Air conditioning system

Abstract

Provided is an air conditioning system capable of more reliably maintaining positive pressure in a room to be air-conditioned in the air conditioning system that comprises an outside air conditioner and an indoor unit. The air conditioning system replaces and conditions the air in the room to be air-conditioned, the air conditioning system comprising: the indoor unit that cools air suctioned from an air conditioning intake port in an upper part of the room to be air-conditioned and blows out the cooled air in a lower part of the room to be air-conditioned; and the outside air conditioner capable of reheating dehumidified outside air. Blow-out ports of at least the indoor unit and the outside air conditioner are disposed at a plurality of locations in the room to be air-conditioned. Fins for applying a swirl component to the blown-out air are each provided to the blow-out ports of the indoor unit and the outside air conditioner. The air volume of the air supplied by the outside air conditioner to the blow-out ports of the outside air conditioner is controlled so as to make the room to be air-conditioned have a positive pressure. The indoor unit increases the air volume to be blown out from the blow-out ports of the indoor unit when the air volume of the air supplied by the outside air conditioner to the blow-out ports of the outside air conditioner decreases.

Description

Air conditioning system

[0001] The present invention relates to an air conditioning system.

[0002] In recent years, various air conditioning systems have been proposed (see, for example, Patent Document 1).

[0003] Patent No. 7068261

[0004] Displacement air conditioning is one method for reducing the energy required for air conditioning. Displacement air conditioning performs air conditioning while maintaining thermal stratification, thereby reducing energy loss caused by air conditioning an upper space where equipment or people are not present. In this type of displacement air conditioning, for example, an indoor unit is used that draws air from the top of the air-conditioned space, cools it, and blows it out from an air intake port located at the bottom of the air-conditioned space. Because displacement air conditioning performs air conditioning while maintaining thermal stratification, it is particularly effective in factories and other places with relatively high ceilings.

[0005] Factories and other facilities where production equipment is installed often have clean rooms that are set to positive pressure to prevent the intrusion of dust and other contaminants from the outside. In air conditioning systems equipped with outdoor and indoor units, the outdoor and indoor units are often controlled separately. In such air conditioning systems, there may be cases where the airflow rate of the indoor units remains unchanged despite a decrease in the airflow rate of the outdoor unit. In such cases, maintaining positive pressure in the clean room can be difficult.

[0006] In one aspect, the present disclosure has been made in consideration of this situation, and its purpose is to provide an air conditioning system that can more reliably maintain positive pressure in the room to be air-conditioned in an air conditioning system equipped with an outdoor air conditioning unit and an indoor unit.

[0007] One aspect of the disclosed technology is exemplified by the following air conditioning system: The air conditioning system performs displacement air conditioning on a room to be air-conditioned, and includes an indoor unit that cools air drawn in through an air conditioning intake port at an upper part of the room to be air-conditioned and blows the air out at a lower part of the room to be air-conditioned, and an outdoor air conditioning unit that can reheat dehumidified outdoor air, at least the air outlets of the indoor unit and the outdoor air conditioning unit are arranged at multiple locations in the room to be air-conditioned, each of the air outlets of the indoor unit and the outdoor air conditioning unit is provided with fins that impart a swirling component to the blown-out air, the air volume of the air supplied by the outdoor air conditioning unit to the air outlet of the outdoor air conditioning unit is controlled to maintain a positive pressure in the room to be air-conditioned, and when the air volume of the air supplied by the outdoor air conditioning unit to the air outlet of the outdoor air conditioning unit decreases, the indoor unit increases the air volume blown out of the air outlet of the indoor unit.

[0008] In the above air conditioning system, when the volume of air supplied by the outdoor air conditioning unit to the air outlet of the outdoor air conditioning unit decreases, the indoor unit can increase the volume of air blown out of the air outlet of the indoor unit. This air conditioning system can more reliably maintain positive pressure in the air-conditioned room because the increase in the air volume of the indoor unit can compensate for the decrease in the air volume of the outdoor air conditioning unit. Here, if the air outlet of the outdoor air conditioning unit and the air outlet of the indoor unit are arranged adjacent to each other, it becomes easier to compensate for the decrease in the air volume of the outdoor air conditioning unit due to the increase in the air volume of the indoor unit.

[0009] In the air conditioning system, the conditioned room may be provided with a heat generating device and an exhaust device that exhausts air from the heat generating device, the exhaust device operating according to the operating state of the heat generating device, and the outdoor air conditioning unit may vary the air volume supplied by the outdoor air conditioning unit to an outlet of the outdoor air conditioning unit according to the operating state of the heat generating device. Because the air volume of the outdoor air conditioning unit varies according to the operating state of the heat generating device, for example, when the heat generating device is stopped, the air volume of the outdoor air conditioning unit decreases. In the air conditioning system, even when the air volume of the outdoor air conditioning unit decreases due to the heat generating device being stopped, the positive pressure in the air conditioned room can be easily maintained by increasing the air volume of the indoor unit.

[0010] Here, if the distance between the air outlet of the outdoor air-conditioning unit and the heat-generating device is set shorter than the distance between the air outlet of the indoor unit and the heat-generating device, the outdoor air-conditioning unit can effectively cool the heat-generating device. Also, if the temperature of the air blown out from the air outlet of the outdoor air-conditioning unit into the air-conditioned room is set lower than the temperature of the air blown out from the air outlet of the indoor unit into the air-conditioned room, the heat-generating device can be effectively cooled.

[0011] Here, the outdoor air-conditioning unit may be one that reheats the outdoor air using air in the upper space of the room to be air-conditioned, or one that reheats the outdoor air using a reheat coil.

[0012] Furthermore, in this air conditioning system, the air outlet of the outdoor air-conditioning unit may be formed in an air outlet unit disposed in the room to be air-conditioned, and the air outlet unit may be formed thinner than the indoor unit. Because the air cooled by the outdoor air-conditioning unit is supplied to the air outlet unit from the outdoor air-conditioning unit, a heat-absorbing coil or the like may not be provided. Therefore, the air outlet unit can be easily formed thinner than the indoor unit. Furthermore, forming the air outlet unit thinner than the indoor unit increases the degree of freedom in the placement of the air outlet unit. For example, forming the air outlet unit thinner than the indoor unit makes it easier to place the air outlet unit near the heat-generating device, which in turn makes it easier to cool the heat-generating device with the air blown out of the air outlet unit.

[0013] In the air conditioning system, the outdoor air-conditioning unit may be disposed in a machine room, and the air outlet of the outdoor air-conditioning unit may be disposed on the machine room side of the room to be air-conditioned. By disposing the air outlet of the outdoor air-conditioning unit in such a position, the duct connecting the outdoor air-conditioning unit and the air outlet of the outdoor air-conditioning unit can be made as short as possible.

[0014] According to the disclosed technology, it is possible to provide an air conditioning system that is equipped with an outdoor air conditioning unit and an indoor unit and that can more reliably maintain positive pressure in the room to be air-conditioned.

