d, and is returned to the air conditioner a in the air conditioner room g through the space in the ceiling h of the room c.

  In the conventional air conditioning system described above, the conditioned air is supplied in parallel to a large number of server racks installed in the server room, and the use temperature difference is not so large. A small amount of outside air is introduced for maintenance personnel.

JP-A-8-303815 JP 2008-2690 A

  As described above, a conventional air conditioning system in a data center or the like has a large air flow rate because the difference in use temperature is not so large, and thus the air conditioning equipment is also large, and the running power is large because the conveyance power is large.

  In addition, since a free access floor with a height of about 600 mm is used, the floor height is increased, the volume of the floor is reduced, and the floor area ratio is not effectively used.

  In addition, since data centers and the like are cooled annually, there is a possibility that the use period of natural energy can be extended, but there have been few examples of active use in the past.

  The present invention aims to solve the above-described problems.

  In order to solve the above-described problems, in the present invention, in a building where a large number of heat generating devices are installed, an air conditioning air passage is configured so that conditioned air from an air conditioner passes through a plurality of heat generating devices in series, and air conditioning is performed. Configure an air recirculation path from the downstream side of the air passage to the air conditioner, and supply the conditioned air from the air conditioner so that the conditioned air temperature on the upstream side of the heating device on the most downstream side of the conditioned air passage becomes the upper limit temperature. We propose an air conditioning system that constitutes the control means to control.

  According to the present invention, in the above configuration, the air conditioner proposes an air conditioning system that can supply low-temperature conditioned air having a large difference from the upper limit temperature by serial operation of the refrigerator.

  The present invention also proposes an air conditioning system having an auxiliary air conditioner installed in the middle of the air conditioning air passage in the above configuration.

  In the present invention, the conditioned air passage is configured in the vertical direction in the above configuration, and a plurality of heat generating devices are spaced apart in the height direction by a floor material having air permeability in the vertical conditioned air passage. Propose the arranged air conditioning system. In addition, in this configuration, an air conditioning system is proposed in which the floor material having air permeability is grating. Further, in this configuration, the heat generating device is configured to allow the conditioned air to pass in the horizontal direction, and the intake side and the exhaust side of the heat generating device are arranged on the opposite side on the opposite floor, and the floor portion corresponding to the exhaust side of the heat generating device is provided. Proposed is an air conditioning system that is configured to be non-breathable to form a zigzag conditioned air passage and a partition for allowing all of the conditioned air to pass through a heat-generating device.

  Further, the present invention proposes an air conditioning system in which the conditioned air passage is configured in the lateral direction and a plurality of heat generating devices are arranged in the lateral conditioned air passage at intervals in the lateral direction. In addition, in this configuration, an air conditioning system is proposed in which a blow-off is arranged upstream or downstream of the conditioned air passage.

  Moreover, in this invention, the air conditioning system which comprised the external air intake system which takes in external air in a building in the above structure is proposed. And in this structure, the air-conditioning system which comprised the dehumidification part for dew condensation prevention in the external air intake system is proposed.

  Moreover, in this invention, the air conditioning system which comprised the air cooling system which cools the air of the upper part in a building with a total heat exchanger with external air in the above structure is proposed. In addition, in this configuration, an air conditioning system is proposed in which a cooling unit by a cool pit is configured on the downstream side of the total heat exchanger of the air cooling system.

  In the air conditioning system of the present invention, the conditioned air for cooling from the air conditioner, that is, the cool air, sequentially passes through a plurality of heat generating devices arranged along the air conditioned air passage in order to cool each heat generating device. As such, it is heated and recirculates from the downstream side of the conditioned air passage to the air conditioner via the air recirculation path.

  At this time, by controlling the conditioned air from the air conditioner by the control means so that the conditioned air temperature on the upstream side of the heating device on the most downstream side of the conditioned air passage becomes the upper limit temperature, In addition, it is possible to reliably use conditioned air at a temperature required for predetermined cooling.

  In the present invention described above, when the upper limit air-conditioning air temperature is controlled to be equal to, for example, the conventional air-conditioning air temperature, the temperature of the air-conditioning air from the air conditioner to the most upstream heating device is reduced as much as possible. Therefore, the use temperature difference can be increased, so that the amount of blown air can be reduced, the conveyance power can be reduced, and the air conditioner can be downsized. Further, it is possible to reduce the amount of water supplied from the refrigerator to the cold water coil of the air conditioner. From these facts, in the present invention, energy saving can be achieved by reducing the conveyance power.

  The air conditioner can easily supply low-temperature conditioned air having a large difference from the above-described upper limit temperature by serial operation of the refrigerator.

  If the number of heat generating devices arranged along the conditioned air passage is large, an auxiliary air conditioner, such as a booster coil and a booster fan, is installed in the middle of the conditioned air passage to generate heat most downstream of the conditioned air passage. It is possible to reliably supply conditioned air having a temperature required for predetermined cooling up to the equipment.

  If the air-conditioning air passage is configured in the vertical direction and a plurality of heat generating devices are arranged in the vertical air-conditioning air passage with an air-permeable flooring at an interval in the height direction, the rising airflow due to the temperature difference Can be used for transporting conditioned air, and transport power can be reduced. In addition, by cooling the air in the upper part of the building with natural energy or the like, the cold draft can be used for air circulation.

