WO2014016865A1

WO2014016865A1 - Air-conditioning device

Info

Publication number: WO2014016865A1
Application number: PCT/JP2012/004708
Authority: WO
Inventors: 智一川越; 嶋本　大祐; 幸志東; 孝好本多
Original assignee: 三菱電機株式会社
Priority date: 2012-07-24
Filing date: 2012-07-24
Publication date: 2014-01-30
Also published as: EP2878902A1; EP2878902A4; JP5774225B2; US20150128628A1; JPWO2014016865A1; CN104364590B; CN104364590A; EP2878902B1

Abstract

An air-conditioning device (100) having: a heat-source-side unit (1) equipped with a compressor (10) that compresses a refrigerant and a heat-source-side heat exchanger (12) that exchanges heat between air and the refrigerant; multiple usage-side units (2a, 2b) each of which is equipped with a usage-side heat exchanger (26a) that exchanges heat between air and a heat medium; and multiple intermediate heat exchangers (15a, 15b) that are connected to the heat-source-side unit (1) by means of refrigerant pipes and are connected to the usage-side units (2a, 2b) by means of heat medium pipes, and that exchange heat between the refrigerant and the heat medium. A subject determination means (521) detects the respective condensation state of each usage-side unit (2a, 2b), and individually determines from the condensation states whether to perform condensation suppression control for controlling the condensation in each usage-side unit (2a, 2b). A usage-side unit (2b) for which the subject determination means (521) has determined that condensation suppression control is to be performed is connected to the intermediate heat exchanger (15b), which is the heat exchanger of the multiple intermediate heat exchangers (15a, 15b) which is used for adjustments. Then, a refrigerant circuit control means (53) controls the temperature of the refrigerant flowing into the adjustment-use intermediate heat exchanger (15b) such that the temperature T of the heat medium flowing into the usage-side unit (2b) is within a prescribed target temperature range.

Description

Air conditioner

The present invention relates to an air conditioner capable of air-conditioning operation using cold water or hot water generated using a heat pump cycle (refrigeration cycle).

An air conditioner that is equipped with a heat pump cycle, exchanges heat between the refrigerant and water, transports cold water or hot water and air-conditions indoors, can cope with refrigerant leakage, and can save CFCs. ing. As such, a compressor, an outdoor heat exchanger, an expansion device, an indoor heat exchanger, and an air-conditioning refrigerant system heat exchanger having an accumulator are used as a water heat exchanger, and are generated by a water heat exchanger. There is an air conditioner that can provide cooling operation and heating operation simultaneously by conveying cold water or hot water using a pump and a valve or the like (see, for example, Patent Document 1). In the air conditioner described in Patent Document 1, a unit having a refrigerant-water heat exchanger and a water-type indoor unit are connected to a heat source unit. It is possible to make air conditioning possible.

International Publication No. 2010/049998 (Fig. 3 etc.)

However, when the carrier fluid that exchanges heat with air is water as in Patent Document 1, there is a problem that condensation is likely to occur due to the large specific heat. In particular, if some of the indoor units that are in cooling operation are indoor units dedicated to natural convection (for example, chilled beams), the amount of heat exchange by natural convection is small, so the entire indoor unit is in a low temperature state. There is a problem that condensation tends to occur. Here, when a plurality of indoor units are provided as in Patent Document 1, it is desirable to suppress condensation for each indoor unit. However, there is a problem that it is difficult to perform control for suppressing the occurrence of condensation for each individual indoor unit.

The present invention has been made to solve the above-described problems, and is an air conditioner capable of individually controlling dew condensation control on a use side unit that may cause dew condensation among a plurality of use side units. The purpose is to provide.