[0015] FIG. 1 is a schematic diagram of an air conditioning system according to an embodiment. FIG. 2 is an external perspective view of an indoor unit. FIG. 3 is a diagram illustrating the internal structure of the indoor unit. FIG. 4 is a schematic diagram of an air outlet unit, an outdoor air conditioning unit, and a duct according to an embodiment. FIG. 5 is a first diagram illustrating the temperature of air blown out of the air outlet unit when controlling the indoor temperature of an air-conditioned room in an embodiment. FIG. 6 is a second diagram illustrating the temperature of air blown out of the air outlet unit when controlling the indoor temperature of an air-conditioned room in an embodiment. FIG. 7 is a third diagram illustrating the temperature of air blown out of the air outlet unit when controlling the indoor temperature of an air-conditioned room in an embodiment. FIG. 8 is a diagram illustrating a case where the temperature of a device belonging to the first row rises in an embodiment. FIG. 9 is an image diagram showing a temperature gradient in the height direction of an air-conditioned room. FIG. 10 is a system diagram of a heat source system according to an embodiment. FIG. 11 is a diagram illustrating the schematic configuration of an air conditioning system according to a first modified example. FIG. 12 is a diagram illustrating the schematic configuration of an air conditioning system according to a second modified example. Fig. 13 is a diagram illustrating a schematic configuration of an air conditioning system according to a third modified example. Fig. 14 is a diagram illustrating an example of the opening degree of the motor damper and the rotation speed of the fan, which are controlled in accordance with the temperature measured by the temperature sensor, according to the third modified example.

[0016] DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS The following describes embodiments of the present invention. The embodiments described below are merely examples of the present invention, and the technical scope of the present invention is not limited to the following aspects.

[0017] FIG. 1 is a schematic diagram of an air-conditioning system 1 according to an embodiment. The air-conditioning system 1 conditions an air-conditioned room 2 in which equipment 3 is installed. In this embodiment, a clean room in a semiconductor device manufacturing factory, which requires high air cleanliness, is exemplified as the air-conditioned room 2 to which the air-conditioning system 1 is applied. Various types of heat-generating semiconductor manufacturing equipment are installed in the clean room of the semiconductor device manufacturing factory. Therefore, in this embodiment, such semiconductor manufacturing equipment is assumed as the equipment 3. Examples of the semiconductor manufacturing equipment include etching equipment and CVD (Chemical Vapor Deposition) equipment. FIG. 1 illustrates multiple pieces of equipment 3 arranged in the air-conditioned room 2. In FIG. 1, the equipment 3 is arranged in three rows: a first row 3A, a second row 3B, and a third row 3C. The air-conditioning system 1 of this embodiment is not limited to application to such semiconductor device manufacturing factories, but may also be applied to, for example, factories manufacturing lithium-ion batteries, precision optical instruments, and various other industrial products.

[0018] The air-conditioned room 2 to be air-conditioned by the air-conditioning system 1 must satisfy the temperature conditions set by the device 3. When the device 3 is installed on the floor of the air-conditioned room 2, it is sufficient that the ambient temperature near the device 3 meets the temperature conditions; there is no need to perform air-conditioning so that the ambient temperature of the space above the device 3 meets the temperature conditions. Therefore, the air-conditioning system 1 of this embodiment employs a displacement air-conditioning method to minimize the power required for air-conditioning the air-conditioned room 2. That is, the air-conditioning system 1 includes air outlet units 4A, 4B, and 4C for supplying outside air treated by the outdoor air-conditioning units 6A, 6B, and 6C to the air-conditioned room 2, as well as an indoor unit 5 that cools air drawn in at the top of the air-conditioned room 2 and blows it out at the bottom of the air-conditioned room 2. In FIG. 1 , multiple air outlet units 4 and indoor units 5 are arranged side by side near the wall of the air-conditioned room 2, but the air outlet units 4 and indoor units 5 may also be arranged away from the wall.

[0019] The system configuration of the air conditioning system 1 will be described in detail below. The outdoor air conditioning units 6A, 6B, and 6C are units that take in outside air, purify it, adjust the temperature and humidity, and supply it to the air outlet units 4A, 4B, and 4C via ducts 7A, 7B, and 7C. The outdoor air conditioning units 6A, 6B, and 6C are disposed, for example, in the machine room 200. The air outlet units 4A, 4B, and 4C are disposed in multiple locations in the air-conditioned room 2. When the outdoor air conditioning units 6A, 6B, and 6C are not distinguished, they are also referred to as outdoor air conditioning units 6. When the ducts 7A, 7B, and 7C are not distinguished, they are also referred to as ducts 7. When the air outlet units 4A, 4B, and 4C are not distinguished, they are also referred to as air outlet units 4.

[0020] The indoor unit 5 is a device that controls the indoor temperature of the air-conditioned room 2 by cooling the air drawn in from the top of the air-conditioned room 2 and blowing it out at the bottom of the air-conditioned room 2. Because the air-conditioning system 1 uses a displacement air conditioning method, the indoor unit 5 is configured to blow air sideways and is installed on the floor of the air-conditioned room 2.

[0021] Fig. 2 is an external perspective view of the indoor unit 5. Fig. 3 is a diagram showing the internal structure of the indoor unit 5. As shown in Fig. 2, an air conditioning inlet 54 is provided on the top surface of the indoor unit 5. An air conditioning outlet 55 is provided on the front surface of the indoor unit 5. Air from the upper part of the air-conditioned room 2 is drawn in through the air conditioning inlet 54 by the suction force of the electric fan 51. Air cooled by the heat-absorbing coil 52 is blown out through the air conditioning outlet 55 by the suction of the electric fan 51.

[0022] As can be seen from FIG. 2 , multiple circular air conditioning outlets 55 are arranged vertically and horizontally on the front surface of the indoor unit 5. The air conditioning outlets 55 are arranged side by side in the height and width directions of the front surface of the indoor unit 5 with gaps between them. Each air conditioning outlet 55 has fins that are arranged radially and equidistantly in the circumferential direction around the central axis of the air conditioning outlet 55 to generate a swirling flow centered on the center of the air conditioning outlet 55. These fins arranged around the center of the air conditioning outlet 55 are arranged at an angle with respect to the central axis of the air conditioning outlet 55. As a result, a swirling component that swirls around the central axis passing through the center of the air conditioning outlet 55 is imparted to the air blown out from the air conditioning outlet 55, thereby attracting air in the air-conditioned room 2 around the air conditioning outlet 55.

[0023] Furthermore, adjacent air conditioning outlets 55 above and below among the multiple air conditioning outlets 55 have fins with inclined directions opposite to each other, so that the swirling components imparted to the cool air are opposite to each other. For example, as shown by the thin arrows in FIG. 2 , if the first air conditioning outlet 55 from the top imparts a counterclockwise swirling component to the air, the second air conditioning outlet 55 from the top imparts a clockwise swirling component to the air. As a result, between these air conditioning outlets 55, the swirling components of the first air conditioning outlet 55 from the top and the second air conditioning outlet 55 from the top are in the same direction (to the right in FIG. 2 ), and the swirling components mutually enhance each other. In this case, the third air conditioning outlet 55 from the top imparts a counterclockwise swirling component to the cool air. As a result, between the second air conditioning outlet 55 from the top and the third air conditioning outlet 55 from the top, the swirl component caused by the second air conditioning outlet 55 from the top and the swirl component caused by the third air conditioning outlet 55 from the top are in the same direction (leftward in Figure 2), and the swirl components mutually enhance each other.

[0024] As a result, the amount of air attracted (attraction ratio) in the air-conditioned room 2 around the air conditioning outlets 55 by the cool air blown out from the air conditioning outlets 55 increases, making it possible to diffuse the cool air into the air-conditioned room 2 toward the front of the indoor unit 5. This makes it possible to blow out the cool air without a drafty feeling compared to when no swirling component is given to the cool air. Furthermore, displacement air conditioning using temperature stratification with a small temperature difference from top to bottom can be achieved within the height range from the lowest air conditioning outlet 55 to the highest air conditioning outlet 55 in the space within the air-conditioned room 2.

