JP6938950B2 - Air conditioning system - Google Patents

Description

The present invention relates to an air conditioning system for air conditioning in a room.

Conventionally, an air conditioner in which a plurality of indoor units are connected to one heat source unit has been known. Patent Document 1 and Patent Document 2 disclose this type of air conditioner. The heat source unit of the air conditioner of Patent Document 1 includes a heat exchanger that exchanges heat with a refrigerant for heat source water supplied from the outside. On the other hand, the heat source unit of the air conditioner of Patent Document 2 includes a heat exchanger that exchanges heat with the refrigerant for outdoor air.

Further, in Patent Document 2, the target value of the evaporation temperature or the condensation temperature of the refrigerant in the indoor unit is set according to the air conditioning load in the room, and the air is set so that the evaporation temperature or the condensation temperature of the refrigerant in the indoor unit becomes the target value. It is described to control the operation of the air conditioner.

Japanese Unexamined Patent Publication No. 07-012417 Japanese Unexamined Patent Publication No. 2011-257126

A plurality of indoor units provided in an air conditioner do not necessarily have the same air conditioning load to be processed by each. Generally, the perimeter zone near the outer wall of the building has a higher air conditioning load than the interior zone. Therefore, the indoor unit installed in the perimeter zone has a larger air conditioning load to be processed than the indoor unit installed in the interior zone.

In such a case, if a control operation is performed to set the target value of the evaporation temperature or the condensation temperature in the indoor unit according to the air conditioning load in the room, the target value will be set according to the air conditioning load in the perimeter zone. .. Then, for the indoor unit in the interior zone, the target value of the evaporation temperature is too low during the cooling operation, and the target value of the condensation temperature is too high during the heating operation. Therefore, the difference between the high pressure and the low pressure of the refrigeration cycle cannot be sufficiently reduced, and as a result, the energy required to drive the compressor increases, and the energy consumption of the air conditioner may not be sufficiently reduced. ..

The control operation of setting the target value of the evaporation temperature or the condensation temperature in the indoor unit according to the air conditioning load in the room is an air conditioner as disclosed in Patent Document 1 (that is, the refrigerant is heated with water in the heat source side unit. It can also be done in an air conditioner to be replaced). Even in that case, the above-mentioned problem (that is, the problem that the energy consumption of the air conditioner cannot be sufficiently reduced due to the large difference in the air conditioning load to be processed by each indoor unit) may occur.

The present invention has been made in view of this point, and an object of the present invention is to provide an air conditioning system including an air conditioner having a heat source side unit for exchanging heat with a heat source fluid and a plurality of indoor units. The purpose is to reduce energy consumption.

The first invention is intended for an air conditioning system, and a heat source fluid circuit (20) in which a heat source fluid circulates and a heat source device (13) for cooling or heating the heat source fluid circulating in the heat source fluid circuit (20). A heat source side unit (61) connected to the heat source fluid circuit (20), and a plurality of utilization side units (62a to 62d) each supplying conditioned air to the indoor space (110, 120). An air conditioner that performs a refrigeration cycle by exchanging heat with the heat source fluid for the refrigerant circulating in the refrigerant circuit (70) formed by connecting the side unit (61) and the utilization side units (62a to 62d) with pipes. The air conditioner (60a, 60b) is provided with (60a, 60b), and the evaporation temperature or condensation temperature of the refrigerant in the utilization side units (62a to 62d) depends on the air conditioning load in the indoor space (110,120). While the air-conditioning side controller (16) that controls the operation of the air conditioner (60a, 60b) is provided so as to achieve the target value set in the above, the heat source fluid is connected to the heat source fluid circuit (20). It further includes a fan coil unit (50a, 50b) that supplies conditioned air whose temperature has been adjusted by heat exchange with the above indoor space (110,120) to the perimeter zone (112,122).

In the first invention, the heat source side unit (61) of the air conditioner (60a, 60b) and the fan coil unit (50a, 50b) are connected to the heat source fluid circuit (20) through which the heat source fluid circulates. The heat source fluid cooled or heated in the heat source equipment (13) is used for cooling or heating the refrigerant in the heat source side unit (61) and cooling or heating the air in the fan coil unit (50a, 50b). The fan coil unit (50a, 50b) supplies conditioned air whose temperature is regulated by heat exchange with the heat source fluid to the perimeter zone (112,122) of the indoor space (110,120). Therefore, at least a part of the air conditioning load in the perimeter zone (112,122) is processed by the fan coil unit (50a, 50b).

In the first invention, the air conditioning side controller (16) is air-conditioned so that the evaporation temperature or the condensation temperature of the refrigerant in the user side units (62a to 62d) becomes a target value set according to the air conditioning load in the room. Control the operation of the aircraft (60a, 60b). On the other hand, in the present invention, at least a part of the air conditioning load in the perimeter zone (112,122) is processed by the fan coil unit (50a, 50b). Therefore, the difference in the air conditioning load to be processed by each user unit (62a to 62d) is smaller than that when all the air conditioning load in the perimeter zone (112,122) is processed by the user unit (62a to 62d). As a result, the target value of the evaporation temperature in the user unit (62a to 62d) is set to a high value during the cooling operation, and the target concentration temperature in the user unit (62a to 62d) is set during the heating operation. The value is set to a low value.

As described above, in the first invention, the fan coil unit (50a, 50b) of the heat source fluid circuit (20) is provided, and the perimeter zone (perimeter zone (60a, 60b) is used by utilizing the heat source fluid used for operating the air conditioner (60a, 60b). By processing the air conditioning load of 112,122), it is possible to sufficiently reduce the difference between the high pressure and the low pressure of the refrigeration cycle performed by the air conditioner (60a, 60b).

Further, in the first invention, in addition to the above configuration, in the heat source fluid circuit (20), the fan coil unit (50a) is upstream of the heat source side unit (61) of the air conditioner (60a, 60b). , 50b) is arranged, and the heat source fluid cooled or heated by the heat source device (13) passes through the fan coil unit (50a, 50b) and then passes through the heat source side unit (61).

In the first invention, in the heat source fluid circuit (20), the fan coil unit (50a, 50b) and the heat source side unit (61) are arranged in series. The heat source fluid cooled or heated in the heat source equipment (13) first flows into the fan coil unit (50a, 50b) and exchanges heat with air, and then the heat source side unit (60a, 60b) of the air conditioner (60a, 60b). It flows into 61), exchanges heat with the refrigerant, and is then sent back to the heat source equipment (13). Therefore, the temperature of the heat source fluid sent from the heat source device (13) is higher than that in the case where the fan coil unit (50a, 50b) and the heat source side unit (61) are arranged in parallel in the heat source fluid circuit (20). , The difference from the temperature of the heat source fluid flowing into the heat source device (13) becomes large.

If the amount of heat transferred by the heat source fluid is the same, the greater the difference between the temperature of the heat source fluid sent out from the heat source equipment (13) and the temperature of the heat source fluid flowing into the heat source equipment (13), the greater the difference in the heat source fluid. The flow rate is small. Therefore, in the present invention, the heat source fluid circulating in the heat source fluid circuit (20) is compared with the case where the fan coil unit (50a, 50b) and the heat source side unit (61) are arranged in parallel in the heat source fluid circuit (20). The flow rate can be reduced.