An air conditioner according to the present invention includes a compressor that compresses refrigerant, a heat source side unit that includes a heat source side heat exchanger that performs heat exchange between air and the refrigerant, and air and a heat medium. Between a plurality of usage-side units having usage-side heat exchangers that perform heat exchange, and between the refrigerant and the heat medium that are connected to the heat-source side unit by refrigerant piping and connected to the usage-side unit by heat medium piping A plurality of intermediate heat exchangers that perform heat exchange at each of them, a heat medium flow switching device that switches a combination of connections between each use-side unit and each intermediate heat exchanger, and a dew condensation state in each use-side unit. Condensation detection means, and object determination means for determining whether or not to perform condensation suppression control for suppressing the condensation on each use side unit from the state of condensation detected by the condensation detection means, and condensation by the object determination means The temperature detection means for detecting the temperature of the heat medium flowing into the use side unit determined to perform the control control as the heat medium temperature, and the use side unit determined to perform the condensation suppression control by the object determination means include a plurality of Heat medium circuit control means for controlling the heat medium flow switching device to be connected to the adjustment intermediate heat exchanger assigned for dew condensation suppression control among the intermediate heat exchanger, and detected by the temperature detection means And a refrigerant circuit control means for controlling the temperature of the refrigerant flowing into the adjustment intermediate heat exchanger so that the heat medium temperature falls within a predetermined target set temperature range.

According to the present invention, when any one or more usage-side units among the plurality of usage-side units is in a state where condensation occurs or there is a possibility that condensation will occur, heat is generated using the adjustment intermediate heat exchanger. In order to suppress condensation by raising the temperature of the medium and flowing the heat medium through the use side heat exchanger, it is possible to suppress condensation on a specific use side unit without stopping normal operation of other use side units. It becomes possible.

It is a block diagram of the air conditioning apparatus 100 which concerns on Embodiment 1 of this invention. It is a block diagram which shows an example of the utilization side unit control means of FIG. It is a block diagram which shows an example of the intermediate unit control means of FIG. It is a control flowchart of the utilization side unit control means in the dew condensation suppression control of the air conditioning apparatus 100 which concerns on Embodiment 1 of this invention. It is a control flowchart of the intermediate | middle unit control means in the dew condensation suppression control of the air conditioning apparatus 100 which concerns on Embodiment 1 of this invention.

Embodiment 1 FIG.
(Configuration of air conditioner)
FIG. 1 is a configuration diagram of an air-conditioning apparatus 100 according to Embodiment 1 of the present invention. The air conditioning apparatus 100 of FIG. 1 is installed in a building, a condominium, a hotel, or the like, and supplies a cooling load and a heating load by using a heat pump cycle (refrigeration cycle) that circulates a refrigerant. The air conditioner 100 employs a method of indirectly using the heat source side refrigerant. That is, the cold or warm heat stored in the heat source side refrigerant is transmitted to a heat medium flowing through a circulation circuit different from that of the heat source side refrigerant, and the air-conditioning target space is cooled or heated by the cold heat or heat stored in the heat medium.

The air conditioner 100 includes one heat source unit 1 that is a heat source unit, a plurality of use side units (indoor units) 2a and 2b, and an intermediate unit 3. The heat source unit 1 and the intermediate unit 3 are connected by a refrigerant pipe (a high-pressure main pipe 5a and a low-pressure main pipe 5b), and the

use side units

2a and 2b and the intermediate unit 3 are connected by a heat medium pipe. The cold or warm heat generated by the heat source unit 1 is transmitted to the

use side units

2a and 2b via the intermediate unit 3.

The heat source unit 1 is installed in a space outside a building such as a building (for example, a rooftop or the like), and supplies cold energy or heat to the

use side units

2a and 2b via the intermediate unit 3. As described above, the heat source unit 1 has been described as being installed in the outer space, but the present invention is not limited to this. For example, the heat source unit 1 may be installed in an enclosed space such as a machine room with a ventilation opening. If the waste heat can be exhausted outside the building by an exhaust duct, the heat source unit 1 is installed inside the building. Alternatively, when the water-cooled heat source unit 1 is used, it may be installed inside a building. Even if the heat source unit 1 is installed in such a place, no particular problem occurs.

The

use side units

2a and 2b are, for example, ceiling cassette type indoor units, which are arranged at a position where cooling air or heating air can be supplied to the air conditioning target space inside the building, and the cooling air is supplied to the air conditioning target space. Alternatively, heating air is supplied.