[0025] Each of the air outlet units 4 may be arranged, for example, to blow air supplied from the outdoor air-conditioning unit 6 toward at least one of the devices 3. In the example of Fig. 1 , the air outlet unit 4A is arranged to blow air toward the devices 3 belonging to the first row 3A, the air outlet unit 4B is arranged to blow air toward the devices 3 belonging to the second row 3B, and the air outlet unit 4C is arranged to blow air toward the devices 3 belonging to the third row 3C. Furthermore, at least some of the air outlet units 4 are arranged adjacent to the indoor unit 5.

[0026] FIG. 4 is a schematic diagram of the air outlet unit 4, outdoor air conditioning unit 6, and duct 7 according to an embodiment. The outdoor air conditioning unit 6 takes in and purifies outdoor air, adjusts the temperature and humidity, and supplies the air to the air outlet unit 4 via the duct 7. The outdoor air conditioning unit 6 includes a filter 61, a heating coil 62, a cooling coil 63, a reheat coil 64, and an electric fan 65. The filter 61 captures foreign matter such as dust and dirt in the air. The heating coil 62 heats the air taken in by the outdoor air conditioning unit 6. The cooling coil 63 cools the air to remove moisture. The reheat coil 64 heats the air cooled by the cooling coil 63 to a temperature suitable for supplying the air to the air-conditioned room 2. The electric fan 65 rotates with the power of an electric motor to send air.

[0027] The air outlet unit 4 is a unit for blowing out the air (outside air) processed by the outdoor air conditioning unit 6 into the air-conditioned room 2. The air outlet unit 4 introduces outside air into the air-conditioned room 2, maintaining the air-conditioned room 2 at a positive pressure. The air outlet unit 4 includes an air outlet 42 from which air is blown out and a filter 41 for purifying the blown air. Similar to the indoor unit 5, the air outlet 42 has fins arranged radially and equidistantly around the central axis of the air outlet 42 to generate a swirling flow centered on the center of the air outlet 42. Because the air conditioning system 1 employs a displacement air conditioning system, the air outlet unit 4 is configured to blow air horizontally (parallel to the floor) and is installed on the floor of the air-conditioned room 2. Furthermore, because the air outlet unit 4 does not include a heat-absorbing coil 52 used for cooling, it can be thinner than the indoor unit 5.

[0028] The indoor unit 5 controls the volume and temperature of air blown out from the air conditioning outlet 55 so that the indoor temperature of the air-conditioned room 2 becomes the desired indoor temperature. That is, the indoor unit 5 controls the temperature of the indoor temperature of the air-conditioned room 2, and the outdoor air conditioning unit 6 controls the pressure to maintain a positive pressure in the air-conditioned room 2. Here, the amount of reheating by the reheat coil 64 of the outdoor air conditioning unit 6 may be limited according to the desired indoor temperature. By limiting the amount of reheating by the reheat coil 64, the temperature of the air blown out from the outlet unit 4 decreases. As a result, the burden on the indoor unit 5, which controls the indoor temperature of the air-conditioned room 2, is reduced. In other words, the amount of reheating by the reheat coil 64 is limited so as to compensate for the temperature control of the indoor temperature of the air-conditioned room 2 by the indoor unit 5. In addition, if the amount of reheating by the reheating coil 64 is restricted too much, there is a risk that the air blown out from the air outlet unit 4 will condense, so the amount of reheating by the reheating coil 64 is restricted to a range in which the air blown out from the air outlet unit 4 will not condense.

[0029] Here, limiting the amount of reheating by the reheat coil 64 according to the desired indoor temperature will be described with reference to Figs. 5 to 7. Fig. 5 is a diagram illustrating the temperature of air blown out of the air outlet unit 4 when the indoor temperature of the air-conditioned room 2 is controlled to 25°C in an embodiment. When the indoor temperature of the air-conditioned room 2 is controlled to 25°C, for example, the amount of reheating by the reheat coil 64 is performed as usual, and air at 22°C is blown out of the air outlet unit 4 into the air-conditioned room 2.

[0030] 6 is a diagram illustrating the temperature of air blown out of the air outlet unit 4 when the indoor temperature of the air-conditioned room 2 is controlled to 22° C. in the embodiment. When the indoor temperature of the air-conditioned room 2 is controlled to 22° C., for example, the amount of reheating by the reheat coil 64 is limited to the first reheating amount, and air at 20° C. is blown out of the air outlet unit 4 into the air-conditioned room 2.

[0031] 7 is a diagram illustrating the temperature of air blown out of the air outlet unit 4 when the indoor temperature of the air-conditioned room 2 is controlled to 20° C. in the embodiment. When the indoor temperature of the air-conditioned room 2 is controlled to 20° C., for example, the amount of reheating by the reheat coil 64 is limited to a second reheating amount that is lower than the first reheating amount, and air at 18° C. is blown out of the air outlet unit 4 into the air-conditioned room 2.

[0032] In this way, by limiting the amount of reheat by the reheat coil 64 in accordance with the desired indoor temperature of the air-conditioned room 2, it is possible to lower the temperature of the air blown from the air outlet unit 4 into the air-conditioned room 2. As a result, even in cases where a lower indoor temperature is desired, it is possible to minimize the air-conditioning energy required by the indoor unit 5. Furthermore, because the temperature of the air blown from the air outlet unit 4 into the air-conditioned room 2 is reduced by limiting the amount of reheat by the reheat coil 64, it is also possible to minimize the air-conditioning energy required by the outdoor air-conditioning unit 6.

[0033] Each of the devices 3 may be provided with, for example, a thermometer, and the measurement value indicating the temperature of the device 3 measured by the thermometer may be input to the outdoor air-conditioning unit 6. When such a configuration is adopted, for example, the measurement value of the thermometer provided in the device 3 belonging to the first row 3A is input to the outdoor air-conditioning unit 6A, the measurement value of the thermometer provided in the device 3 belonging to the second row 3B is input to the outdoor air-conditioning unit 6B, and the measurement value of the thermometer provided in the device 3 belonging to the third row 3C is input to the outdoor air-conditioning unit 6C.

[0034] The temperature of the device 3 installed in the air-conditioned room 2 may rise depending on the operating conditions. When the outdoor air-conditioning unit 6 detects an increase in the measurement value input from the thermometer, it limits the amount of reheating by the reheat coil 64. FIG. 8 illustrates an example of a case in which the temperature of the device 30 in the first row 3A rises in this embodiment. Air blown out from the outlet units 4B and 4C is not shown in FIG. 8 . The device 30 is one of the devices 3 installed in the air-conditioned room 2 and belongs to the first row 3A. Because the device 30 belongs to the first row 3A, an increase in the temperature of the device 30 results in an increase in the measurement value input to the outdoor air-conditioning unit 6A. In this case, the outdoor air-conditioning unit 6A limits the amount of reheating by the reheat coil 64 of the outdoor air-conditioning unit 6A. The air, whose temperature has been reduced by limiting the amount of reheating, is blown out from the outdoor air-conditioning unit 6A through the outlet unit 4A into the air-conditioned room 2. As described above, the air outlet unit 4A is arranged to blow air toward the device 3 belonging to the first row 3A. Therefore, the air supplied from the outdoor air-conditioning unit 6A with a reduced reheat amount is blown out from the air outlet unit 4A toward the first row 3A including the device 30. The device 3 is an example of a "heat-generating device."

[0035] In this way, by limiting the amount of reheating by the reheat coil 64 of the outdoor air-conditioning unit 6 corresponding to the air outlet unit 4 that blows air toward the device 3 whose temperature has risen, it is possible to blow air at a lower temperature from the air outlet unit 4, thereby cooling the device 3 whose temperature has risen. Furthermore, because the temperature of the air blown out from the air outlet unit 4 is reduced by limiting the amount of reheating by the reheat coil 64, it is possible to minimize the air-conditioning energy required to cool the device 3 whose temperature has risen. Furthermore, the lower temperature of the air blown out from the air outlet unit 4 further reduces the indoor temperature of the air-conditioned room 2. Therefore, by increasing the temperature of the air blown out from the indoor unit 5, it is possible to control the temperature in the air-conditioned room 2 to a desired temperature, and it is possible to minimize the air-conditioning energy consumed by the indoor unit 5.