In the second invention, in the first invention, the fan coil unit (50a, 50b) processes only the sensible heat load in the perimeter zone (112,122).

In the second invention, the fan coil unit (50a, 50b) processes only the sensible heat load in the perimeter zone (112,122) and not the latent heat load in the perimeter zone (112,122).

The third invention is the supply side temperature sensor (25) for measuring the temperature of the heat source fluid flowing out from the heat source device (13) and the supply side temperature sensor (25) in the first or second invention. It is provided with a heat source side controller (15) that adjusts the capacity of the heat source device (13) so that the measured value of the above is maintained at a predetermined target temperature.

In the third invention, the heat source side controller (15) performs a control operation using the measured values of the supply side temperature sensor (25). In the present invention, since the operation of the air conditioner (60a, 60b) is controlled by the air conditioning side controller (16), the heat source fluid at an appropriate temperature is supplied to the heat source side unit (61) to supply the air conditioner (60a). , 60b) operates normally, and the air conditioning load in the room is properly handled. On the other hand, the temperature of the heat source fluid returning to the heat source device (13) changes depending on the magnitude of the air conditioning load processed by the fan coil unit (50a, 50b) and the air conditioner (60a, 60b). Therefore, if the temperature of the heat source fluid sent from the heat source device (13) is maintained at an appropriate value by the control operation of the heat source side controller (15), the fan coil unit (50a, 50b) and the air conditioner (50a, 50b) and the air conditioner ( 60a, 60b) will properly handle the air conditioning load in the room. In other words, the heat source side controller (15) performs the control operation based on the measured value of the supply side temperature sensor (25) without acquiring the information from the air conditioner (60a, 60b), so that the indoor space (110,120) It is possible to properly handle the air conditioning load of.

In the present invention, the fan coil unit (50a, 50b) of the heat source fluid circuit (20) is provided, and the heat source fluid used for operating the air conditioner (60a, 60b) is used to control the air conditioning load of the perimeter zone (112,122). The treatment makes it possible to sufficiently reduce the difference between the high pressure and the low pressure of the refrigeration cycle performed by the air conditioners (60a, 60b). Therefore, according to the present invention, the energy required for operating the air conditioner (60a, 60b) can be reduced, and the energy consumption of the air conditioner system (10) can be reduced.

Further, in the heat source fluid circuit (20) of the present invention, the heat source side unit (61) is arranged downstream of the fan coil unit (50a, 50b). Therefore, the temperature of the heat source fluid at the outlet and inlet of the heat source equipment (13) is higher than that in the case where the fan coil unit (50a, 50b) and the heat source side unit (61) are arranged in parallel in the heat source fluid circuit (20). The difference can be widened and, as a result, the flow rate of the heat source fluid in the heat source fluid circuit (20) can be reduced. Therefore, according to the present invention, the energy required to circulate the heat source fluid in the heat source fluid circuit (20) can be reduced, and the energy consumption of the air conditioning system (10) can be further reduced.

In the third invention, the heat source side controller (15) performs a control operation based on the measured value of the supply side temperature sensor (25) without acquiring information from the air conditioners (60a, 60b). It is possible to properly handle the air conditioning load in the room. Therefore, according to the present invention, the amount and type of data transmitted / received between the heat source side controller (15) and the air conditioner (60a, 60b) can be suppressed, and the control system of the air conditioner system (10) can be suppressed. Can be simplified.

FIG. 1 is a piping system diagram showing the configuration of the air conditioning system of the embodiment. FIG. 2 is a refrigerant circuit diagram showing a configuration of an air conditioner of the air conditioning system of the embodiment. FIG. 3 is a configuration diagram showing a schematic configuration of a fan coil unit of the air conditioning system of the embodiment.

Embodiments of the present invention will be described in detail with reference to the drawings. It should be noted that the embodiments and modifications described below are essentially preferred examples and are not intended to limit the scope of the present invention, its applications, or its uses.

The present embodiment is an air conditioning system (10) that performs air conditioning in an indoor space (110, 120).

-Overall configuration of air conditioning system-
As shown in FIG. 1, the air conditioning system (10) of the present embodiment includes a plurality of subsystems (11, 12), a heat source water circuit (20), a heat source device (13), and a heat source side controller ( It has 15) and. Note that FIG. 1 illustrates only two subsystems (11, 12).

<sub-system>
The first subsystem (11) performs air conditioning of the first indoor space (110). The second subsystem (12) harmonizes the air in the second indoor space (120). In this embodiment, each subsystem (11,12) includes two fan coil units (50a, 50b) and one air conditioner (60a, 60b). Further, the air conditioners (60a, 60b) of each subsystem (11,12) include one heat source side unit (61) and a plurality of (four in this embodiment) user side units (62a, 62b). , 62c, 62d) and. The number of fan coil units (50a, 50b), air conditioners (60a, 60b), heat source side units (61), and user side units (62a to 62d) shown here is merely an example.

Further, although not shown, each subsystem (11,12) is provided with a ventilation device for ventilating the indoor space (110,120). As this ventilation device, a ventilation device provided with a so-called total heat exchanger or a ventilation device provided with an adsorption rotor carrying an adsorbent can be used.

<Heat source water circuit>
The heat source water circuit (20) is a circuit in which heat source water, which is a heat source fluid, circulates, and constitutes a heat source fluid circuit.

As shown in FIG. 1, the heat source water circuit (20) includes one main feed pipe (30) and one main return pipe (40). Further, the heat source water circuit (20) has the same number of sub feed pipes (31a, 31b) and sub return pipes (41a, 41b) as the subsystems (11, 12). The sub-feed pipe (31a, 31b) and the sub-return pipe (41a, 41b) correspond to each subsystem (11, 12) one by one.

The main feed pipe (30) is connected to the outlet of the heat source equipment (13). A plurality of (three in this embodiment) heat source water pumps (21) are provided in parallel with each other in the main feed pipe (30). One end of each sub-feed pipe (31a, 31b) is connected to the downstream side of the heat source water pump (21) in the main feed pipe (30). On the other hand, the main return pipe (40) is connected to the inflow port of the heat source equipment (13).

Each subfeed pipe (31a, 31b) is connected to a fan coil unit (50a, 50b) of the corresponding subsystem (11,12). In the first auxiliary feed pipe (31a), one branch pipe (32a) is connected to one fan coil unit (50a) of the first subsystem (11), and the other branch pipe (32b) is the first subsystem. It is connected to the other fan coil unit (50b) of (11). In the second auxiliary feed pipe (31b), one branch pipe (32a) is connected to one fan coil unit (50a) of the second subsystem (12), and the other branch pipe (32b) is the second subsystem. It is connected to the other fan coil unit (50b) of (12). The branch pipes (32a, 32b) of each sub-feed pipe (31a, 31b) are provided with one flow control valve (33) on the utilization side, which is an electric valve with a variable opening.