In addition, although the case where use

side unit

2a, 2b is a ceiling cassette type was demonstrated to the example, it is not limited to this, A ceiling embedding type, a ceiling suspended type, etc., directly to an air-conditioning object space, a duct, etc. As long as the heating air or the cooling air can be blown out, any type of air may be used. In addition, FIG. 1 shows an example in which two usage-

side units

2a and 2b are configured, but the configuration is not limited to two, and three or more usage-side units are configured. Also good.

The intermediate unit 3 transmits the cold or warm heat supplied from the heat source unit 1 to the

use side units

2a and 2b, the refrigerant flowing in the refrigerant circuit A on the heat source unit 1 side, the use side unit 2a, Heat exchange is performed with the heat medium flowing in the heat medium circuit B on the 2b side. The intermediate unit 3 is configured as a separate housing from the heat source unit 1 and the

use side units

2a and 2b so that it can be installed at a position different from the outer space and the air-conditioning target space. The intermediate unit 3 is connected to the heat source unit 1 by the high-pressure main pipe 5a and the low-pressure main pipe 5b, and is connected to the

use side units

2a and 2b by the

heat medium pipes

27 and 28.

(Configuration of heat source unit 1)
The heat source unit 1 includes a compressor 10, a first refrigerant flow switching device 11, a heat source side heat exchanger 12, and an accumulator 19, which are connected in series by a refrigerant pipe. Furthermore, the heat source unit 1 includes a heat source unit control means 51 that performs frequency control of the compressor 10, flow path switching control of the first refrigerant flow path switch 11, and the like. The compressor 10 sucks a refrigerant in a gas state and compresses the refrigerant to a high temperature / high pressure state. For example, the compressor 10 may be configured using various types such as a reciprocating, a rotary, a scroll, or a screw type. What is necessary is just to be comprised with the inverter compressor etc. which can control capacity | capacitance.

1st refrigerant | coolant flow path switch 11 is comprised, for example with a four-way valve etc., and switches a refrigerant | coolant flow path according to the requested | required operation mode. Specifically, the refrigerant flow path (heating flow path) during the heating operation (the heating only operation mode and the heating main operation mode described later) and the refrigerant during cooling operation (the all cooling operation mode and the cooling main operation mode described later). The flow path (cooling flow path) is switched.

The heat source side heat exchanger 12 performs heat exchange between the air supplied from the blower 12a and the refrigerant, functions as an evaporator during heating operation, and serves as a radiator (gas cooler) during cooling operation. Function. As described above, the heat source side heat exchanger 12 is a pneumatic heat exchanger that performs heat exchange with the air supplied from the blower 12a, but is not limited thereto, and is water or brine. It is good also as what is comprised with the water heat exchanger which uses as a heat source.

The accumulator 19 is provided on the suction side of the compressor 10, and surplus refrigerant due to the difference between the heating operation and the cooling operation, and a surplus with respect to a transient operation change (for example, a change in the number of indoor units operated). Stores refrigerant.

Further, the heat source unit 1 is provided with a flow path forming part 13 constituted by a first connection pipe 4a, a second connection pipe 4b, and check valves 13a to 13d. In the heat source unit 1, the first connection pipe 4 a includes a refrigerant pipe that connects the first refrigerant flow switch 11 and a check valve 13 d described later, a high-pressure main pipe 5 a that causes the refrigerant to flow out of the heat source unit 1, and The refrigerant pipe for connecting the check valve 13a is connected. In the heat source unit 1, the second connection pipe 4 b includes a refrigerant pipe that connects a low-pressure main pipe 5 b that allows the refrigerant to flow into the heat source unit 1 and a check valve 13 d described later, a heat source side heat exchanger 12, and a check described later. The refrigerant pipe for connecting the valve 13a is connected. By providing this flow path forming part 13, the flow of the refrigerant flowing into the intermediate unit 3 through the high-pressure main pipe 5a and the low-pressure main pipe 5b is made to be in a certain direction regardless of the operation required by the

use side units

2a and 2b. Can do.