[0036] FIG. 9 is an image diagram showing the temperature gradient in the height direction within the air-conditioned room 2. In the graph of FIG. 9, the solid line indicates the temperature gradient in the air-conditioning system 1 of this embodiment, and the dashed-dotted line indicates the temperature gradient in general displacement air conditioning, in which the cool air does not have a swirl component. The air-conditioning system 1 of this embodiment uses an indoor unit 5 that imparts a swirl component to the air through the air-conditioning outlets 55. Therefore, as shown by the solid line in the graph of FIG. 9, displacement air conditioning with temperature stratification with a small temperature difference can be achieved within the height range from the lowest air-conditioning outlet 55 to the highest air-conditioning outlet 55 within the space within the air-conditioned room 2. On the other hand, in general displacement air conditioning, in which the cool air does not have a swirl component, in order to conform the upper part of the region where the temperature conditions are set, the air-conditioning system 1 must blow out cool air at a temperature lower than the cool air blown out of the air-conditioning outlets 55 in the lower region of the air-conditioned room 2 where the temperature conditions are set, as shown by the dashed-dotted line in the graph of FIG. 9, which inevitably results in temperature stratification with a large temperature difference. Therefore, in the case of typical displacement air conditioning, it is difficult to maintain air below the upper limit temperature and above the lower limit temperature in an area where the temperature condition is set within a relatively narrow range of the difference between the upper limit temperature and the lower limit temperature. The air conditioning system 1 of this embodiment is capable of performing displacement air conditioning with a small temperature difference between the upper and lower limits by using cool air with a swirl component, making it possible to maintain air below the upper limit temperature and above the lower limit temperature in an area where the temperature condition is set within a relatively narrow range of the difference between the upper limit temperature and the lower limit temperature. When performing displacement air conditioning with an airflow that does not have a swirl component, a large airflow volume is required to meet the temperature conditions. However, with an airflow that has a swirl component, as in the air conditioning system 1 of this embodiment, the temperature conditions can be met even with a reduced airflow volume, thereby reducing the power required for airflow in the entire air conditioning system 1. Furthermore, because displacement air conditioning with a small temperature difference between the upper and lower limits can be performed using cool air with a swirl component, the temperature conditions can be met even if the blowing temperature is set higher than in typical displacement air conditioning without a swirl component. Increasing the blowout temperature means that the temperature of the heat medium passing through the heat-absorbing coil 52 can be increased, thereby improving the heat source efficiency.In addition, by reducing the amount of air being blown, the temperature of the heat medium passing through the heat absorption coil 52 that recovers heat from the upper space of the air-conditioned room 2 becomes higher, and the outside air can be efficiently heated using the heat of the heat medium that has passed through the heat absorption coil 52 as described below.

[0037] Next, we will explain the heat source system of the air conditioning system 1. Fig. 10 is a system diagram of a heat source system 8 according to an embodiment. The air conditioning system 1 includes a heat source system 8 as shown in Fig. 10. The heat source system 8 includes, for example, a heat medium system 81, a cooling water system 82, and a hot water system 83.

[0038] The heat transfer medium system 81 is a system through which a heat transfer medium circulates to supply cold and hot heat to equipment that handles air to be conditioned, such as the indoor unit 5 and the outdoor air-conditioning unit 6. The heat transfer medium system 81 includes a refrigerator 811 for producing cold, a heat transfer medium circulation pump 812 for circulating the heat transfer medium, a heat transfer medium supply header 813 for supplying the heat transfer medium to each air-conditioning equipment, and a heat transfer medium return header 814 for returning the heat transfer medium distributed to each air-conditioning equipment. In the heat transfer medium system 81, the heat transfer medium that passes through the evaporator of the refrigerator 811 is sent to the heat transfer medium supply header 813 by the heat transfer medium circulation pump 812, which is installed midway along the heat transfer medium piping 8110 connecting the refrigerator 811 to the heat transfer medium supply header 813. The heat transfer medium sent to the heat transfer medium supply header 813 flows to the heat transfer medium piping 8112 connected to the heat absorption coil 52 of the indoor unit 5 and the heat transfer medium piping 8113 connected to the cooling coil 63 of the outdoor air-conditioning unit 6. The heat medium that flows to the heat absorption coil 52 of the indoor unit 5 returns to the heat medium return header 814 through the heat medium piping 8115, and the heat medium that flows to the cooling coil 63 of the outdoor air-conditioning unit 6 returns to the heat medium return header 814 through the heat medium piping 8116. The heat medium that returns to the heat medium return header 814 passes through the heat medium piping 8111 and again through the evaporator of the chiller 811. Note that although Figure 10 shows that the heat medium system 81 is provided with only one each of the indoor unit 5, outdoor air-conditioning unit 6, and chiller 811, various devices, valves, piping, and pumps are provided in the heat medium system 81 as appropriate.

[0039] The cooling water system 82 is a system through which cooling water for cooling the condenser of the refrigerator 811 provided in the heat transfer medium system 81 circulates. The cooling water system 82 is provided with a cooling water circulation pump 821 for circulating the cooling water and a cooling tower 822 for cooling the cooling water. In the cooling water system 82, the heat transfer medium that has passed through the condenser of the refrigerator 811 is sent to the cooling tower 822 by the cooling water circulation pump 821 provided midway through a cooling water pipe 824 connecting the refrigerator 811 to the cooling tower 822. The cooling water sent to the cooling tower 822 drips from the top of the cooling tower 822 and accumulates at the bottom of the cooling tower 822. The cooling water that has accumulated at the bottom of the cooling tower 822 flows again through a cooling water pipe 823 to the condenser of the refrigerator 811. The cooling tower 822 is provided with an electric fan capable of generating an internal updraft, and the electric fan is turned on and off appropriately depending on the temperature of the cooling water flowing through the cooling water pipe 823, thereby cooling the cooling water using the principle of latent heat of vaporization. The on / off of the electric fan is preferably controlled so that the temperature of the cooling water flowing through the cooling water pipe 823 is set to a temperature at which the operating efficiency of the chiller 811 is high. The cooling tower 822 is also provided with a water supply means, such as a ball tap valve, that replenishes the cooling water so that the level of the cooling water pooled at the bottom of the cooling tower 822 remains constant. While FIG. 10 shows only one chiller 811, one cooling tower 822, and one cooling water circulation pump 821 in the cooling water system 82, various devices, valves, pipes, and pumps are provided in the cooling water system 82 as appropriate.

[0040] The hot water system 83 heats the heat medium that flows from the heat absorption coil 52 to the heating coil 62 and the reheat coil 64. Any suitable heat source is used for the hot water system 83. Examples of heat sources that can be used for the hot water system 83 include heat from heat source equipment such as a heat pump or a boiler, and exhaust heat generated by utility equipment such as a compressor.

[0041] When heating air in an air conditioning system, hot water such as that produced by the hot water system 83 is typically used. However, in the air conditioning system 1 of this embodiment, the power required to heat the air is reduced by flowing the heat medium that has passed through the heat absorption coil 52 through the heating coil 62 and reheat coil 64 of the outdoor air conditioning unit 6 that processes the outdoor air. That is, as shown in the system diagram of FIG. 10 , a heat medium pipe 8114 is connected as a branch path to the heat medium pipe 8115 connecting the heat absorption coil 52 to the heat medium return header 814, for dividing the heat medium to the heating coil 62 and reheat coil 64. The heat medium branched to the heat medium pipe 8114 further flows to the heating coil 62 and reheat coil 64 via a heat medium pipe 8118. The heat medium that has passed through the heating coil 62 and reheat coil 64 then rejoins the heat medium pipe 8115 via a heat medium pipe 8119 and flows to the heat medium return header 814.