Each sub-return pipe (41a, 41b) connects the heat source side unit (61) of the air conditioner (60a, 60b) and the fan coil unit (50a, 50b) in the corresponding subsystem (11,12). There is. Further, each sub-return pipe (41a, 41b) is connected to the sub-feed pipe (31a, 31b) of the corresponding subsystem (11,12) via the water pipe (44a, 44b).

The first sub-return pipe (41a) is connected to the heat source side unit (61) of the air conditioner (60a) of the first subsystem (11). Further, in the first sub-return pipe (41a), one branch pipe (42a) is connected to one fan coil unit (50a) of the first subsystem (11), and the other branch pipe (42b) is the first. It is connected to the other fan coil unit (50b) of the subsystem (11). The first sub-return pipe (41a) is connected to the first sub-feed pipe (31a) via the water pipe (44a). A solenoid valve (43a) is provided in the water pipe (44a).

The second sub-return pipe (41b) is connected to the heat source side unit (61) of the air conditioner (60b) of the second subsystem (12). Further, in the second secondary return pipe (41b), one branch pipe (42a) is connected to one fan coil unit (50a) of the second subsystem (12), and the other branch pipe (42b) is the second. It is connected to the other fan coil unit (50b) of the subsystem (12). The second sub-return pipe (41b) is connected to the second sub-feed pipe (31b) via the water pipe (44b). A solenoid valve (43b) is provided in the water pipe (44b).

The heat source side unit (61) of the air conditioner (60a) of the first subsystem (11) is connected to the main return pipe (40) via the water pipe (45a). Further, the heat source side unit (61) of the air conditioner (60b) of the second subsystem (12) is connected to the main return pipe (40) via the water pipe (45b).

The heat source water circuit (20) is provided with a heat source side bypass pipe (22). One end of the heat source side bypass pipe (22) is connected to the downstream side of the heat source water pump (21) in the main feed pipe (30), and the other end is connected to the main return pipe (40). The heat source side bypass pipe (22) is provided with a heat source side flow rate control valve (23) which is an electric valve having a variable opening degree.

The heat source water circuit (20) is provided with a feed side water temperature sensor (25) and a return side water temperature sensor (26). The feed side water temperature sensor (25) is arranged on the upstream side of the heat source water pump (21) in the main feed pipe (30). The feed-side water temperature sensor (25) is a supply-side temperature sensor that measures the temperature of the heat source water sent by the heat source device (13). The return side water temperature sensor (26) is arranged on the downstream side of the connection portion of the heat source side bypass pipe (22) in the main return pipe (40). The return side water temperature sensor (26) measures the temperature of the heat source water sent from each subsystem (11, 12) to the heat source device (13) through the main return pipe (40).

<Heat source equipment>
The heat source device (13) is configured to adjust the temperature of the heat source water flowing in from the main return pipe (40) and send the temperature-controlled heat source water to the main feed pipe (30). The heat source device (13) of the present embodiment is composed of a plurality of chiller devices connected in parallel with each other. The chiller device constituting the heat source device (13) performs a refrigeration cycle. Further, this chiller device selectively performs an operation of cooling the heat source water with the refrigerant and an operation of heating the heat source water with the refrigerant.

The heat source device (13) may be composed of a refrigerating device that cools the heat source water by performing a refrigeration cycle, and a boiler that heats the heat source water by the heat of combustion of fuel. Further, the heat source device (13) may include, for example, a cooling tower that directly or indirectly exchanges heat with the atmosphere to cool the heat source water.

<Heat source side controller>
The heat source side controller (15) is configured to perform a control operation for adjusting the capacity of the heat source device (13) and a control operation for adjusting the flow rate of the heat source water. Although not shown, the heat source side controller (15) includes electronic components such as a CPU and a memory. The heat source side controller (15) performs a predetermined control operation based on the program recorded in the memory.

The heat source side controller (15) adjusts the cooling capacity or the heating capacity of the heat source equipment (13) by controlling the operating capacity of the compressor of the chiller device constituting the heat source equipment (13). Further, the heat source side controller (15) adjusts the flow rate of the heat source water by adjusting the number of operating heat source water pumps (21). The measured values of the feed side water temperature sensor (25) and the return side water temperature sensor (26) are input to the heat source side controller (15). The heat source side controller (15) performs the above control operation based on the received measured value.

<Fan coil unit>
As shown in FIG. 1, the fan coil unit (50a, 50b) of the present embodiment is configured as a floor-standing type. The fan coil units (50a, 50b) of each subsystem (11,12) are installed in the perimeter zone (112,122) of the corresponding indoor space (110,120). The type of the fan coil unit (50a, 50b) may be other than the floor-standing type (for example, the ceiling-mounted type).

As shown in FIG. 3, the fan coil unit (50a, 50b) includes an air conditioning heat exchanger (51) and a blower fan (52). The air conditioning heat exchanger (51) is a cross-fin type fin-and-tube heat exchanger. This air-conditioning heat exchanger (51) is connected to a heat source water circuit (20) and exchanges heat with air for the heat source water of the heat source water circuit (20). The fan coil unit (50a, 50b) sucks air from the perimeter zone (112,122) of the indoor space (110,120), exchanges heat with the heat source water in the heat exchanger (51) for air conditioning, and then the indoor space. Blow into the perimeter zone (112,122) at (110,120). That is, the fan coil units (50a, 50b) of each subsystem (11,12) handle the air conditioning load of the perimeter zone (112,122) of the indoor space (110,120) corresponding to each subsystem (11,12).

The perimeter zone is an area of the indoor space that is easily affected by the external conditions of the building (for example, outside air temperature, amount of solar radiation, etc.). Generally, in the plane of the interior of a building, the area of about 3.5 to 5 m from the outer wall (including windows) of the building is the perimeter zone, and the area farther from the outer wall (including windows) of the building than the perimeter zone. Is the interior zone.

<Air conditioner>
As shown in FIG. 1, the air conditioners (60a, 60b) of each subsystem (11,12) are one heat source side unit (61) and the user side of a plurality of (four in this embodiment). It is equipped with units (62a to 62d). Each user-side unit (62a to 62d) is configured to be installed on the ceiling. The type of the user-side unit (62a to 62d) may be other than the ceiling-mounted type (for example, a duct connection type connected to the indoor space via a duct).

Of the multiple user-side units (62a to 62d) of each air conditioner (60a, 60b), some (two in this embodiment) of the user-side units (62a, 62d) are in the indoor space (110,120). It is arranged in the perimeter zone (112,122), and the remaining (two units in this embodiment) user-side units (62b, 62c) are arranged in the interior zone (111,121) of the indoor space (110,120).

In the interior space of a general building, the interior zone is usually wider than the perimeter zone. Therefore, in the present embodiment, the number of user-side units (62b, 62c) provided in the interior zone (111,121) is the same as the number of user-side units (62a, 62d) provided in the perimeter zone (112,122). In a general building, the number of user-side units provided in the interior zone is usually larger than the number of user-side units provided in the perimeter zone.

As shown in FIG. 2, the heat source side unit (61) includes a heat source side circuit (71). In addition, each user-side unit (62a to 62d) contains one user-side circuit (72). In the air conditioner (60a, 60b), the heat source side circuit (71) of the heat source side unit (61) and the user side circuit (72) of each user side unit (62a to 62d) are connected to the liquid side connecting pipe (73). ) And the gas side connecting pipe (74) to form a refrigerant circuit (70). The air conditioner (60a, 60b) performs a vapor compression refrigeration cycle by circulating the refrigerant in the refrigerant circuit (70).