The check valve 13 a is provided in a refrigerant pipe connecting the heat source side heat exchanger 12 and the high pressure main pipe 5 a that causes the refrigerant to flow out of the heat source unit 1, and only in the direction from the heat source side heat exchanger 12 to the intermediate unit 3. A refrigerant is circulated. The check valve 13b is provided in the first connection pipe 4a, and causes the refrigerant discharged from the compressor 10 to flow only in the direction toward the intermediate unit 3 during the heating operation. The check valve 13c is provided in the second connection pipe 4b, and causes the refrigerant returned from the intermediate unit 3 during the heating operation to flow only in the direction toward the heat source side heat exchanger 12. The check valve 13d is provided in a refrigerant pipe that connects the first refrigerant flow switch 11 and the low-pressure main pipe 5b that allows the refrigerant to flow into the heat source unit 1, and the first refrigerant flow switch 11 from the low-pressure main pipe 5b. The refrigerant is circulated only in the direction of

(Configuration of

usage side units

2a and 2b)
The plurality of usage-

side units

2a and 2b include usage-

side heat exchangers

26a and 26b,

suction temperature sensors

32a and 32b, and

suction humidity sensors

33a and 33b, respectively. Further, the

use side units

2a and 2b receive the suction temperature information detected by the

suction temperature sensors

32a and 32b and the suction humidity information detected by the

suction humidity sensors

33a and 33b, respectively, and calculate based on each information. Use side unit control means 52a, 52b for carrying out the above.

The use

side heat exchangers

26a and 26b are connected to a heat medium pipe 27 through which the heat medium flowing out from the intermediate unit 3 flows and a heat medium pipe 28 through which the heat medium flowing out from the use side unit 2, respectively. Further, the use

side heat exchangers

26a and 26b function as a radiator (gas cooler) during heating operation, and function as a heat absorber during cooling operation. The use-

side heat exchangers

26a and 26b exchange heat between indoor air supplied from a fan (not shown) such as a fan and a heat medium to give cold or hot air to the air-conditioning target space. Heating air or cooling air to be supplied is generated. The use-

side heat exchangers

26a and 26b have been described with respect to the case where they are blown by a fan or the like. However, the use-

side heat exchangers

26a and 26b are from coil-shaped heat exchangers with a rough fin pitch that are installed on the ceiling using natural convection called so-called chilled beams. It may be.

(Configuration of intermediate unit 3)
The intermediate unit 3 includes an expansion device 9, a plurality of intermediate heat exchangers 15a and 15b, a plurality of refrigerant expansion devices 16a and 16b, a liquid refrigerant supply valve 17a, a gas refrigerant supply valve 17b, and second refrigerant flow switching devices 18a and 18b. , Pumps 21a and 21b, secondary side water

flow path switchers

22a and 22b, primary side water

flow path switchers

23a and 23b, and heat

medium adjusting valves

25a and 25b.

The intermediate heat exchangers 15a and 15b exchange heat between the refrigerant and the heat medium, and the cold or warm heat generated in the heat source unit 1 and stored in the refrigerant is transmitted to the heat medium. The intermediate heat exchanger 15a is provided between the refrigerant expansion device 16a and the second refrigerant flow switching unit 18a in the refrigerant circuit A. The intermediate heat exchanger 15b is provided between the refrigerant expansion device 16b and the second refrigerant flow switching unit 18b in the refrigerant circuit A.

The refrigerant throttle devices 16a and 16b are, for example, electronic expansion valves whose opening degree can be variably controlled, have functions as expansion / decompression valves in the refrigerant circulation circuit A, and expand and depressurize the refrigerant. is there. One of the expansion devices 16a is connected to the intermediate heat exchanger 15a, and the other is connected to the liquid refrigerant supply valve 17a. One of the expansion devices 16b is connected to the intermediate heat exchanger 15b, and the other is connected to the liquid refrigerant supply valve 17a.