[0042] As described above, the heat medium system 81 of the heat source system 8 is provided with a path for sending the heat medium that has passed through the heat absorption coil 52 to the heating coil 62 and the reheat coil 64. Therefore, when heat is generated from each device 3 installed in the air-conditioned room 2 due to operation of the device 3, the generated heat is transferred to the heat absorption coil 52 via the air in the air-conditioned room 2, and heats the heat medium passing through the heat absorption coil 52. Since the heat medium system 81 is provided with a path for sending the heat medium that has passed through the heat absorption coil 52 to the heating coil 62 and the reheat coil 64, the heat medium that has been heated by the heat of the device 3 flows from the heat absorption coil 52 to the heating coil 62 and the reheat coil 64, heating the outside air with the heating coil 62 and also heating the air cooled by the cooling coil 63 that dehumidifies the outside air with the reheat coil 64. Therefore, according to the air conditioning system 1, the heat generated by the device 3 is effectively used to heat the outside air taken in by the outdoor air-conditioning unit 6 and to heat the outside air after it has been dehumidified by the cooling coil 63, thereby reducing the air conditioning energy consumed by the entire air conditioning system 1. In view of this mechanism for effective use of heat, it is preferable from the standpoint of heat utilization that the heat-absorbing coil 52 has a heat exchange capacity sufficient to raise the temperature of the heat medium to a temperature higher than the temperature conditions set in the lower space of the room 2 to be air-conditioned.

[0043] According to this embodiment, the amount of reheating by the reheat coil 64 is limited as the desired indoor temperature decreases, thereby lowering the temperature of the air blown out from the air outlet unit 4 into the air-conditioned room 2. The decrease in temperature of the air from the air outlet unit 4 is achieved by limiting the amount of reheating, and this limitation on the amount of reheating is carried out so as to supplement the temperature control of the indoor temperature of the air-conditioned room 2 by the indoor unit unit 5. Therefore, the decrease in the temperature of the air from the air outlet unit 4 reduces the load related to the temperature control of the air-conditioned room 2 by the indoor unit unit 5, and ultimately, according to this embodiment, the air-conditioning energy related to cooling the air-conditioned room 2 can be suppressed as much as possible.

[0044] According to this embodiment, the amount of reheating by the reheat coil 64 of the outdoor air-conditioning unit 6 corresponding to the air outlet unit 4 that blows air toward the device 3 whose temperature has risen is reduced, so that low-temperature air is blown out from the air outlet unit 4. As a result, the device 3 whose temperature has risen can be cooled. Furthermore, because the temperature of the air blown out from the air outlet unit 4 is reduced by reducing the amount of reheating by the reheat coil 64, the air-conditioning energy required to cool the device 3 whose temperature has risen can be minimized.

[0045] Here, the air outlet unit 4 is preferably disposed closer to the device 3 than the indoor unit 5. That is, the distance between the air outlet unit 4 and the device 3 is preferably set shorter than the distance between the indoor unit 5 and the device 3. By disposing the air outlet unit 4 in this manner, the device 3 can be cooled more efficiently by the air blown out from the air outlet unit 4.

[0046] In the heat medium system 81 of this embodiment, the heat medium that has passed through the heat absorption coil 52 flows through the heating coil 62 and reheat coil 64 of the outdoor air-conditioning unit 6, heating the air in the outdoor air-conditioning unit 6. Therefore, for example, the system configuration is simpler than when a two-stage heat transport system is adopted in which the heat medium that passes through the heat absorption coil 52 is separated from the heat medium that passes through the heating coil 62 and reheat coil 64, and heat is exchanged between the systems of each heat medium using a heat pump or the like. Therefore, the air conditioning energy required to transport heat from the heat absorption coil 52 to the reheat coil 64 is reduced as much as possible.

[0047] In addition, in the heat transfer medium system 81 of this embodiment, the heat transfer medium that has passed through the heat absorption coil 52 flows through the heating coil 62 and reheating coil 64 of the outdoor air conditioning unit 6, and the air in the outdoor air conditioning unit 6 is heated, thereby reducing the energy required to heat the air.

[0048] In order to prevent the air that has passed through the reheat coil 64 from being supercooled, the heating medium system 81 is provided with regulating valves 818 and 819 that regulate the flow rate of the heating medium that passes through the reheat coil 64. The regulating valves 818 and 819 are valves whose openings are adjusted based on the measurement value of a temperature sensor 817 that measures the temperature of the heating medium that has passed through the reheat coil 64. For example, if the measurement value of the temperature sensor 817 is higher than the set value, the opening of the regulating valve 818 is decreased, and the opening of the regulating valve 819 is increased. Furthermore, for example, if the measurement value of the temperature sensor 817 is lower than the set value, the opening of the regulating valve 818 is increased, and the opening of the regulating valve 819 is decreased. In this way, the air that has passed through the reheat coil 64 is adjusted to an appropriate temperature.

[0049] Furthermore, in preparation for the case where the heat generated by the device 3 is not sufficient to heat the heat medium passing through the heat absorption coil 52 because the device 3 has just stopped or started up, for example, the heat source system 8 is provided with a means for heating the heat medium flowing from the heat absorption coil 52 to the heating coil 62 and the reheat coil 64 with the heat of hot water in the hot water system 83. That is, the heat source system 8 is provided with a heat exchanger 832 between the heat medium pipe 8114 and the heat medium pipe 8118 of the heat medium system 81 for exchanging heat with the hot water of the heat source system 8, and an adjustment valve 8117 in a bypass path for increasing or decreasing the flow rate of the heat medium passing through the heat exchanger 832. The hot water system 83 is also provided with an adjustment valve 831 for adjusting the flow rate of the hot water in the heat exchanger 832 in accordance with the measurement value of a temperature sensor 816 that measures the temperature of the heat medium flowing from the heat exchanger 832 to the heat medium pipe 8118, so that the heat medium passing through the heat exchanger 832 reaches a predetermined temperature. Furthermore, the heat medium pipe 8114 is provided with a heat medium booster pump 815 for compensating for a lack of flow rate due to pressure loss when the heat medium passes through the heat exchanger 832. The adjustment valve 8117 controls the flow rate of the heat medium passing through the heating coil 62 and the reheat coil 64 by increasing or decreasing the valve opening so that the pressure difference between the heat medium pipe 8114 and the heat medium pipe 8118 is appropriate. As a result, for example, if the heat medium passing through the heat absorption coil 52 cannot be sufficiently heated by the heat generated by the device 3 and the heat medium passing through the heat absorption coil 52 is below a predetermined temperature, the opening of the adjustment valve 831 is increased until the heat medium passing through the heat exchanger 832 reaches the predetermined temperature, and the heat medium flowing from the heat absorption coil 52 to the heating coil 62 and the reheat coil 64 is heated by the heat of the hot water in the hot water system 83. Furthermore, for example, if the heat medium passing through the heat absorption coil 52 is sufficiently heated by the heat generated from the device 3 and the heat medium that has passed through the heat absorption coil 52 is at or above a predetermined temperature, the opening of the adjustment valve 831 is reduced so that the heat medium that has passed through the heat exchanger 832 becomes below the predetermined temperature, causing the adjustment valve 831 to close, and the heat medium flowing from the heat absorption coil 52 to the heating coil 62 and reheat coil 64 will not be heated by the heat of the hot water in the hot water system 83.Because the heat source system 8 is configured in this manner, the air conditioning system 1 is able to reduce the air conditioning energy consumed by the entire air conditioning system 1 when the device 3 is operating, while supplying air at an appropriate temperature from the outdoor air conditioning unit 6 to the room 2 to be air-conditioned immediately after the device 3 is stopped or started.