  In this case, the intake side and the exhaust side of the heat generating device are arranged on the opposite side on the adjacent floor, and the floor portion corresponding to the exhaust side of the heat generating device is configured to be non-breathable to form a zigzag conditioned air passage, A partition can be provided to allow all of the conditioned air to pass through the heating device.

  When grating is used as a flooring material having air permeability, the volume of the building can be effectively used because it is not included in the total building area.

  The conditioned air passage is configured in the lateral direction, and a plurality of heat generating devices can be arranged in the lateral conditioned air passage at intervals in the lateral direction. In this configuration, on the downstream side of the conditioned air passage. By arranging the blow-through, the rising airflow due to the temperature difference can be used for the conveyance of the conditioned air, and the conveyance power can be reduced.

  In the present invention, an outside air intake system that takes outside air into the building is configured, an air cooling system that takes in the air in the upper part of the building, passes through the total heat exchanger with the outside air, and enters the building, or the latter By configuring the cooling section by the cool pit, it is possible to effectively use natural energy. By effectively using natural energy in this way, the cooling load in the system can be reduced and energy saving can be achieved.

  Also, in the outside air intake system, it is possible to prevent the occurrence of condensation by configuring a dehumidifying part for preventing condensation and operating it when there is a possibility that condensation will occur in the building depending on the humidity of the outside air. it can.

  In the air conditioning system of the present invention, all the conditioned air flowing through the conditioned air passage can be passed through the heat generating device, or a part of the conditioned air flowing through the conditioned air passage can be passed through the heat generating device. You can also

It is typical system explanatory drawing which shows the whole structure of 1st Embodiment of the air conditioning system of this invention. It is typical system explanatory drawing which shows the whole structure of 2nd Embodiment of the air conditioning system of this invention. It is typical system explanatory drawing which shows the whole structure of 3rd Embodiment of the air conditioning system of this invention. It is typical system explanatory drawing which shows the whole structure of 4th Embodiment of the air conditioning system of this invention. It is typical system explanatory drawing which shows an example of the conventional air conditioning system in a data center. It is typical system explanatory drawing which shows the other example of the conventional air conditioning system in a data center.

Next, embodiments of the present invention will be described with reference to the accompanying drawings.
First, FIG. 1 shows a first embodiment of an air conditioning system of the present invention.
Reference numeral 1 denotes a data center building, and a number of server racks 2 in which servers are mounted are installed in the building 1. The building 1 is partitioned on the left and right sides by a nitrogen fire-extinguishing partition wall 4, and the server rack 2 is divided into a plurality of levels in the vertical direction by a grating 3 as a floor material having air permeability in each partition, in this case 3 It is installed on the left and right sides at intervals. A plurality of server racks 2 are also arranged in the depth direction in the figure. As shown in the figure, the three-stage server racks 2 in the vertical direction are distinguished from each other by adding subscripts a, b, and c from the bottom.

  As described above, in this embodiment, since the floor for installing the server racks 2 in a plurality of stages in the vertical direction is configured by the grating 3, the floor area of the building 1 is not included in the total building area. It can be used and the construction cost can be reduced.

  The server racks 2a, 2b, 2c installed in three vertical stages are surrounded by a common vertical air-conditioning air passage 5 for preventing the diffusion of the air-conditioning air. The upper part of the air passage 5 is open to the upper space in the building 1, and the air conditioner 6 is installed in the lower part. At this time, the conditioned air passage 5 may be configured to surround the periphery of each server rack 2 at the same height, or may be configured to surround the periphery of a plurality of adjacent server racks 2. In this embodiment, the air-conditioning air passage 5 uses a cardboard air-conditioning duct constructed of a plate material in which aluminum foil is laminated on both surfaces of a corrugated cardboard having a hollow structure.

  Here, the air conditioner 6 is composed of a chilled water coil 6a and a fan 6b leading to the heat source device 7, and the heat source device 7 is an absorption chiller 7a and a turbo chiller connected in series on the discharge side thereof. 7b and a heat storage tank 7c using nighttime power.

  A flow control valve 9 is provided in the cold water pipe 8 extending from the turbo refrigerator 7b to the cold water coil 6a, and a temperature sensor 10 is provided upstream of the third-stage server rack 2c on the most downstream side in the conditioned air passage 5. The flow rate control valve 9 controls the temperature of the upstream side of the server rack 2c in the conditioned air passage 5 detected by the temperature sensor 10 so that the temperature does not exceed the set upper limit temperature. The supply amount of the cold water and the air volume of the fan 6b are controlled.