Here, the intermediate heat exchangers 15a and 15b can generate heat media having different temperatures under the control of the expansion devices 16a and 16b. For example, when the temperature of the heat medium generated by the intermediate heat exchanger 15b is set higher than the temperature of the heat medium generated by the intermediate heat exchanger 15a, the expansion device 16b on the side of the intermediate heat exchanger 15b Control is performed so as to narrow down the diaphragm device 16a on the exchanger 15a side. Then, the temperature of the refrigerant flowing into the intermediate heat exchanger 15b becomes higher than the temperature of the refrigerant flowing into the intermediate heat exchanger 15a, and the temperature of the heat medium generated by the intermediate heat exchanger 15b is increased. In the same manner, the temperature of the heat medium generated by the intermediate heat exchanger 15b can be made higher than the temperature of the heat medium generated by the intermediate heat exchanger 15a. In this way, it is possible to generate a heat medium having a different temperature even in the same operation state.

The liquid refrigerant supply valve 17a and the gas refrigerant supply valve 17b are constituted by two-way valves or the like, and open and close the refrigerant pipe in the refrigerant circulation circuit A. Among these, one of the liquid refrigerant supply valves 17a is connected to the high-pressure main pipe 5a that allows the refrigerant to flow into the intermediate unit 3, and the other is connected to the expansion devices 16a and 16b. One of the gas refrigerant supply valves 17b is connected to the high-pressure main pipe 5a that allows the refrigerant to flow into the intermediate unit 3, and the other is connected to the second refrigerant flow switching devices 18a and 18b. The liquid refrigerant supply valve 17a and the gas refrigerant supply valve 17b may be selected in accordance with the flow rate of refrigerant flowing through the valves and the application. For example, if the open / close operations of the valves do not match, a four-way valve is used. May be.

The second refrigerant flow switching units 18a and 18b are constituted by four-way valves or the like, and switch the refrigerant flow according to the operation mode. Specifically, when the intermediate heat exchanger 15a functions as a radiator (heat radiation from the refrigerant to the thermal refrigerant), the second refrigerant flow switching unit 18a is a high-temperature and high-pressure refrigerant that has passed through the gas refrigerant supply valve 17b. Is switched to a heating channel that flows into the refrigerant channel of the intermediate heat exchanger 15a. When the intermediate heat exchanger 15a functions as an evaporator (the refrigerant absorbs heat from the thermal refrigerant), the second refrigerant flow switching unit 18a causes the refrigerant flowing out of the refrigerant flow path of the intermediate heat exchanger 15a to go to the low-pressure main pipe 5b. Can be switched to a new cooling channel. When the intermediate heat exchanger 15b functions as a radiator (heat radiation from the refrigerant to the water), the second refrigerant flow switching unit 18b performs intermediate heat exchange with the high-temperature and high-pressure refrigerant that has passed through the liquid refrigerant supply valve 17b. It is switched to a heating flow path that flows into the refrigerant flow path of the vessel 15b. When the intermediate heat exchanger 15b functions as an evaporator (the refrigerant absorbs heat from water), the second refrigerant flow switch 18b is configured such that the refrigerant flowing out of the refrigerant flow path of the intermediate heat exchanger 15b goes to the low-pressure main pipe 5b. It is switched to the cooling channel.

Here, the second refrigerant flow switch 18a and the second refrigerant flow switch 18b have a function of switching to different flow paths. That is, when the intermediate heat exchanger 15a side generates a cooled heat medium and the intermediate heat exchanger 15b side generates a heat medium having a higher temperature than the intermediate heat exchanger 15a side, the second refrigerant flow switching device 18a is cooled. While switching the flow path to become a flow path, the second refrigerant flow switching device 18b switches the flow path to become a heating flow path. By the same method, the temperature of the heat medium generated on the intermediate heat exchanger 15b side can be made higher than the temperature of the heat medium generated on the intermediate heat exchanger 15a side. As described above, by switching the second refrigerant flow switching units 18a and 18b, the two intermediate heat exchangers 15a and 15b can generate heat media having different temperatures.