[0050] For example, as shown in Figure 10, a case will be described where the temperature of the heat medium in the heat medium supply header 813 is designed to be 14°C. When the target temperature value of the heat medium set in the controller of the chiller 811 is 14°C, the heat medium in the heat medium supply header 813 will be 14°C. As described above, the 14°C heat medium in the heat medium supply header 813 is sent to the heat absorption coil 52 of the indoor unit 5 and the cooling coil 63 of the outdoor air-conditioning unit 6. The 14°C heat medium sent to the cooling coil 63 of the outdoor air-conditioning unit 6 cools the outside air flowing into the outdoor air-conditioning unit 6 by the suction of the electric fan 65.

[0051] Meanwhile, the 14°C heat medium sent to the heat absorption coil 52 of the indoor unit 5 is heated to, for example, about 26°C by cooling the air in the air-conditioned room 2 that flows into the indoor unit 5 through suction by the electric fan 51. The heat medium heated to about 26°C by the heat absorption coil 52 is sent from the heat absorption coil 52 to the heating coil 62 and the reheat coil 64, as described above. Therefore, in the outdoor air-conditioning unit 6, the outside air that flows into the outdoor air-conditioning unit 6 is heated by the 26°C heat medium in the heating coil 62. Also, in the outdoor air-conditioning unit 6, the outside air that has been cooled by the 14°C heat medium in the cooling coil 63 is heated by the 26°C heat medium in the reheat coil 64.

[0052] In the air conditioning system 1 of this embodiment, the heat medium that branches off from the heat medium supply header 813 and is divided into the indoor unit 5 and the outdoor air-conditioning unit 6 is not returned directly to the heat medium return header 814, but rather a portion of the heat medium that has passed through the indoor unit 5 is used for heating in the outdoor air-conditioning unit 6. Therefore, with a simple system configuration, the air-conditioning energy required for heat transport is reduced as much as possible, and the heat contained in the air in the room 2 to be air-conditioned is effectively utilized.

[0053] In the case of general displacement air conditioning, it is difficult to keep the air below the upper limit temperature and above the lower limit temperature in an area where the temperature conditions are set in a relatively narrow range, where the difference between the upper limit temperature and the lower limit temperature is relatively narrow. Therefore, general displacement air conditioning is difficult to apply to places with strict temperature conditions, such as clean rooms in semiconductor manufacturing factories (for example, where the temperature conditions are 23°C ± 3°C). With the air conditioning system 1 of this embodiment, it is possible to perform displacement air conditioning with a small temperature difference between the top and bottom using cold air with a swirling component, so it is possible to keep the air below the upper limit temperature and above the lower limit temperature in an area where the temperature conditions are set in a relatively narrow range, where the difference between the upper limit temperature and the lower limit temperature is relatively narrow. This makes it possible to apply the system to places with such strict temperature conditions.

[0054] Furthermore, the air conditioning system 1 of this embodiment is capable of performing displacement air conditioning with a small temperature difference between the top and bottom using cold air with a swirl component. Therefore, the temperature conditions can be met even when the blowout temperature is set higher than in typical displacement air conditioning without a swirl component. For example, in the case of displacement air conditioning without a swirl component, if the supply air temperature of the indoor unit is set to 19-20°C, it is impossible to maintain the temperature condition (23°C ± 3°C) in the area set below the upper limit temperature. However, the air conditioning system 1 of this embodiment is capable of performing displacement air conditioning with a small temperature difference between the top and bottom using cold air with a swirl component. Therefore, even if the supply air temperature of the indoor unit 5 is set to 19-20°C, the temperature condition (23°C ± 3°C) in the area set below the upper limit temperature can be maintained below the upper limit temperature. Therefore, even if the heat medium supply header 8A3 supplies a relatively high-temperature heat medium (14°C) to the indoor unit 5, the temperature condition can be maintained below the upper limit temperature in the area set below the upper limit temperature.

[0055] The fact that the temperature of the heat medium supplied from the refrigerator 811 of the heat medium system 81 can be set to a relatively high temperature range of 14°C means that the refrigerator 811 can be operated at a low load, thereby reducing the power required for the refrigerator 811. As a result, the entire heat medium system 81 can be operated with high efficiency.

[0056] Furthermore, the heat source for the heat used in the heating coil 62 and the reheat coil 64 could be, for example, the heat of the cooling water from the chiller 811 in the cooling water system 82. However, in this case, in order to properly heat the outdoor air in the outdoor air-conditioning unit 6, the cooling water in the cooling water system 82 needs to be operated at a relatively high temperature (e.g., 32°C). Operating the cooling water in the cooling water system 82 at such a temperature reduces the condensing capacity of the condenser of the chiller 811, resulting in poor operating efficiency of the chiller 811. In this regard, the air-conditioning system 1 of this embodiment uses the heat of the heat medium that has passed through the heat-absorbing coil 52 as the heat source for the heat used in the heating coil 62 and the reheat coil 64. This allows the cooling water in the cooling water system 82 to be operated at a temperature range suitable for the operating efficiency of the chiller 811. In other words, the air-conditioning system 1 of this embodiment allows the cooling water in the cooling water system 82 to be operated at a low temperature range at which the condenser of the chiller 811 can exhibit sufficient condensing capacity. Therefore, the operation efficiency of the refrigerator 811 can be increased.

[0057] In the air conditioning system 1 of this embodiment, the air temperature at the top of the air-conditioned room 2 is assumed to be in the range of approximately 30°C to 35°C, although this will depend on the amount of heat emitted by the device 3 in the air-conditioned room 2 and the building's insulation performance. This is a relatively low-temperature waste heat among the waste heat emitted from a wide variety of devices. It is generally difficult to recover waste heat in this temperature range as warm heat using a heat transfer medium such as hot water. However, in the air conditioning system 1 of this embodiment, we have focused on the fact that displacement air conditioning using an airflow with a swirling component can meet the temperature requirements with supply air that is higher than in conventional displacement air conditioning, and have discovered that waste heat in this temperature range can be recovered using a heat transfer medium flowing through the heat-absorbing coil 52 in the indoor unit 5. The reason why waste heat in this temperature range can be used to heat outdoor air in the outdoor air conditioning unit 6 is because displacement air conditioning using an airflow with a swirling component allows the temperature requirements to be met even with high-temperature supply air. This type of effective heat utilization is impossible with conventional displacement air conditioning.

[0058] In the above embodiment, the outdoor air is dehumidified by the cooling coil 63 in the outdoor air-conditioning unit 6. However, such dehumidification may be performed only in the summer when humidity is high, and dehumidification may be omitted in the winter when humidity is low. For example, when dehumidification is omitted in the winter, the air conditioning system 1 may stop the flow of heat medium through the cooling coil 63 with a valve, and only heat the outdoor air with the heating coil 62 and reheat coil 64.

[0059] In addition, in the above embodiment, the outdoor air conditioning unit 6 is equipped with both the heating coil 62 and the reheat coil 64, but the air conditioning system 1 may, for example, be one in which the heating coil 62 is omitted from the outdoor air conditioning unit 6.

[0060] Furthermore, the temperature of the air blown from the outdoor air-conditioning unit 6 into the air-conditioned room 2 through the air outlet unit 4 may be set lower than the temperature of the air blown from the indoor unit 5 into the air-conditioned room 2. By setting the temperature of the air blown from the outdoor air-conditioning unit 6 into the air-conditioned room 2 in this manner, the device 3 whose temperature has risen can be cooled more efficiently.