  In the building 1, a space other than the vertical conditioned air passage 5 formed on the left and right sides of each section is configured as an air return path 11, and a return fan 12 is provided in the upper part. Further, a radiation panel 13 of a radiation air conditioning system is provided above the air conditioning air passage 5 and in the vicinity of the ceiling of the building 1, and further, an auxiliary chilled water coil 14 is provided on the air recirculation path 11 side, and a drain pan 15 is provided below the auxiliary cooling water coil 14. Is provided. The radiant panel 13 can prevent water leakage by holding the inside of the cold water pipe at a negative pressure using a vacuum roots refrigerator. An exhaust section 16 provided with a fan 16a and a motor damper 16b is formed on the ceiling of the building 1 above the air reflux path 11. Further, an information system wiring rack 17a and a power system wiring rack 17b are installed in the space as the air recirculation path 11, and the former indicates the wiring with white circles and the latter displays the wiring with black circles.

  Next, reference numeral 18 denotes an outside air intake system. The outside air intake system 18 sucks outside air from the outside air inlet 19 of the building 1 by a fan 20 and passes through a dehumidifier 21 that operates as necessary. It is the structure introduced into the lower part of the building 1. Reference numeral 22 denotes an air cooling system having a structure in which air in the upper part of the building 1 is taken in by a fan 23 and introduced into the lower part of the building 1 through a total heat exchanger 24 with outside air. When the pit 25 can be used, the cooling unit can be configured by passing the cool pit 25 on the downstream side of the total heat exchanger 24 of the air cooling system 22. As shown in the figure, the air cooling system 22 can also be provided with a dehumidifying device 26 to further prevent condensation. As these dehumidifiers 21 and 26, a dehumidifier using an air conditioner, a cooling coil, or an adsorbent such as silica gel can be used. Reference numeral 27 denotes an outside air system in which the outside air taken in from the outside air inlet 19 is discharged from the exhaust port 28 through heat exchange with the air cooling system 22 in the total heat exchanger 24. Further, an outer heat insulating material 30 is applied to the outer peripheral wall 29 of the building 1 and a pipe 31 is embedded. The pipe 31 and the pipe 32 of the radiant panel 13 use geothermal heat and free cooling as heat source water. It is configured to flow cold water using a refrigerator, ice storage, etc. Further, in the figure, reference numeral 33 denotes a damper with a piston releaser, and reference numeral 34 denotes a motor damper.

  In the above configuration, the 17 ° C. chilled water is first cooled to 10 ° C. by the absorption refrigeration machine 7a, then introduced to the turbo chiller 7b connected in series and cooled to 3 to 5 ° C. Is supplied to the cold water coil 6a. The supply amount of the cold water supplied from the turbo refrigerator 7b to the cold water coil 6a through the cold water pipe 8 and the air volume of the fan 6b are determined by the temperature of the conditioned air upstream of the server rack 2c in the conditioned air passage 5 as described above. Control is performed so as not to exceed the set upper temperature limit. This upper limit temperature is set to 22 ° C., which is the temperature of the conditioned air supplied to the server rack in the conventional air conditioning system, for example.

  The ambient warm air, for example, 27 ° C. to 28 ° C. air is cooled to 10 ° C. by the cold water of 3 ° C. to 5 ° C. supplied to the cold water coil 6a, and blown out by the fan 6b. Supplied as conditioned air at 12 ° C upstream.

The 12 ° C. conditioned air that has passed through the grating 3 and has flowed into the server rack 2a is used to cool the mounted server, the temperature rises to 17 ° C., flows out of the server rack 2a, and then the grating 3 And flows into the second-stage server rack 2b.

  In the server rack 2b, the temperature is increased from 17 ° C. to 22 ° C. by exchanging heat with the server, and the conditioned air flowing out of the server rack 2b then passes through the grating 3 and flows into the uppermost server rack 2c. To do.

  At this time, the temperature of the conditioned air flowing out from the server rack 2b is monitored by the temperature sensor 10, and the conditioned air is controlled by the supply amount of cold water and the air volume of the fan 6b so that the temperature does not exceed the upper limit temperature. Therefore, the uppermost server rack 2c on the most downstream side of the air-conditioning air passage 5 is supplied with air-conditioning air, for example, 22 ° C., which is the supply temperature in the conventional air-conditioning system. Can be cooled to. In this control, the conditioned air is controlled to 22 ° C. ± 2 ° C., for example.

  In this way, heat is exchanged with the server in the server rack 2c, the temperature rises from 22 ° C. to 27 ° C. to 28 ° C., and the conditioned air flowing out of the server rack 2c flows from the downstream end of the conditioned air passage 5 to the building 1 It flows into the upper space. The warm air that has flowed out into the upper space is sucked by the reflux fan 12, reaches the upper side of the air reflux path 11, and returns to the lower space of the building 1 through the air reflux path 11.

  At this time, in this embodiment, warm air of 27 ° C. to 28 ° C. flowing out into the upper space is radiatively cooled by the radiating panel 13 and is cooled through the auxiliary chilled water coil 14, for example, at a temperature of about 24 ° C. Therefore, a cold draft is generated and the reflux through the air reflux path 11 is promoted, so that the power required for the reflux by the fan 12 can be reduced. Further, by providing the information system wiring rack 17a and the power system wiring rack 17b in the space constituting the air recirculation path 11, the heat generated in these can be removed and the reflux can be performed smoothly. In addition, when the said radiation panel 13 cannot be installed, the auxiliary | assistant chilled water coil 14 can perform the above-mentioned reflux promotion effect | action only.