The heat source side circuit (71) includes a compressor (81), a four-way switching valve (82), a heat source side heat exchanger (83), a heat source side expansion valve (84), and a liquid side closing valve (85). And a gas side closing valve (86) are provided. In the heat source side circuit (71), in the compressor (81), the discharge pipe is connected to the first port of the four-way switching valve (82), and the suction pipe is connected to the second port of the four-way switching valve (82). NS. In the four-way switching valve (82), the third port is connected to the secondary side flow path (83b) of the heat source side heat exchanger (83) described later, and the fourth port is connected to the gas side closing valve (86). Will be done. Further, the secondary side flow path (83b) of the heat source side heat exchanger (83) is connected to one end of the heat source side expansion valve (84), and the other end of the heat source side expansion valve (84) is a liquid side closing valve (85). ) Is connected.

The compressor (81) is a fully enclosed scroll compressor. The four-way switching valve (82) has a first state (a state shown by a solid line in FIG. 1) in which the first port communicates with the third port and the second port communicates with the fourth port, and the first. It is a switching valve that switches to a second state (a state shown by a broken line in FIG. 1) in which the port communicates with the fourth port and the second port communicates with the third port. The heat source side expansion valve (84) is an electronic expansion valve having a variable opening degree.

The heat source side heat exchanger (83) is a plate type heat exchanger in which a plurality of primary side flow paths (83a) and a plurality of secondary side flow paths (83b) are formed. In the heat source side heat exchanger (83), the primary side flow path (83a) is connected to the heat source water circuit (20), and the secondary side flow path (83b) is the heat source side circuit (60a, 60b) of the air conditioner (60a, 60b). 71) is connected. Then, the heat source side heat exchanger (83) exchanges heat between the refrigerant flowing in the secondary side flow path (83b) and the heat source water flowing in the primary side flow path (83a).

The user-side circuit (72) of each user-side unit (62a to 62d) is provided with a user-side heat exchanger (88) and a user-side expansion valve (87). In the user-side circuit (72), the user-side heat exchanger (88) and the user-side expansion valve (87) are connected in series. In the user-side circuit (72) of each user-side unit (62a to 62d), the liquid-side end on the user-side expansion valve (87) side passes through the liquid-side connecting pipe (73) to the liquid in the heat source-side circuit (71). Connected to the side closing valve (85), the gas side end on the user side heat exchanger (88) side becomes the gas side closing valve (86) of the heat source side circuit (71) via the gas side connecting pipe (74). Be connected.

The user-side heat exchanger (88) is a cross-fin type fin-and-tube heat exchanger. The user-side heat exchanger (88) exchanges heat with air for the refrigerant in the refrigerant circuit (70). The user-side expansion valve (87) is an electronic expansion valve with a variable opening.

Each user-side unit (62a to 62d) is provided with a user-side fan (63). The user-side fan (63) is a fan for sucking air from the indoor space (110,120) and supplying it to the user-side heat exchanger (88).

In each subsystem (11,12), the utilization side unit (62a, 62d) provided in the perimeter zone (112,122) of the indoor space (110,120) sucks air from the perimeter zone (112,122) and is a utilization side heat exchanger. The air conditioning load in the perimeter zone (112,122) is treated by blowing the air that has passed through (88) into the perimeter zone (112,122). Further, in each subsystem (11,12), the user side unit (62b, 62c) provided in the interior zone (111,121) of the indoor space (110,120) sucks air from the interior zone (111,121) and heats the user side. The air conditioning load in the interior zone (111,121) is processed by blowing the air that has passed through the exchanger (88) into the interior zone (111,121).

The heat source side circuit (71) of the heat source side unit (61) is provided with a discharge pressure sensor (91) and a suction pressure sensor (92). The discharge pressure sensor (91) is connected to a pipe connecting the compressor (81) and the first port of the four-way switching valve (82), and measures the pressure of the refrigerant discharged from the compressor (81). The suction pressure sensor (92) is connected to a pipe connecting the compressor (81) and the second port of the four-way switching valve (82), and measures the pressure of the refrigerant sucked into the compressor (81).

Each user-side unit (62a to 62d) is provided with a liquid-side refrigerant temperature sensor (93), a gas-side refrigerant temperature sensor (94), and a suction temperature sensor (95). The liquid-side refrigerant temperature sensor (93) is a pipe connecting the liquid-side end of the user-side heat exchanger (88) in the user-side circuit (72) (the pipe connecting the user-side heat exchanger (88) and the user-side expansion valve (87). ), And measures the temperature of the refrigerant flowing through this part. It is attached near the gas side end of the gas side refrigerant temperature sensor (94) and the user side heat exchanger (88) in the user side circuit (72), and measures the temperature of the refrigerant flowing through this portion. The suction temperature sensor (95) is the air that is sucked into the user unit (62a to 62d) and sent to the user heat exchanger (88) (that is, the air before passing through the user heat exchanger (88)). Measure the temperature of.

<Air conditioning side controller>
The air conditioners (60a, 60b) of each subsystem (11,12) are equipped with an air conditioning side controller (16). The air conditioning side controller (16) of each air conditioner (60a, 60b) is one for each main controller (17) provided in the heat source side unit (61) and one for each user side unit (62a to 62d). It is composed of an auxiliary controller (18) provided. Although not shown, the main controller (17) of the heat source side unit (61) and the sub controller (18) of each user side unit (62a to 62d) are each provided with electronic components such as a CPU and memory. There is. The main controller (17) and each sub-control (18) perform a predetermined control operation based on the program recorded in the memory.

The sub-controller (18) of each user unit (62a to 62d) is provided with the sub-control unit (62a) according to the air conditioning load processed by the user unit (62a to 62d) provided with the sub-control (18). It is configured to calculate the required value of the evaporation temperature or the condensation temperature of the refrigerant in the user-side heat exchanger (88) of ~ 62d). The details of this control operation performed by the sub-controllator (18) will be described later.

The main controller (17) is based on the required value of the refrigerant evaporation temperature or the condensation temperature calculated by the sub-controller (18) of each user-side unit (62a to 62d), and each user-side unit (62a to 62d). Set the target value (target evaporation temperature or target condensation temperature) of the refrigerant evaporation temperature or condensation temperature in the user-side heat exchanger (88). Then, the main controller (17) adjusts the operating capacity of the compressor (81) based on the set target evaporation temperature or target condensation temperature. At that time, the main controller (17) controls the operating frequency of the compressor (81) (specifically, the frequency of the AC supplied to the motor of the compressor (81)) to control the compressor (81). ) (Specifically, the rotation speed of the compressor (81)) is adjusted. The details of the control operation performed by the main controller (17) will be described later.

In addition to the above control operation, the sub controller (18) performs an operation of adjusting the opening degree of the user side expansion valve (87) and an operation of adjusting the rotation speed of the user side fan (63). Further, in addition to the above control operation, the main controller (17) performs an operation of adjusting the opening degree of the heat source side expansion valve (84) and an operation of operating the four-way switching valve (82).