[0061] Furthermore, the volume of air blown from the outdoor air-conditioning unit 6 to the air-conditioned room 2 through the air outlet unit 4 may be increased or decreased depending on the operating state (temperature) of the device 3. For example, the outdoor air-conditioning unit 6 may reduce the volume of air blown out of the air outlet unit 4 when the temperature of the device 3 decreases, and may increase the volume of air blown out of the air outlet unit 4 when the temperature of the device 3 increases.

[0062] The air outlet unit 4 may also be disposed in an area on the machine room 200 side (an area close to the machine room 200) of the air-conditioned room 2. By disposing the air outlet unit 4 in such a position, the duct 7 connecting the outdoor air-conditioning unit 6 and the air outlet unit 4 can be made as short as possible.

[0063] <First Modification> In the embodiment described above, the reheat coil 64 is used to reheat the outside air in the outdoor air-conditioning unit 6, but for example, air in the upper space of the air-conditioned room 2 that has been warmed by the device 3 may be used to reheat the air in the outdoor air-conditioning unit 6. In the first modification, a configuration will be described in which reheating is performed using air in the upper space of the air-conditioned room 2 that has been warmed by the device 3. The same components as in the embodiment will be assigned the same reference numerals, and their description will be omitted. Below, the first modification will be described with reference to the drawings.

[0064] Fig. 11 is a diagram illustrating the schematic configuration of an air conditioning system 1A according to a first modified example. Fig. 11 illustrates the state of the air-conditioned room 2 as viewed from the side. For simplicity, the indoor unit 5 is not shown in Fig. 11. The outdoor air-conditioning unit 16 differs from the outdoor air-conditioning unit 6 according to the embodiment in that the reheat coil 64 is omitted.

[0065] In air conditioning system 1A, outdoor air-conditioning unit 16 and air outlet unit 4 are connected by duct 71. Duct 71 includes ducts 72, 73, and 74. In air conditioning system 1A, duct 72 connects outdoor air-conditioning unit 16 to pipe line 731 of duct 73. Air intake port 75 and electric fan 66 are connected by duct 73. Duct 71 is provided with an adjustment damper 68. Air intake port 75 of duct 73 is provided with an adjustment damper 69 between pipe line 731 and pipe line 731. Electric fan 66 and air outlet unit 4 are connected by duct 74.

[0066] In the outdoor air-conditioning unit 16, reheating is not performed by the reheat coil 64, so air at 15°C flows through duct 72. Furthermore, air from the upper space of the air-conditioned room 2, which is taken in through the air intake 75, flows through duct 73. Here, the air in the upper space of the air-conditioned room 2 has been heated by the device 3 to about 30°C, for example. The air flowing through duct 72 and the air flowing through duct 73 are guided to duct 74 by the suction of the electric fan 66.

[0067] Duct 74 is provided with a temperature sensor 67 that measures the temperature of the air flowing through duct 74, and the opening degrees of adjustment dampers 68 and 69 are controlled in accordance with the measurement value of temperature sensor 67. By controlling the opening degrees of adjustment dampers 68 and 69 in accordance with the measurement value of temperature sensor 67, the flow rate of 30°C air drawn in from intake port 75 and the flow rate of 15°C air supplied from outdoor air-conditioning unit 16 are controlled. Consequently, the air blown out from air outlet unit 4 is controlled to a desired temperature.

[0068] <Second Modification> The air-conditioned room 2, which is a clean room, is preferably maintained at a positive pressure to prevent dust and other foreign matter from entering from the outside. In the air-conditioning system 1, the air volume of the air outlet unit 4 is controlled so that the air is blown out into the air-conditioned room 2 by the air outlet unit 4, thereby creating a positive pressure in the air-conditioned room 2. The same components as those in the embodiment are designated by the same reference numerals, and their description will be omitted. The second modification will be described below with reference to the drawings.

[0069] Fig. 12 is a diagram illustrating a schematic configuration of an air conditioning system 1B according to a second modified example, in which the air-conditioned room 2 is viewed from the side.

[0070] The device 3 is connected to an exhaust fan 32 by an exhaust duct 31 through under the floor of the air-conditioned room 2. At least a portion of the heat from the device 3 is discharged to the outside of the air-conditioned room 2 by exhaust air caused by suction from the exhaust fan 32. The exhaust fan 32 is controlled to increase its exhaust volume as the amount of heat generated by the device 3 increases. As air is exhausted by the exhaust fan 32, there is a risk that the air pressure inside the air-conditioned room 2 will drop.

[0071] In the air conditioning system 1B, a barometric pressure sensor 21 is disposed to measure the air pressure in the air-conditioned room 2. The air volume of the outdoor air-conditioning unit 26 is controlled in accordance with the measurement value of the barometric pressure sensor 21. For example, if the measurement value of the barometric pressure sensor 21 indicates a decrease in the air pressure in the air-conditioned room 2, the air volume of the outdoor air-conditioning unit 26 is increased. Also, for example, if the measurement value of the barometric pressure sensor 21 indicates an increase in the air pressure in the air-conditioned room 2, the air volume of the outdoor air-conditioning unit 26 is decreased.

[0072] Here, the air volume of the indoor unit 15 is controlled, for example, so that the blown air speed is in the range of 0.7 to 1.4 m / s depending on the indoor temperature. If the blown air speed is in this range, it is suitable for attracting air from the air-conditioned room 2 around the air conditioning outlet 55. When the air volume of the outdoor air-conditioning unit 26 decreases, the indoor temperature rises, so the indoor unit 15 increases the air volume from the air conditioning outlet 55, and when the air volume of the outdoor air-conditioning unit 26 increases, the indoor temperature drops, so the indoor unit 15 decreases the air volume from the air conditioning outlet 55.

[0073] For example, when the air volume of the outdoor air-conditioning unit 26 is equal to or greater than a predetermined air volume, the indoor unit 15 determines the air volume to be blown out from the air conditioning outlet 55 so that the blown air speed is equal to or less than a predetermined threshold value in the range of 0.7 to 1.4 m / s. Furthermore, when the air volume of the outdoor air-conditioning unit 26 is less than the predetermined air volume, the indoor unit 15 determines the air volume to be blown out from the air conditioning outlet 55 so that the blown air speed is greater than the predetermined threshold value in the range of 0.7 to 1.4 m / s because the indoor temperature will rise.

[0074] According to the second modification, the air volume of the outdoor air-conditioning unit 26 is controlled in accordance with the measurement value of the air pressure sensor 21, so that the air-conditioned room 2 can be maintained at a positive pressure.

[0075] <Third Modification> In the third modification, similar to the first modification, reheating is performed using air in the upper space of the air-conditioned room 2 that has been warmed by the device 3, and when the air from the outdoor air-conditioning unit 6 is at a predetermined temperature or lower, an inverter-controlled motor damper 68A blows at least a portion of the air from the outdoor air-conditioning unit 6 into the upper space of the air-conditioned room 2. The same components as in the first modification are assigned the same reference numerals, and their description will be omitted. The third modification will be described below.

[0076] Fig. 13 is a diagram illustrating a schematic configuration of an air conditioning system 1C according to a third modified example. Fig. 13 illustrates a state in which the air-conditioned room 2 is viewed from the side. In Fig. 13, the indoor unit 5 is not shown to simplify the illustration.