  As described above, in the present invention, even when the upper limit temperature of the conditioned air supplied to the server rack 2 is adjusted to, for example, about 22 ° C., which is the same as the conventional conditioned air temperature, the conditioned air passage 5 from the air conditioner 6. The temperature of the conditioned air to the most upstream server rack 2a can be lowered as much as possible, for example, about 12 ° C., so that the difference in use temperature can be made larger than before. It is possible to reduce the amount of blown air and reduce the conveyance power, and it is possible to reduce the size of the air conditioner 6 itself. Thus, energy saving and cost reduction of the air conditioning system can be achieved.

  The air conditioner 6 can easily supply conditioned air at a temperature lower than that of the prior art by using low-temperature cold water obtained by serial operation of the refrigerators such as the absorption refrigerator 7a and the turbo refrigerator 7b. . In addition, when the load of the server as the heat source device is small, it is possible to stop any one of the refrigerators and perform the independent operation.

  In this embodiment, in addition to the above operation, the outside air intake system 18 sucks outside air from the outside air inlet 19 of the building 1 and introduces it into the lower part of the building 1 or the air cooling system 22. The air in the upper part of the building 1 is taken in and introduced into the lower part of the building 1 through the total heat exchanger 24 with the outside air, or the pipe 30 of the peripheral wall part of the building 1 and the pipe 31 of the radiation panel 13 are subjected to geothermal heat. By flowing cold water by use, free cooling, refrigerator, ice heat storage, etc., natural energy can be used effectively to reduce the cooling load and save energy. Since data centers and the like are cooled annually, it is possible to set a longer period for using natural energy in this way, and the effect of reducing the cooling load and saving energy is great. In addition, when supplying outside air into the building 1 by the outside air intake system 18, the amount of air can be balanced by opening the motor damper 16b and discharging warm air inside the building 1 by the fan 16a. . Further, in taking outside air into the building 1 by the outside air intake system 18, it is possible to prevent dew condensation inside the building 1 by operating the dehumidifying device 21 according to the humidity condition of the outside air.

Next, FIG. 2 shows a second embodiment of the air conditioning system of the present invention.
In the second embodiment, as in the first embodiment, the building 1 is partitioned on the left and right sides by the nitrogen fire extinguishing section wall 4, and the server rack 2 has air permeability in each section. The grating 3 as a flooring material is installed in three steps in the vertical direction and at left and right sides at intervals, and the air conditioning system has the same elements as in the first embodiment, so the first embodiment The same reference numerals are given to the same elements in FIG.

In this embodiment, the configuration of the conditioned air passage 5 is made different on the left and right sides partitioned by the nitrogen fire extinguishing partition wall 4.
First, in the right section, the conditioned air passage 5 is configured as a space between the nitrogen fire extinguishing section wall 4 and the peripheral wall 29 of the building 1 and the partition wall 35 of the air recirculation path 11. 2 is configured to flow from the lower side to the upper side in the space in which the server 2 is installed, and a part thereof passes through the server rack 2. This configuration can be applied to a case where a blank panel closes a portion of the unused space in the server rack 2 on the intake side.

  Next, in the left compartment, similarly to the right compartment, the conditioned air passage 5 is formed in a space between the nitrogen fire extinguishing compartment wall 4 and the peripheral wall 29 of the building 1 and the partition wall 35 of the air return path 11. However, the intake side and the exhaust side of the server rack 2 are arranged opposite to each other on the adjacent floors, and the zigzag conditioned air passage 5 is configured by making the floor portions corresponding to those exhaust sides non-breathable, Furthermore, partitions 36 and 37 for allowing all of the conditioned air to pass through the server rack 2 are configured. That is, in this embodiment in which the grating 3 is used as a flooring material, the rubber mat 38 is laid on the corresponding portion of the grating 3 so as to be non-breathable. Then, by the partition 36 provided on the upper side of the intake side of the server rack 2 and the partition 37 provided on the upper side of the exhaust side, all of the conditioned air that has flowed into the intake side via the grating 3 flows into the server rack 2, and All of the conditioned air flowing out from the exhaust side of the server rack 2 is made to flow into the intake side of the server rack 2 on the upper floor through the adjacent upper floor grating 3. This configuration can be applied when there is an opening margin in the server rack 2. The partition wall 35 and the partitions 36 and 37 can be elements of a cardboard air conditioning duct.

  Further, in this embodiment, in the first embodiment, the pipe 31 embedded in the peripheral wall 29 of the building 1 is provided inside the peripheral wall 29 to be configured in the conditioned air passage 5. .

Next, FIG. 3 shows a third embodiment of the air conditioning system of the present invention.
Reference numeral 101 denotes a data center building. This building 101 is composed of a plurality of floors with a void slab as a floor 102, in this case, from the second floor to the sixth floor, and the first floor to the fifth floor are the installation floors of the server rack 103. At the same time, the server rack 103 is not installed on the sixth floor, and the air passage 104 is configured.

  On the central side in the left-right direction of the building 1, there is an atrium 105 extending from the first floor at the bottom to the sixth floor at the top. An air vent 107 provided with a smoke-proof fire-proof damper 106 is provided.