-Operating operation of air conditioning system-
The operating operation of the air conditioning system (10) will be described. The air conditioning system (10) selectively performs cooling operation and heating operation. The temperature of the heat source water shown below is just an example.

In the cooling season from late spring to early autumn, the heat source device (13) supplies heat source water (medium hot water for cooling) of, for example, about 20 ° C. to the subsystem. On the other hand, in the heating season from late autumn to early spring, the heat source device (13) supplies heat source water (medium hot water for heating) of, for example, about 30 ° C. to the subsystem.

<Cooling operation>
The cooling operation is an operation in which each subsystem (11,12) cools the indoor space (110, 120). In each subsystem (11,12) during cooling operation, the fan coil unit (50a, 50b) handles the sensible heat load in the indoor space (110,120), and the air conditioner (60a, 60b) handles the sensible heat load in the indoor space (110,120). Handles sensible and latent heat loads. In addition, in each subsystem (11,12) during cooling operation, a ventilation device (not shown) supplies air from the outdoor space to the indoor space (110,120) and exhausts air from the indoor space (110,120) to the outdoor space. conduct.

In the cooling operation, the heat source device (13) supplies heat source water (medium hot water for cooling) at about 20 ° C. to each subsystem (11, 12). In the cooling operation, the solenoid valves (43a, 43b) corresponding to each subsystem (11,12) are set to the closed state. Therefore, in the part of the heat source water circuit (20) corresponding to each subsystem (11,12), the heat source side unit (61) and the fan coil unit (50a, 50b) of the air conditioner (60a, 60b) are used. Along with being arranged in series, a fan coil unit (50a, 50b) is arranged upstream of the heat source side unit (61).

The heat source water sent from the heat source device (13) to the main feed pipe (30) is distributed to a plurality of sub feed pipes (31a, 31b). The heat source water that has flowed into each of the sub-feed pipes (31a, 31b) is distributed to a plurality of fan coil units (50a, 50b) connected in parallel (two in this embodiment). The heat source water that has flowed into the fan coil unit (50a, 50b) flows into the air conditioning heat exchanger (51) and exchanges heat with the indoor air that has been sucked into the fan coil unit (50a, 50b), and its temperature rises. do. The fan coil unit (50a, 50b) blows the air cooled in the air conditioning heat exchanger (51) into the perimeter zone (112,122) of the indoor space (110,120).

Usually, the dew point of indoor air is lower than 20 ° C. (that is, the temperature of medium hot water for cooling). Therefore, in the heat exchanger for air conditioning (51), the temperature of the air is lowered, but dew condensation does not occur, so that the amount of water contained in the air (that is, absolute humidity) does not change. Therefore, the fan coil unit (50a, 50b) handles only the sensible heat load in the perimeter zone (112,122).

The heat source water whose temperature has risen to about 23 ° C in the heat exchanger (51) for air conditioning of the fan coil unit (50a, 50b) passes through the sub-return pipe (41a, 41b) to the air conditioner (60a, 60b). It flows into the heat source side unit (61). As will be described in detail later, in the heat source side unit (61) of the air conditioner (60a, 60b), the heat source water absorbs heat from the refrigerant of the refrigerant circuit (70), and the temperature rises to about 30 ° C.

The heat source water flowing out from the heat source side unit (61) of the air conditioners (60a, 60b) of each subsystem (11, 12) flows into the main return pipe (40) and merges, and then the heat source equipment (13). ). The heat source device (13) cools the inflowing heat source water to 20 ° C. and then sends it out to the main feed pipe (30).

In the cooling operation, in the air conditioners (60a, 60b) of each subsystem (11,12), the four-way switching valve (82) is set to the first state (the state shown by the solid line in FIG. 1). Further, in each air conditioner (60a, 60b), the heat source side expansion valve (84) is held in a fully open state, and the opening degree of the utilization side expansion valve (87) of each utilization side unit (62a to 62d) is appropriately adjusted. Will be done. In each air conditioner (60a, 60b), the heat source side heat exchanger (83) functions as a condenser, and the user side heat exchanger (88) of each user side unit (62a to 62d) acts as an evaporator. Perform a functioning refrigeration cycle.

Specifically, the refrigerant discharged from the compressor (81) flows into the secondary side flow path (83b) of the heat source side heat exchanger (83) and dissipates heat to the heat source water flowing through the primary side flow path (83a). And condense. After that, the refrigerant flows into the liquid side connecting pipe (73) and is distributed to the user side circuit (72) of each user side unit (62a to 62d). The refrigerant that has flowed into each user-side circuit (72) is decompressed when passing through the user-side expansion valve (87), then flows into the user-side heat exchanger (88), and then flows into the user-side unit (62a to 62d). It absorbs heat from the sucked indoor air and evaporates. After that, the refrigerant evaporated in the user-side heat exchanger (88) of each user-side circuit (72) flows into the gas-side connecting pipe (74), merges, and is then sucked into the compressor (81). The compressor (81) compresses the sucked refrigerant and then discharges it.

Normally, the evaporation temperature of the refrigerant in the user side heat exchangers (88) of each user side unit (62a to 62d) is set to a value lower than the dew point of the indoor air sucked into the user side units (62a to 62d). NS. Therefore, in the user-side heat exchanger (88), the temperature of the indoor air passing through the heat exchanger (88) decreases, and the moisture contained in the indoor air condenses. Then, the user-side units (62a to 62d) process the sensible heat load and the latent heat load of the indoor space (110,120) by blowing the cooled and dehumidified indoor air into the indoor space (110,120).

The user unit (62a, 62d) located in the perimeter zone (112,122) mainly handles the sensible heat load and latent heat load of the perimeter zone (112,122), and the user unit (111,121) located in the interior zone (111,121). 62b, 62c) mainly handles the sensible heat load and latent heat load of the interior zone (111,121). Therefore, in each indoor space (110,120), the air conditioning load in the perimeter zone (112,122) is processed by the user side unit (62a, 62d) and the fan coil unit (50a, 50b) arranged in the perimeter zone (112,122). , The air conditioning load in the interior zone (111,121) is handled by the user unit (62b, 62c) located in the interior zone (111,121).

<Heating operation>
The heating operation is an operation in which each subsystem (11,12) heats the indoor space (110, 120). In each subsystem (11,12) during heating operation, the fan coil unit (50a, 50b) handles the sensible heat load in the indoor space (110,120), and the air conditioner (60a, 60b) handles the sensible heat load in the indoor space (110,120). Handle the sensible heat load of. In addition, in each subsystem (11,12) during heating operation, a ventilation device (not shown) supplies air from the outdoor space to the indoor space (110,120) and exhausts air from the indoor space (110,120) to the outdoor space. conduct. Further, in the heating operation, the air is humidified by the ventilation device.

In the heating operation, the heat source device (13) supplies heat source water (medium hot water for heating) at about 30 ° C. to each subsystem (11, 12). In the heating operation, the solenoid valves (43a, 43b) corresponding to each subsystem (11,12) are set to the closed state. Therefore, in the part of the heat source water circuit (20) corresponding to each subsystem (11,12), the heat source side unit (61) and the fan coil unit (50a, 50b) of the air conditioner (60a, 60b) are used. Along with being arranged in series, a fan coil unit (50a, 50b) is arranged upstream of the heat source side unit (61).