In the refrigerant circuit A, one of the expansion devices 9 is connected to the liquid refrigerant supply valve 17a and the other is connected to the low-pressure main pipe 5b. The expansion device 9 functions as an expansion / decompression valve, and expands and depressurizes the refrigerant. It is something to be made.

The

pumps

21a and 21b are for pumping and circulating water in the heat medium circulation circuit B. The pump 21 a is provided in a heat medium pipe between the intermediate heat exchanger 15 a and the heat medium flow switching unit 22. The pump 21 b is provided in a heat medium pipe between the intermediate heat exchanger 15 b and the heat medium flow switching unit 22. Moreover, what is necessary is just to comprise the

pumps

21a and 21b so that capacity | capacitance control is possible by an inverter or the number of pumps, for example. The

pumps

21a and 21b are illustrated as being provided on the suction side of the intermediate heat exchangers 15a and 15b, respectively, but may be configured to be provided on the outlet side of the intermediate heat exchangers 15a and 15b.

The heat medium

flow switching units

22 and 23 are configured by three-way valves or the like, and switch the combination of connections between the

use side units

2a and 2b and the intermediate heat exchangers 15a and 15b. The number of the heat medium

flow switching devices

22 and 23 is set according to the number of installed usage-

side units

2a and 2b. Of the three heat medium

flow switching units

22 and 23, one is connected to the pump 21a, the other is connected to the pump 21b, and the other is connected to the flow rate adjusting means 25.

The primary-side water flow path switch 23 is configured by a three-way valve or the like, and switches the water flow path in the heat medium circuit B according to the operation mode. Further, the number of primary side water flow path switching units 23 (two in FIG. 1) corresponding to the number of usage side units 2 installed is provided. The primary side water flow path switch 23 is connected to the intermediate heat exchanger 15a, the other to the intermediate heat exchanger 15b, and the remaining one to the user side heat exchanger 26, respectively. Has been.

The flow rate adjusting means 25a, 25b is configured by a two-way valve or the like that can control the opening area, and one is used for the use side heat exchanger 26 of the use side unit 2 and the other is used for the secondary side flow path switch 22. Each is connected. The flow rate adjusting means 25a and 25b control the flow rate of the heat medium flowing through the use

side heat exchangers

26a and 26b, respectively. The flow rate adjusting means 25a, 25b are installed in the heat medium piping system on the outlet side of the use

side heat exchangers

26a, 26b, but are not limited to this, and the use

side heat exchangers

26a, 26b. It is good also as what is installed in the heat-medium piping system (for example, the exit side of the primary side water flow path switch 23a, 23b) of the inlet side.

The intermediate unit 3 includes heat

medium temperature sensors

31a and 31b, outlet

water temperature sensors

34a and 34b, first

refrigerant temperature sensors

35a and 35b,

pressure sensors

36a and 36b, and second

refrigerant temperature sensors

37a and 37b. Furthermore, the intermediate unit 3 includes an intermediate unit control means 53 that performs a calculation based on each information detected by each sensor.

The temperature detection means 31a, 31b detects the temperature of water flowing out from the intermediate heat exchangers 15a, 15b, that is, water at the outlet side of the water flow path of the intermediate heat exchanger 15, What is necessary is just to comprise. Among these, the temperature detection means 31a is provided in the heat medium piping in the exit side of the water flow path of the intermediate heat exchanger 15a. The temperature detecting means 31b is provided in the heat medium pipe 28 on the outlet side of the water flow path of the intermediate heat exchanger 15b.

The outlet water temperature sensor 34a is provided between the use side heat exchanger 26a and the flow rate adjusting means 25a and detects the temperature of the water flowing out from the use side heat exchanger 26a. What should I do? Further, the number of outlet water temperature sensors 34 (two in FIG. 1) according to the number of installed usage-side units 2 is provided.