  A free access floor 108 is provided on the first to fifth floors 102, and the server rack 103 is installed thereon. The free access floor 108 is like a free access floor in a conventional air conditioning system. In addition, the air-conditioning air is not supplied to the lower space and is used as a storage location for the information system wiring rack 109a, so the height is about 200 to 300 mm, which is 1/3 of the height of the conventional free access floor. The floor height can be reduced. In this way, the volume ratio can be used effectively and the construction cost can be reduced.

  On the free access floor 108 on the left and right sides of each floor, a plurality of, in this case, three server racks 103 are installed at intervals in the left-right direction. These three server racks 103 are distinguished from each other by adding a, b, c suffixes from the end of the floor 102 toward the blow-through 105 for convenience.

  These three server racks 103a, 103b, and 103c are surrounded by a common left and right conditioned air passage 110 for preventing the diffusion of conditioned air. While installing the air conditioner 111, the handrail 112 which can ventilate is provided in the atrium 105 side. Further, a power supply system wiring rack 109b is installed above the conditioned air passage 110. In the figure, the information system wiring rack 109a displays wiring with white circles, and the power system wiring rack 109b displays wiring with black circles.

  As in the first embodiment, the air conditioner 111 includes a cold water coil 111a and a fan 111b that reach the heat source device 113, and the heat source device 113 is connected to the absorption refrigerator 113a and its discharge side. It is composed of a turbo refrigerator 113b connected in series and a heat storage tank 113c using nighttime power. The chilled water pipe 114 extending from the turbo refrigerator 113b to the chilled water coil 111a of each air conditioner 111 is provided with a flow control valve (not shown), and at the most downstream side, that is, on the blowout 105 side in the conditioned air passage 110. A temperature sensor 115 is provided on the upstream side of the server rack 103c, and the temperature on the upstream side of the server rack 103c in the conditioned air passage 110 detected by the temperature sensor 115 does not exceed a set upper limit temperature (22 ° C.). Thus, the supply amount of cold water and the air volume of the fan 111b are controlled. In this embodiment as well, the air-conditioned air passage 110 uses a cardboard air-conditioning duct constructed of a plate material in which aluminum foil is laminated on both surfaces of a hollow cardboard.

  As described above, the sixth floor of the building 101 is configured as the air passage 104, the fan 116 is provided above the blow-through 105 reaching the air passage 104, and the auxiliary chilled water coil 117 is provided at the end of the air passage 104. Is provided.

  Furthermore, an outside air intake system 120 that draws in outside air from the outside air inlet 119 of the building 1 by the fan 118 and introduces the air into the end side of the air passage 104 at the top of the building 101, and air at the center of the air passage 104. Is cooled by the suction force of the fan 121 and is introduced to the end side of the air passage 104 through the total heat exchanger 122 and the cool pit 123 with the outside air. Reference numeral 125 denotes an outside air system in which the outside air taken in from the outside air inlet 119 is heat-exchanged with the air cooling system 124 in the total heat exchanger 122 and discharged from the exhaust port 126.

  Similar to the first and second embodiments, a dehumidifier 127 is provided in the outside air intake system 120 in order to prevent condensation in the building 101 due to humidity in the outside air. Similarly, the air cooling system 124 is also provided with a dehumidifying device 128. Further, a water spray type air heat exchanger 129 is provided to efficiently cool the air in the outside air intake system 120 and the air cooling system 124. In addition, an outer heat insulating material 131 is applied to the outer peripheral wall 130 of the building 1 and a pipe 132 is embedded in the outer wall 130. The pipe 132 and the auxiliary chilled water coil 117 use geothermal heat, free cooling, and refrigeration as heat source water. It is configured to flow cold water from the machine and ice heat storage. Reference numeral 133 denotes a motor damper.

  In the above configuration, in the heat source device 113, the 17 ° C. cold water is first cooled to 10 ° C. by the absorption refrigerator 113a and then introduced into the serially connected turbo refrigerator 113b to 3 ° C. to 5 ° C. It is cooled and supplied to the cold water coil 111a of each air conditioner 111 through the cold water pipe 114. As described above, the supply amount of the cold water supplied to the cold water coil 111a and the air volume of the fan 111b are the upper limit temperature set by the temperature of the conditioned air upstream of the server rack 103c in the conditioned air passage 110 as described above. For example, it is controlled not to exceed 22 ° C.

  Thus, the ambient warm air, for example, 27 ° C. to 28 ° C. air is cooled to 10 ° C. by the cold water of 3 ° C. to 5 ° C. supplied to the cold water coil 111a, and blown out by the fan 111b as 12 ° C. conditioned air. It is supplied to the side surface of the most upstream server rack 103a.

  The 12 ° C. conditioned air that has flowed into the inside from the side surface of the server rack 103a is used to cool the mounted server, the temperature rises to 17 ° C., flows out from the downstream side surface of the server rack 103a, and then enters the space. And then flows from the side into the second server rack 103b.

  In the server rack 103b, the temperature rises from, for example, 17 ° C. to 22 ° C. by exchanging heat with the server, and the conditioned air flowing out from the downstream side surface then flows into the most downstream server rack 103c from the side surface. .