[0077] In the third modified example, a motor damper 68A is provided in the duct 71. An inverter-controlled fan 66A is provided between the intake port 75 of the duct 73 and the middle of the duct 731. The opening degree of the motor damper 68A and the rotation speed of the fan 66A are controlled in accordance with the temperature measured by the temperature sensor 67. The amount of air exhausted from the duct 71 to the upper space of the air-conditioned room 2 varies in accordance with the opening degree of the motor damper 68A. The amount of air taken into the duct 73 from the upper space of the air-conditioned room 2 varies in accordance with the rotation speed of the fan 66A.

[0078] Fig. 14 is a diagram illustrating the opening of the motor damper 68A and the rotation speed of the fan 66A in the third modified example, which are controlled in response to the temperature measured by the temperature sensor 67. The vertical axis on the left side of Fig. 14 illustrates the opening of the motor damper 68A (labeled "MD opening" in the diagram), and the vertical axis on the right side illustrates the frequency of the inverter that controls the rotation speed of the fan 66A. The horizontal axis of Fig. 14 also illustrates the temperature of the air flowing through the duct 74 measured by the temperature sensor 67 (i.e., the temperature of the air blown out by the outdoor air-conditioning unit 6).

[0079] When the temperature measured by the temperature sensor 67 is lower than temperature T1, the opening degree of the motor damper 68A is 100%, and the frequency of the inverter controlling the fan 66A is 60 Hz (maximum value). Because the opening degree of the motor damper 68A is 100%, the amount of air exhausted from the duct 71 to the upper space of the air-conditioned room 2 is at its maximum. Furthermore, because the frequency of the inverter is at its maximum value, the amount of air drawn into the duct 73 by the fan 66A is also at its maximum.

[0080] When the temperature measured by the temperature sensor 67 is equal to or greater than temperature T1 and less than temperature T2, the opening degree of the motor damper 68A decreases as the temperature measured by the temperature sensor 67 decreases, while the frequency of the inverter controlling the fan 66A becomes 60 Hz (maximum value). The opening degree of the motor damper 68A decreases as the temperature measured by the temperature sensor 67 increases. Therefore, the amount of air exhausted from the duct 71 to the upper space of the air-conditioned room 2 decreases as the temperature measured by the temperature sensor 67 increases. Furthermore, because the inverter frequency becomes maximum, the amount of air drawn into the duct 73 by the fan 66A also becomes maximum.

[0081] When the temperature measured by temperature sensor 67 is equal to or higher than temperature T2 and lower than temperature T3, the opening degree of motor damper 68A becomes 0% (closed state), and the frequency of the inverter controlling fan 66A decreases in accordance with the decrease in temperature measured by temperature sensor 67. When the opening degree of motor damper 68A becomes 0%, air is no longer exhausted from duct 71 to the upper space of the air-conditioned room 2. Furthermore, because the frequency of the inverter decreases in accordance with the decrease in temperature measured by temperature sensor 67, the amount of air drawn into duct 73 by fan 66A also decreases in accordance with the decrease in temperature measured by temperature sensor 67.

[0082] In the third modified example, the opening degree of the motor damper 68A and the rotation speed of the fan 66A are controlled according to the temperature of the air from the outdoor air-conditioning unit 6 (the temperature of the air flowing through the duct 74). This makes it possible to exhaust air from the duct 71 and draw air from the upper space of the air-conditioned room 2 according to the temperature of the air from the outdoor air-conditioning unit 6, thereby enabling appropriate control of the reheating of air from the outdoor air-conditioning unit 6 using air drawn from the upper space of the air-conditioned room 2. Furthermore, in the third modified example, when the temperature of the air from the outdoor air-conditioning unit 6 is lower than temperature T2, the air is exhausted from the duct 71 to the upper space of the air-conditioned room 2. Because the air is exhausted from the duct 71 to the air-conditioned room 2, a drop in air pressure within the air-conditioned room 2 is suppressed.

[0083] Furthermore, as in the embodiment, at least some of the air outlet units 4 are arranged adjacent to the indoor unit 5. By arranging the indoor unit 5 and the air outlet units 4 adjacent to each other, it becomes easy to compensate for the decrease in the air volume blown out from the air outlet units 4 due to the decrease in the air volume of the outdoor air-conditioning unit 6 by increasing the air volume of the indoor unit 5.

[0084] 1, 1A, 1B... Air conditioning system 2... Air-conditioned room 21... Barometric pressure sensor 3, 30... Device 3A... First row 3B... Second row 3C... Third row 31... Exhaust duct 32... Exhaust fan 4, 4A, 4B, 4C... Air outlet unit 41, 53, 61... Filter 42... Air outlet 5, 15... Indoor unit 6, 6A, 6B, 6C, 16, 26... Outdoor air conditioning unit 62... Heating coil 63... Cooling coil 64... Reheat coil 51, 65, 66... ​​Electric fan 67... Temperature sensor 68, 69... Adjusting damper 7, 7A, 7B, 7C, 71, 72, 73, 74... Duct 75... Air intake 8... Heat source system 81... Heat medium system 82: Cooling water system 83: Hot water system 200: Machine room 811: Refrigerator 52: Heat absorption coil 54: Intake port 55: Air conditioning outlet

Claims

1. An air conditioning system that performs displacement air conditioning on a room to be air-conditioned, comprising: an indoor unit that cools air drawn in from an air conditioning intake port at an upper part of the room to be air-conditioned and blows it out at a lower part of the room to be air-conditioned; and an outdoor air conditioning unit that can reheat dehumidified outdoor air, wherein at least the air outlets of the indoor unit and the outdoor air conditioning unit are arranged in multiple locations within the room to be air-conditioned, and each of the air outlets of the indoor unit and the outdoor air conditioning unit is provided with fins that impart a swirling component to the air that is blown out, the volume of air that the outdoor air conditioning unit supplies to the air outlet of the outdoor air conditioning unit is controlled to create a positive pressure in the room to be air-conditioned, and wherein when the volume of air that the outdoor air conditioning unit supplies to the air outlet of the outdoor air conditioning unit decreases, the indoor unit increases the volume of air that it blows out of the air outlet of the indoor unit.

2. The air conditioning system according to claim 1, wherein the air outlet of the outdoor air-conditioning unit and the air outlet of the indoor unit are arranged adjacent to each other.

3. The air conditioning system of claim 1, wherein the room to be air-conditioned is provided with a heat generating device and an exhaust device that exhausts air from the heat generating device, the exhaust device operates according to the operating state of the heat generating device, and the outdoor air conditioning unit varies the volume of air that the outdoor air conditioning unit supplies to the air outlet of the outdoor air conditioning unit according to the operating state of the heat generating device.

4. The air conditioning system according to claim 3, wherein the distance between the air outlet of the outdoor air-conditioning unit and the heat generating device is set shorter than the distance between the air outlet of the indoor unit and the heat generating device.

5. The air conditioning system of claim 1, wherein the temperature of the air blown out from the air outlet of the outdoor air conditioning unit into the room to be air-conditioned is set lower than the temperature of the air blown out from the air outlet of the indoor unit into the room to be air-conditioned.

6. The air conditioning system according to claim 1, wherein the outdoor air-conditioning unit reheats the outside air using air in an upper space of the room to be air-conditioned.

7. The air conditioning system according to claim 1, wherein the outdoor air-conditioning unit reheats the outdoor air using a reheat coil.

8. The air conditioning system according to claim 1, wherein the air outlet of the outdoor air-conditioning unit is formed in an air outlet unit disposed in the room to be air-conditioned, and the air outlet unit is formed thinner than the indoor unit.

9. An air conditioning system according to any one of claims 1 to 8, wherein the outdoor air conditioning unit is arranged in a machine room, and an air outlet of the outdoor air conditioning unit is arranged on the machine room side of the room to be air-conditioned.

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