The first refrigerant temperature sensor 35 is installed between the intermediate heat exchanger 15 and the second refrigerant flow switching unit 18 and detects the temperature of the refrigerant flowing in and out of the intermediate heat exchanger 15. For example, a thermistor or the like may be used. Among these, the first refrigerant temperature sensor 35a is provided between the intermediate heat exchanger 15a and the second refrigerant flow switching unit 18a. The first refrigerant temperature sensor 35b is provided between the intermediate heat exchanger 15b and the second refrigerant flow switch 18b.

Similar to the installation position of the first refrigerant temperature sensor 35, the pressure sensor 36 is provided between the intermediate heat exchanger 15 and the second refrigerant flow switching units 18a and 18b, and the intermediate heat exchangers 15a and 15b and the refrigerant. The pressure of the refrigerant flowing between the flow path changers 18a and 18b is detected. Among these, the pressure sensor 36a is provided between the intermediate heat exchanger 15a and the refrigerant flow switching device 18a. The pressure sensor 36b is provided between the intermediate heat exchanger 15b and the refrigerant flow switching device 18b.

The second refrigerant temperature sensor 37 is installed between the intermediate heat exchanger 15 and the expansion device 16, and detects the temperature of the refrigerant flowing in and out of the intermediate heat exchanger 15. For example, the thermistor Or the like. Of these, the second refrigerant temperature sensor 37a is provided between the intermediate heat exchanger 15a and the expansion device 16a. The second refrigerant temperature sensor 37b is provided between the intermediate heat exchanger 15b and the expansion device 16b.

Here, in the air conditioner 100, the refrigerant circulation circuit A and the heat medium circulation circuit B are configured, and the refrigerant and the heat medium circulation circuit B that circulates in the refrigerant circulation circuit A in the intermediate heat exchangers 15a and 15b. Heat is exchanged with the circulating water.

That is, the compressor 10, the first refrigerant flow switching device 11, the heat source side heat exchanger 12, the flow path forming unit 13, the accumulator 19, the liquid refrigerant supply valve 17a, the gas refrigerant supply valve 17b, The refrigerant circulation circuit A is connected by connecting the refrigerant flow paths of the second refrigerant flow switching units 18a and 18b, the intermediate heat exchangers 15a and 15b, the expansion devices 16a and 16b, and the expansion device 9 with refrigerant piping. It is composed.

Note that the refrigerant circulating in the refrigerant circuit A is not particularly limited, but the refrigerant that can be used in the refrigeration cycle of the air-conditioning apparatus 100 according to the present embodiment includes a non-azeotropic refrigerant mixture, a pseudo-common refrigerant. There are boiling mixed refrigerant, single refrigerant, natural refrigerant and the like. Among these, the non-azeotropic refrigerant mixture includes R407C (R32 / R125 / R134a) which is an HFC (hydrofluorocarbon) refrigerant. Since this non-azeotropic refrigerant mixture is a mixture of refrigerants having different boiling points, it has a characteristic that the composition ratio of the liquid-phase refrigerant and the gas-phase refrigerant is different. Examples of the pseudo azeotropic refrigerant mixture include R410A (R32 / R125) and R404A (R125 / R143a / R134a) which are HFC refrigerants. This pseudo azeotrope refrigerant has the same characteristic as that of the non-azeotrope refrigerant and has an operating pressure of about 1.6 times that of R22. The single refrigerant includes R22, which is an HCFC (hydrochlorofluorocarbon) refrigerant, R134a, which is an HFC refrigerant, and the like. Since this single refrigerant is not a mixture, it has the property of being easy to handle. Natural refrigerants include carbon dioxide, propane, isobutane and ammonia. Here, R22 is chlorodifluoromethane, R32 is difluoromethane, R125 is pentafluoromethane, R134a is 1,1,1,2-tetrafluoromethane, and R143a is 1,1,1. -Each represents trifluoroethane. Therefore, it is good to use the refrigerant | coolant according to the use and the objective of the air conditioning apparatus 100. FIG.