  At this time, the temperature of the conditioned air flowing out from the server rack 103b and flowing into the next server rack 103c is monitored by the temperature sensor 115, and the supply amount of the cold water and the fan are set so that the temperature does not exceed the upper limit temperature. Since the conditioned air is controlled by the air volume of 111b, in the server rack 103c on the most downstream side of the conditioned air passage 5, conditioned air of, for example, 22 ° C., which is the supply temperature in the conventional air conditioning system, is supplied. The mounted server can be reliably cooled. As in the first and second embodiments, the conditioned air is controlled to 22 ° C. ± 2 ° C., for example, in this control.

  In this way, in the server rack 103c, the temperature is increased from 22 ° C. to 27 ° C. to 28 ° C. by exchanging heat with the server, and the conditioned air flowing out of the server rack 103c flows from the downstream end of the conditioned air passage 110 to the building 101. , And the interior of the blow-through 105 is lifted by the draft action and the suction force of the fan 116 to reach the air passage 104 on the uppermost floor of the building 101.

  Warm air of about 27 ° C. to 28 ° C. flowing out from the upper part of the blow-through 105 into the air passage 104 by the fan 116 flows from the center side to both ends through the air passage 104 and is cooled to about 24 ° C. through the auxiliary chilled water coil 117. Then, the air reaches the vent 107 and descends from the top floor through the vent 107 on each floor, and is sucked and returned to the fan 111b of the air conditioner 111 on each floor. Accordingly, the air path from the top floor through the vent 107 on each floor is used as the air recirculation path 134. As described above, the warm air of about 27 ° C. to 28 ° C. flowing out into the air passage 104 is cooled to about 24 ° C. through the auxiliary chilled water coil 117, so that a cold draft is generated. Since the reflux is promoted, the power required for the reflux by the fans 116 and 111b can be reduced.

  As described above, also in the case of the third embodiment, in the case where the upper limit temperature of the conditioned air supplied to the server rack 2 is adjusted to, for example, about 22 ° C. equivalent to the conventional conditioned air temperature, The temperature of the conditioned air from the air conditioner 111 to the server rack 103a on the most upstream side of the conditioned air passage 110 can be reduced as much as possible, for example, 12 ° C. Since the air flow can be increased, the amount of blown air can be reduced, the conveyance power can be reduced, and the air conditioner 111 itself can be downsized.

  As described above, the air conditioner 111 easily supplies conditioned air at a temperature lower than that of the prior art by using low-temperature cold water obtained by serial operation of the refrigerators such as the absorption refrigerator 113a and the turbo refrigerator 113b. be able to.

  In the third embodiment, the outside air intake system 120 takes in the outside air drawn in from the outside air inlet 119 of the building 1 and the air cooling system 124 takes in warm air at the center side in the upper part of the building 1 to By introducing the air cooled through the total heat exchanger 122 to the end side of the air passage 104 at the top of the building 101, the above-described air recirculation can be promoted. At this time, the dehumidifying device 127 provided in the outside air intake system 120 can prevent the occurrence of condensation by operating when there is a possibility that condensation occurs in the building depending on the humidity of the outside air. Similarly, by operating the dehumidifying device 128 provided in the air cooling system 124 as necessary, it is possible to more reliably prevent the occurrence of dew condensation. Further, since the water spray type air heat exchanger 129 is provided, the air in the outside air intake system 120 and the air cooling system 124 can be efficiently cooled.

  In addition to these, natural water can be effectively used to reduce cooling load and save energy by flowing cold water from the geothermal use, free cooling, freezer, ice storage, etc. through the pipe 131 embedded in the peripheral wall of the building 101. Can be achieved. Since data centers and the like are cooled annually, it is possible to set a longer period for using natural energy in this way, and the effect of reducing the cooling load and saving energy is great. When the outside air is supplied into the building 1 by the outside air intake system 120, the motor damper 136 provided at the exhaust port 135 formed on the extension of the blow-through 105 is opened, and the warm air in the upper part of the building 1 is opened by the fan 116. By discharging the air, the amount of air can be balanced.

Next, FIG. 4 shows a fourth embodiment of the air conditioning system of the present invention.
In the fourth embodiment, as in the third embodiment, the building 101 is configured from the second floor to the sixth floor with the void slab as the floor 102, and the server rack 103 is installed from the first floor to the fifth floor. In addition to the floor, the server rack 103 is not installed on the sixth floor, and is configured as an air passage 104. In addition, an atrium 105 extending from the lowest first floor to the uppermost sixth floor is formed on the center side in the left-right direction of the building 1, and on the left and right end sides of the floor 102 on the second to sixth floors. Is provided with a vent 107 provided with a smoke and fire damper 106. Since this fourth embodiment has the same configuration as that of the third embodiment including the air conditioning system, the same reference numerals are given to the elements in the drawing similar to those of the third embodiment. A duplicate description is omitted.

  First of all, in this embodiment, unlike the third embodiment, the air conditioner 111 is arranged on the side of the atrium 105, and the side of the atrium 105 is used as the air recirculation path 134 and the left and right end sides of the building 101 are used. The space that continues up and down by the air vent 107 is configured as a space for raising the conditioned air heated by heat exchange with the server rack 103. Accordingly, the fan 116 is configured to eject air below the blow-through 105.