The heat source water sent from the heat source device (13) to the main feed pipe (30) is distributed to a plurality of sub feed pipes (31a, 31b). The heat source water that has flowed into each of the sub-feed pipes (31a, 31b) is distributed to a plurality of fan coil units (50a, 50b) connected in parallel (two in this embodiment). The heat source water that has flowed into the fan coil unit (50a, 50b) flows into the air conditioning heat exchanger (51) and exchanges heat with the indoor air that has been sucked into the fan coil unit (50a, 50b), and its temperature drops. do. The fan coil unit (50a, 50b) blows the air heated in the air conditioning heat exchanger (51) into the perimeter zone (112,122) of the indoor space (110,120). The fan coil unit (50a, 50b) handles only the sensible heat load in the perimeter zone (112,122).

The heat source water whose temperature has dropped to about 26 ° C in the heat exchanger (51) for air conditioning of the fan coil unit (50a, 50b) passes through the sub-return pipe (41a, 41b) to the air conditioner (60a, 60b). It flows into the heat source side unit (61). As will be described in detail later, in the heat source side unit (61) of the air conditioner (60a, 60b), the heat source water dissipates heat to the refrigerant of the refrigerant circuit (70), and the temperature drops to about 20 ° C.

The heat source water flowing out from the heat source side unit (61) of the air conditioners (60a, 60b) of each subsystem (11, 12) flows into the main return pipe (40) and merges, and then the heat source equipment (13). ). The heat source device (13) heats the inflowing heat source water to 30 ° C. and then sends it out to the main feed pipe (30).

In the heating operation, in the air conditioners (60a, 60b) of each subsystem (11,12), the four-way switching valve (82) is set to the second state (the state shown by the broken line in FIG. 1). Further, in each air conditioner (60a, 60b), the opening degree of the heat source side expansion valve (84) and the opening degree of the use side expansion valve (87) of each user side unit (62a to 62d) are appropriately adjusted. NS. In each air conditioner (60a, 60b), the user side heat exchanger (88) of each user side unit (62a to 62d) functions as a condenser, and the heat source side heat exchanger (83) acts as an evaporator. Perform a functioning refrigeration cycle.

Specifically, the refrigerant discharged from the compressor (81) flows into the gas-side connecting pipe (74) and is distributed to the user-side circuits (72) of each user-side unit (62a to 62d). The refrigerant that has flowed into each user-side circuit (72) flows into the user-side heat exchanger (88), dissipates heat to the indoor air sucked into the user-side units (62a to 62d), and condenses. The refrigerant condensed in the user-side heat exchanger (88) of each user-side circuit (72) flows into the liquid-side connecting pipe (73) after passing through the user-side expansion valve (87) and joins. After that, the refrigerant is decompressed when passing through the heat source side expansion valve (84), then flows into the secondary side flow path (83b) of the heat source side heat exchanger (83), and flows through the primary side flow path (83a). It absorbs heat from the flowing heat source water and evaporates. The refrigerant evaporated in the heat source side heat exchanger (83) is sucked into the compressor (81). The compressor (81) compresses the sucked refrigerant and then discharges it. Then, the user-side units (62a to 62d) process the sensible heat load in the indoor space (110,120) by blowing the heated indoor air into the indoor space (110,120).

The user units (62a, 62d) located in the perimeter zone (112,122) mainly handle the sensible heat load in the perimeter zone (112,122) and the user units (62b, 62c) located in the interior zone (111,121). ) Mainly handles the sensible heat load in the interior zone (111,121). Therefore, in each indoor space (110,120), the air conditioning load in the perimeter zone (112,122) is processed by the user side unit (62a, 62d) and the fan coil unit (50a, 50b) arranged in the perimeter zone (112,122). , The air conditioning load in the interior zone (111,121) is handled by the user unit (62b, 62c) located in the interior zone (111,121).

-Control operation of the heat source side controller-
As described above, the heat source side controller (15) performs a control operation for adjusting the capacity of the heat source device (13). The control operation performed by the heat source side controller (15) will be described.

The heat source side controller (15) adjusts the capacity of the heat source device (13) so that the measured value of the feed side water temperature sensor (25) reaches a predetermined target temperature. That is, in the cooling operation of the air conditioning system (10), the heat source side controller (15) uses the heat source device (15) so that the measured value of the feed side water temperature sensor (25) becomes 20 ° C., which is the target temperature for cooling. 13) Adjust the cooling capacity. Further, in the heating operation of the air conditioning system (10), the heat source side controller (15) uses the heat source device (15) so that the measured value of the feed side water temperature sensor (25) becomes the target temperature for heating of 30 ° C. 13) Adjust the heating capacity. The heat source side controller (15) adjusts the capacity of the heat source device (13) by adjusting the operating capacity of the compressor provided in the chiller device which is the heat source device (13).

The heat source side controller (15) also performs a control operation for adjusting the flow rate of the heat source water. The heat source side controller (15) increases the flow rate of the heat source water by increasing the number of operating heat source water pumps (21) when the flow rate of the heat source water is too low, while increasing the flow rate of the heat source water when the flow rate of the heat source water is too high. Reduce the flow rate of heat source water by reducing the number of operating heat source water pumps (21).

-Control operation of the air-conditioning side controller (cooling operation)-
The control operation performed by the air conditioning side controller (16) during the cooling operation of the air conditioning system (10) will be described.

<Secondary controller>
In each user-side unit (62a-62d), the sub-controller (18) calculates the evaporation temperature of the refrigerant so that the user-side unit (62a-62d) can exert the required cooling capacity. At that time, the sub-controller (18) is based on the measured values of the temperature sensors (93,94,95) provided in the user-side units (62a to 62d), the rotation speed of the user-side fan (63), and the like. , Calculate the required value of the refrigerant evaporation temperature. That is, the sub-controller (18) calculates the required value of the evaporation temperature of the refrigerant in consideration of the cooling load to be processed by the user-side units (62a to 62d) provided with the sub-controller (18). .. The sub-controllers (18) of each user unit (62a to 62d) transmit the calculated required value of the refrigerant evaporation temperature to the main controller (17).

<Main controller>
The main controller (17) compares the required values of the refrigerant evaporation temperature transmitted from the sub-controls (18) of each user unit (62a to 62d), and sets the lowest value as the target of the refrigerant evaporation temperature. Set to a value (target evaporation temperature). Then, the main controller (17) adjusts the operating capacity of the compressor (81) based on the set target evaporation temperature.

Specifically, the main controller (17) calculates the saturation pressure of the refrigerant at the target evaporation temperature (that is, the pressure when the saturation temperature of the refrigerant becomes the target evaporation temperature), and sets that value as the target evaporation pressure. Then, the main controller (17) adjusts the operating frequency of the compressor (81) so that the measured value of the suction pressure sensor (92) becomes the target evaporation pressure. At that time, the main controller (17) lowers the operating frequency of the compressor (81) if the measured value of the suction pressure sensor (92) is lower than the target evaporation pressure, and the measured value of the suction pressure sensor (92) is the target. If it is higher than the evaporation pressure, increase the operating frequency of the compressor (81).