  And on the right side of the blow-through 105 in the figure, three server racks 103a, 103b, 103c are arranged in the conditioned air passage 110 in the space direction on the right end side of the floor 102 as in the third embodiment. Further, on the left side of the blow-through 105 in the drawing, six server racks 103 a, 103 b, 103 c, 103 d, 103 e, 103 f are arranged in the conditioned air passage 110 in the space direction on the left end side of the floor 102. An auxiliary air conditioner 137 including a booster coil and a booster fan is installed between the third server rack 103c and the fourth server rack 103d. Further, the third server rack 103c and the sixth server rack 103d On the upstream side of each of the server racks 103f, temperature sensors 115a. 115b is provided, and the air conditioner 111 and the auxiliary air conditioner 137 are controlled by the control means so that the temperatures detected by the temperature sensors 115a and 115b do not exceed the set upper limit temperatures, respectively.

  Furthermore, in this embodiment, in the third embodiment, the pipe 132 embedded in the peripheral wall 130 of the building 101 is attached to the indoor side of the peripheral wall 130.

  In the above configuration, the server racks 103a, 103b, and 103c are cooled on the right side of the blow-through 105 in the figure by the same operation as in FIG. On the other hand, on the left side of the blow-through 105 in the figure, the conditioned air, for example, 12 ° C. that has flowed into the inside from the side surface of the server rack 103a is used for cooling the mounted server, and the temperature rises to about 17 ° C. Then, it flows out from the side surface on the downstream side of the server rack 103a, and then flows into the second server rack 103b from the side surface through the space.

  In the server rack 103b, the temperature rises from, for example, 17 ° C. to 22 ° C. by exchanging heat with the server, and the conditioned air flowing out from the downstream side surface then flows into the most downstream server rack 103c from the side surface. .

  At this time, the temperature of the conditioned air flowing out from the server rack 103b and flowing into the next server rack 103c is monitored by the temperature sensor 115a, and the supply amount of cold water and the fan are set so that the temperature does not exceed the upper limit temperature. Since the conditioned air is controlled by the air volume of 111b, conditioned air, for example, 22 ° C., which is the supply temperature in the conventional air conditioning system, is supplied into the server rack 103c to reliably cool the mounted server. be able to. As in the above embodiment, the conditioned air is controlled to 22 ° C. ± 2 ° C., for example, in this control.

  In this way, in the server rack 103c, heat is exchanged with the server, the temperature rises from about 22 ° C. to about 27 ° C. to 28 ° C., and the conditioned air that has flowed out of the server rack 103c remains as it is on the downstream server racks 103d, 103e, 103f. Although it cannot be used for cooling, it is cooled by the auxiliary air conditioner 137 and again supplied as conditioned air at about 12 ° C.

  The air that has passed through the server racks 103 d, 103 e, 103 f and has risen to about 27 ° C. to 28 ° C. in this way, enters the vent 107 from the space at the end of each floor by the draft action and the suction force of the fan 116. Ascend through and reach the air passage 104 on the top floor of the building 101.

  Warm air of about 27 ° C. to 28 ° C. flowing into the air passage 104 from the end by the fan 116 is cooled to about 24 ° C. through the auxiliary chilled water coil 117 and flows through the air passage 104 from the end side to the center side. It reaches the blow-through 105, descends in the blow-through 105, and is sucked and recirculated by the fan 111b of the air conditioner 111 on each floor. Thus, the blow-through 105 is used as the air recirculation path 132. As described above, the warm air of about 27 ° C. to 28 ° C. flowing into the air passage 104 is cooled to about 24 ° C. through the auxiliary chilled water coil 117, so that a cold draft is generated. Since the reflux is promoted, the power required for the reflux by the fans 116 and 111b can be reduced.

  In the fourth embodiment, the outside air intake system 120 takes in outside air sucked from the outside air inlet 119 of the building 1 and warm air at both ends of the air passage 104 by the air cooling system 124, and By introducing the air cooled through the total heat exchanger 122 from above the central blow-through 105 at the upper center of the building 1, the above-described air recirculation can be promoted. At this time, as described above, the dehumidifying device 127 provided in the outside air intake system 120 is operated when there is a possibility that condensation occurs in the building depending on the humidity of the outside air, thereby preventing the occurrence of condensation. be able to. Similarly, by operating the dehumidifying device 128 provided in the air cooling system 124 as necessary, it is possible to more reliably prevent the occurrence of dew condensation. Further, since the water spray type air heat exchanger 129 is provided, the air in the outside air intake system 120 and the air cooling system 124 can be efficiently cooled.

  In addition to these, by using cold water by geothermal use, free cooling, freezer, ice heat storage, etc., to the piping 132 attached to the inner surface of the peripheral wall 130 of the building 101, natural energy can be used effectively to reduce the cooling load. And can save energy. When supplying outside air into the building 1 by the outside air intake system 120, the motor damper 136 provided at the exhaust port 135 formed on the extension on both ends of the air passage 104 is opened and the fan 116 opens the building 1. The amount of air can be balanced by exhausting warm air inside and above.