-Control operation of the air-conditioning side controller (heating operation)-
The control operation performed by the air conditioning side controller (16) during the heating operation of the air conditioning system (10) will be described.

<Secondary controller>
In each user-side unit (62a-62d), the sub-controller (18) calculates the condensation temperature of the refrigerant so that the user-side unit (62a-62d) can exert the required heating capacity. At that time, the sub-controller (18) is based on the measured values of the temperature sensors (93,94,95) provided in the user-side units (62a to 62d), the rotation speed of the user-side fan (63), and the like. , Calculate the required value of the refrigerant condensation temperature. That is, the sub-controller (18) calculates the required value of the condensation temperature of the refrigerant in consideration of the heating load to be processed by the user-side units (62a to 62d) provided with the sub-controller (18). .. The sub-controllers (18) of each user unit (62a to 62d) transmit the calculated required value of the refrigerant condensation temperature to the main controller (17).

<Main controller>
The main controller (17) compares the required values of the refrigerant condensation temperature transmitted from the sub-controls (18) of each user unit (62a to 62d), and sets the highest value as the target of the refrigerant condensation temperature. Set to the value (target condensation temperature). Then, the main controller (17) adjusts the operating capacity of the compressor (81) based on the set target condensation temperature.

Specifically, the main controller (17) calculates the saturation pressure of the refrigerant at the target condensation temperature (that is, the pressure when the saturation temperature of the refrigerant reaches the target condensation temperature), and sets that value as the target condensation pressure. Then, the main controller (17) adjusts the operating frequency of the compressor (81) so that the measured value of the discharge pressure sensor (91) becomes the target condensing pressure. At that time, the main controller (17) lowers the operating frequency of the compressor (81) if the measured value of the discharge pressure sensor (91) is higher than the target condensing pressure, and the measured value of the discharge pressure sensor (91) is the target. If it is lower than the condensation pressure, increase the operating frequency of the compressor (81).

-Effects of the embodiment 1-
Generally, the perimeter zone (112,122) near the outer wall of the building has a higher air conditioning load than the interior zone (111,121). Therefore, if only the user unit (62a, 62d) of the air conditioner (60a, 60b) is provided in the perimeter zone, the air conditioning that the user unit (62a, 62d) of the perimeter zone (112,122) should normally handle. The load is larger than the air conditioning load to be processed by the user unit (62b, 62c) in the interior zone (111,121).

On the other hand, the main controller (17) of the air conditioner (60a, 60b) is one of the required values of the refrigerant evaporation temperature calculated by the sub-controller (18) of each user unit (62a to 62d) during the cooling operation. The lowest value is set as the target evaporation temperature, and the highest value among the required values of the refrigerant condensation temperature calculated by the sub-controllers (18) of each user unit (62a to 62d) is set as the target evaporation temperature during heating operation. Therefore, when only the user-side unit (62a, 62d) of the air conditioner (60a, 60b) is provided in the perimeter zone (112,122), the main controller (17) is the user-side unit (112,122) of the perimeter zone (112,122). The required value of the refrigerant evaporation / condensation temperature calculated by the sub-controller (18) of 62a, 62d) is set to the target evaporation / condensation temperature, and compression is performed based on the target evaporation / condensation pressure corresponding to this target evaporation / condensation temperature. Adjust the operating capacity of the machine (81). Therefore, in this case, for the user-side unit (62b, 62c) in the interior zone (111,121), the evaporation pressure (evaporation temperature) of the refrigerant in the user-side heat exchanger (88) becomes too low during the cooling operation, and during the heating operation. The condensation pressure (condensation temperature) of the refrigerant in the heat exchanger (88) on the user side becomes too high, and the power consumption of the compressor (81) increases.

This problem will be described with a concrete example. Temporarily, during the cooling operation, the required value of the refrigerant evaporation temperature calculated by the sub-controller (18) of the user-side unit (62b, 62c) of the interior zone (111,121) is 10 ° C., and the perimeter zone (112,122) is used. Assuming that the required value of the refrigerant evaporation temperature calculated by the sub-controllers (18) of the side units (62a, 62d) is 6 ° C., the main controller (17) sets the target evaporation temperature to 6 ° C. Then, the main controller (17) sets the target evaporation pressure to the saturation pressure corresponding to the temperature of 6 ° C. instead of the saturation pressure corresponding to the temperature of 10 ° C. Therefore, for the user-side unit (62b, 62c) in the interior zone (111,121), the evaporation temperature of the refrigerant in the user-side heat exchanger (88) becomes too low (that is, the low pressure in the refrigeration cycle becomes too low). , The power consumption of the compressor (81) increases.

On the other hand, in the air conditioning system (10) of the present embodiment, the perimeter zone (112,122) is provided by both the user side unit (62a, 62d) and the fan coil unit (50a, 50b) provided in the perimeter zone (112,122). ) Is processing the air conditioning load. Therefore, compared to the case where only the user side unit (62a, 62d) of the air conditioner (60a, 60b) is provided in the perimeter zone (112,122), the user side unit (62a, 62d) of the perimeter zone (112,122) processes. The air conditioning load to be reduced becomes smaller. Therefore, in the present embodiment, the air conditioning load to be processed by the user side unit (62a, 62d) in the perimeter zone (112,122) and the air conditioning load to be processed by the user side unit (62b, 62c) in the interior zone (111,121). The difference between is small. That is, in the present embodiment, the air conditioning load to be processed by each user unit (62a to 62d) of the air conditioner (60a, 60b) is averaged.

Therefore, in the present embodiment, the required value of the refrigerant evaporation / condensation temperature calculated by the sub-controller (18) of the user-side unit (62a, 62d) of the perimeter zone (112,122) and the user-side of the interior zone (111,121). The difference from the required value of the refrigerant evaporation / condensation temperature calculated by the sub-controller (18) of the unit (62b, 62c) becomes small. As a result, the target evaporation temperature set by the main controller (17) during the cooling operation is compared with the case where only the user side unit (62a, 62d) of the air conditioner (60a, 60b) is provided in the perimeter zone (112,122). The value of is increased, and the value of the target condensation temperature set by the main controller (17) during the heating operation is decreased.

That is, assuming that the air conditioning load of the interior zone (111,121) and the air conditioning load of the perimeter zone (112,122) are the same as the above specific example, the user side unit (62b, 62c) of the interior zone (111,121) The required value of the refrigerant evaporation temperature calculated by the sub controller (18) is 10 ° C., while the required value of the refrigerant evaporation temperature calculated by the sub controller (18) of the user side unit (62a, 62d) in the perimeter zone (112,122) The required value is, for example, 9 ° C. Then, the main controller (17) sets the target evaporation temperature to 9 ° C., sets the target evaporation pressure to the saturation pressure corresponding to the temperature of 9 ° C., and adjusts the operating capacity of the compressor (81).