1 Building 2 (2a, 2b, 2c) Server rack (heat generating equipment)
DESCRIPTION OF SYMBOLS 3 Grating 4 Nitrogen fire-extinguishing division wall 5 Air-conditioning air passage 6 Air conditioner 6a Cold water coil 6b Fan 7 Cooling heat source equipment 7a Absorption-type refrigerator 7b Turbo refrigerator 7c Heat storage tank 8 Cold water piping 9 Flow control valve 10 Temperature sensor 11 Air recirculation path (space)
12 Fan 13 Radiant panel 14 Auxiliary chilled water coil 15 Drain pan 16 Exhaust part 16a Fan 16b Motor damper 17a Information system wiring rack 17b Power system wiring rack 18 Outside air intake system 19 Outside air intake 20 Fan 21 Dehumidifier 22 Air cooling system 23 Fan 24 Total heat exchanger 25 Cool pit 26 Dehumidifier 27 Outside air system 28 Exhaust port 29 Peripheral wall 30 Outer insulation 31 and 32 Piping 33 Damper with piston releaser 34 Motor damper 35 Partitions 36 and 37 Partition 38 Rubber mat 101 Building 102 Floor (void slab)
103 (103a, 103b, 103c) Server rack (heat generating equipment)
104 Air passage 105 Blow-through 106 Smoke prevention fire damper 107 Ventilation hole 108 Free access floor 109a Information system wiring rack 109b Power supply system wiring rack 110 Air conditioning air passage 111 Air conditioner 111a Cold water coil 111b Fan 112 Handrail 113 Heat source equipment 113a Absorption type refrigerator 113b Turbo chiller 113c Thermal storage tank 114 Chilled water piping 115 Temperature sensor 116 Fan 117 Auxiliary chilled water coil 118 Fan 119 Outside air intake 120 Outside air intake system 121 Fan 122 Total heat exchanger 123 Cool pit 124 Air cooling system 125 Outside air system 126 Exhaust port 127 Dehumidifier 128 Dehumidifier 129 Sprinkling air heat exchanger 130 Perimeter wall 131 Outer insulation material 132 Pipe 133 Motor damper 134 Air return path 135 Exhaust port 136 Motor damper 1 7 auxiliary air conditioner

Claims (12)

In a building with a large number of heat generating devices installed, the conditioned air passage is configured so that conditioned air from the air conditioner passes through the plurality of heat generating devices in series, and air is returned from the downstream side of the conditioned air passage to the air conditioner. A plurality of control means configured to control the conditioned air from the air conditioner so that the conditioned air temperature on the upstream side of the heat generating device on the most downstream side of the conditioned air passage is the upper limit temperature. Air-conditioning system in buildings with heat generating equipment. 2. The air conditioning system in a building in which a large number of heat generating devices are installed according to claim 1, wherein the air conditioner can supply low-temperature conditioned air having a large difference from the upper limit temperature by serial operation of the refrigerators. . 2. The air conditioning system in a building in which a large number of heat generating devices are installed according to claim 1, wherein an auxiliary air conditioner is installed in the middle of the air conditioning air passage. The conditioned air passage is configured in a vertical direction, and a plurality of heat generating devices are arranged in the vertical conditioned air passage with a space in the height direction by a floor material having air permeability. The air-conditioning system in the building which installed many heat generating apparatuses of any one of 1-3. 5. The air conditioning system in a building in which a large number of heat generating devices are installed according to claim 4, wherein the floor material having air permeability is grating. The heat generating equipment is configured to allow air-conditioning air to pass in the horizontal direction, and the intake side and exhaust side of the heat generating equipment are arranged on opposite sides of the adjacent floor, and the floor portion corresponding to the exhaust side of the heat generating equipment is configured to be non-breathable. The air conditioning in a building having a large number of heating devices according to claim 4 or 5, wherein the air conditioning air passage of zigzag is formed and a partition for allowing all of the conditioned air to pass through the heating devices is formed. system. The conditioned air passage is configured in a lateral direction, and a plurality of heat generating devices are arranged in the lateral conditioned air passage with a spacing in the lateral direction. An air conditioning system in a building in which a large number of heat generating devices described in 1 are installed. 8. An air conditioning system in a building in which a large number of heat generating devices are installed according to claim 7, wherein a blow-off is arranged upstream or downstream of the conditioned air passage. 9. An air conditioning system in a building in which a large number of heat generating devices are installed according to any one of claims 1 to 8, wherein an outside air intake system for taking outside air into the building is configured. The dehumidification part for dew condensation prevention was comprised in the outside air intake system, The air-conditioning system in the building which installed many heat-emitting devices of Claim 9 characterized by the above-mentioned. The building in which a large number of heat generating devices according to any one of claims 1 to 10 are installed, wherein an air cooling system for cooling the air in the upper part of the building by a total heat exchanger with outside air is configured. Air conditioning system. 12. The air conditioning system in a building in which a large number of heat generating devices are installed according to claim 11, wherein a cooling unit by a cool pit is configured downstream of the total heat exchanger of the air cooling system.

Images