As described above, according to the present embodiment, when comparing the cases where the air conditioning load of the indoor space (110, 120) is the same, the target evaporation pressure can be set to a higher value than before during the cooling operation, and the target condensation pressure during the heating operation. Can be set to a lower value than before. As a result, the difference between the low pressure of the refrigeration cycle (ie, the pressure of the refrigerant sucked into the compressor (81)) and the high pressure of the refrigeration cycle (ie, the pressure of the refrigerant discharged from the compressor (81)) is reduced. can. Therefore, according to the present embodiment, it is possible to reduce the power consumption of the compressor (81).

Further, in the air conditioning system (10) of the present embodiment, the fan coil unit (50a, 50b) is connected to the heat source water circuit (20) to which the heat source side unit (61) of the air conditioner (60a, 60b) is connected. However, the air conditioner (60a, 60b) and the fan coil unit (50a, 50b) handle the air conditioning load in the indoor space (110,120). Therefore, the air conditioning load finally processed by the heat source equipment (13) is equivalent to that of the conventional air conditioner system (10) in which only the air conditioners (60a, 60b) are connected to the heat source water circuit (20). .. Therefore, according to the present embodiment, the power consumption of the air conditioner (60a, 60b) can be reduced while suppressing the power consumption of the heat source device (13) to the same level as the conventional one, and as a result, the entire air conditioner system (10) can be reduced. Power consumption can be reduced.

-Effect of embodiment 2-
In each subsystem (11,12) of the air conditioning system (10) of the present embodiment, the fan coil unit (50a, 50b) and the heat source side unit (61) of the air conditioner (60a, 60b) are heat source water. Arranged in series in circuit (20). Then, the heat source water flowing from the heat source device (13) to the main feed pipe (30) first flows into the fan coil unit (50a, 50b) and exchanges heat with the air, and then the air conditioner (60a, 60b). It flows into the heat source side unit (61), exchanges heat with the refrigerant, and is then sent back to the heat source equipment (13). Therefore, the temperature of the heat source water sent from the heat source device (13) is higher than that in the case where the fan coil unit (50a, 50b) and the heat source side unit (61) are arranged in parallel in the heat source water circuit (20). , The difference from the temperature of the heat source fluid flowing into the heat source device (13) becomes large.

If the amount of heat transferred by the heat source water is the same, the larger the difference between the temperature of the heat source water sent from the heat source device (13) and the temperature of the heat source water flowing into the heat source device (13), the greater the difference in the heat source water. The flow rate is small. Therefore, in the present embodiment, the heat source fluid circulating in the heat source water circuit (20) is compared with the case where the fan coil unit (50a, 50b) and the heat source side unit (61) are arranged in parallel in the heat source water circuit (20). The flow rate of the heat source water pump (21) can be reduced.

-Effect of embodiment 3-
As described above, the heat source side controller (15) performs a control operation for adjusting the capacity of the heat source device (13) by using the measured value of the feed side water temperature sensor (25). That is, the heat source side controller (15) executes the above-mentioned control operation without communicating with the air conditioner (60a, 60b) and the fan coil unit (50a, 50b).

Further, the air conditioning side controller (16) controls the operation of the air conditioner (60a, 60b) by using the measured values of the sensors (91 to 95) provided in the air conditioner (60a, 60b). That is, the air conditioning side controller (16) executes this control operation without communicating with the heat source device (13) and the heat source side controller (15).

As described above, according to the present embodiment, the heat source equipment (13) and the heat source side controller (15) arranged on the primary side of the air conditioning system (10) and the secondary side of the air conditioning system (10). The types and amounts of data transmitted and received between the arranged air conditioners (60a, 60b) and fan coil units (50a, 50b) can be significantly reduced or virtually eliminated. Therefore, according to the present embodiment, the operation of the entire air conditioning system (10) is appropriately controlled according to the air conditioning load of the indoor space (110, 120), and the control system of the entire air conditioning system (10) is simplified. be able to.

− Modifications of the embodiment 1-
The air conditioning system (10) of the present embodiment simultaneously cools and heats a mixture of a subsystem (11,12) for cooling the indoor space (110,120) and a subsystem (11,12) for heating the indoor space (110,120). You can also drive. In this simultaneous cooling and heating operation, it is desirable that the temperature of the heat source water sent from the heat source device (13) to the main feed pipe (30) is set to about 25 ° C.

− Modified example of the embodiment 2-
In the air conditioning system (10) of the present embodiment, even if the heat source side controller (15) is configured to adjust the flow rate of the heat source water by adjusting the rotation speed of the heat source water pump (21). good. In this case, as shown in FIG. 1, a plurality of heat source water pumps (21) may be provided in parallel in the main feed pipe (30) of the heat source water circuit (20), or the heat source water pumps (21) may be provided in parallel. ) May be provided.

As described above, the present invention is useful for an air conditioning system including an air conditioner having a heat source side unit for exchanging heat with a heat source fluid and a plurality of indoor units.

10 Air conditioning system
13 Heat source equipment
15 Heat source side controller
16 Air conditioning side controller
20 Heat source water circuit (heat source fluid circuit)
25 Feed side water temperature sensor (Supply side temperature sensor)
60a, 60b air conditioner
61 Heat source side unit
62a, 62b, 62c, 62d User unit
70 Refrigerant circuit
110,120 Indoor space
112,122 Perimeter Zone

Claims (3)

The heat source fluid circuit (20) through which the heat source fluid circulates,
A heat source device (13) that cools or heats the heat source fluid that circulates in the heat source fluid circuit (20), and
The heat source side unit (61) connected to the heat source fluid circuit (20), and each of the heat source side units (62a to 62d) for supplying conditioned air to the indoor space (110, 120). An air conditioner (60a) that performs a refrigeration cycle by exchanging heat with the heat source fluid for the refrigerant circulating in the refrigerant circuit (70) formed by connecting (61) and the user-side units (62a to 62d) with pipes. , 60b) and
For the air conditioners (60a, 60b), the evaporation temperature or the condensation temperature of the refrigerant in the user-side units (62a to 62d) shall be the target values set according to the air conditioning load in the indoor space (110,120). , While the air conditioner side controller (16) that controls the operation of the above air conditioner (60a, 60b) is provided,
A fan coil unit (50a, 50b) that is connected to the heat source fluid circuit (20) and supplies conditioned air whose temperature is adjusted by heat exchange with the heat source fluid to the perimeter zone (112, 122) of the indoor space (110, 120). further comprising a,
In the heat source fluid circuit (20), the fan coil unit (50a, 50b) is arranged upstream of the heat source side unit (61) of the air conditioner (60a, 60b) and cooled by the heat source device (13). An air conditioning system characterized in that the heat source fluid that has been or is heated passes through the fan coil unit (50a, 50b) and then passes through the heat source side unit (61). In claim 1,
The fan coil unit (50a, 50b) is an air conditioning system characterized in that it processes only the sensible heat load of the perimeter zone (112,122). In claim 1 or 2,
A supply-side temperature sensor (25) that measures the temperature of the heat source fluid flowing out of the heat source device (13), and
It is characterized by being equipped with a heat source side controller (15) that adjusts the capacity of the heat source device (13) so that the measured value of the supply side temperature sensor (25) is maintained at a predetermined target temperature. Air conditioning system.

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