On the other hand, the water flow paths of the intermediate heat exchangers 15a and 15b, the

pumps

21a and 21b, the secondary water

flow path switchers

22a and 22b, the flow rate adjusting means 25a and 25b, and the use

side heat exchangers

26a and 26b The primary-side water

flow switching devices

23a and 23b are connected to each other by a heat medium pipe to constitute a heat medium circulation circuit B.

For example, water or brine (antifreeze) may be used as the heat medium circulating in the heat medium circuit B. The antifreeze for the antifreeze is not particularly limited, and may be selected according to the use, such as ethylene glycol or propylene glycol. By using such a heat medium, even if the heat medium leaks into the air-conditioning target space via the

use side units

2a and 2b, a highly safe heat medium is used. It can contribute to improvement.

Next, each operation mode performed by the air conditioner 100 of FIG. 1 will be described. The air conditioning apparatus 100 can perform a cooling operation or a heating operation in the

use side units

2a and 2b based on instructions from the

use side units

2a and 2b. That is, the air conditioner 100 can perform the same operation for all the usage-

side units

2a and 2b, and can also perform different operations for each usage-side unit 2.

As an operation mode performed by the air conditioner 100, a cooling only operation mode in which all of the driving use side units 2 perform a cooling operation, and a heating operation in which all of the driving use side units 2 perform a heating operation. There are an operation mode, a cooling main operation mode with a larger cooling load, and a heating main operation mode with a larger heating load. Below, each operation mode is demonstrated with the flow of a refrigerant | coolant and water.

(Cooling mode only)
In the cooling only operation mode, on the refrigerant circuit A side, the refrigerant flow path is switched so that the refrigerant discharged from the compressor 10 by the first refrigerant flow switch 11 flows into the heat source side heat exchanger 12. In the intermediate unit 3, the liquid refrigerant supply valve 17a is opened and closed, and the gas refrigerant supply valve 17b is closed. Further, the second refrigerant flow switching units 18a and 18b are switched to cooling channels such that the refrigerant flowing out from the refrigerant flow channels of the intermediate heat exchangers 15a and 15b goes to the low-pressure main pipe 5b. On the other hand, on the heat medium circuit B side, in the intermediate unit 3, the

pumps

21a and 21b are driven, the flow rate adjusting means 25a and 25b are opened, and the intermediate heat exchangers 15a and 15b and the use-

side heat exchangers

26a and 26b. The heat medium circulates between the two.

First, the flow of the refrigerant in the refrigerant circuit A will be described with reference to FIG. The low-temperature and low-pressure gas refrigerant is compressed by the compressor 10 and discharged as a high-temperature and high-pressure refrigerant. The high-temperature and high-pressure refrigerant discharged from the compressor 10 flows into the heat source side heat exchanger 12 that functions as a condenser via the first refrigerant flow switching device 11. The high-temperature and high-pressure gas refrigerant is condensed by heat exchange with the outside air while passing through the heat source side heat exchanger 12, and flows out as a high-pressure liquid refrigerant. Thereafter, the high-temperature and high-pressure refrigerant becomes high-pressure refrigerant while radiating heat to the outdoor air, and flows out of the heat source unit 1 through the check valve 13a. Thereafter, the high-pressure refrigerant flows into the intermediate unit 3 via the high-pressure main pipe 5a.

The high-pressure refrigerant flowing into the intermediate unit 3 branches after passing through the liquid refrigerant supply valve 17a, and flows into the expansion devices 16a and 16b, respectively. In the expansion devices 16a and 16b, the high-pressure hot refrigerant is expanded and depressurized to become a low-temperature and low-pressure gas-liquid two-phase refrigerant. This gas-liquid two-phase refrigerant flows into each of the intermediate heat exchangers 15a and 15b acting as an evaporator, and evaporates while cooling the heat medium by absorbing heat from the heat medium circulating in the heat medium circuit B. It becomes a low-temperature and low-pressure gas refrigerant. The gas refrigerant that has flowed out of the intermediate heat exchangers 15a and 15b merges via the second refrigerant flow switching devices 18a and 18b, respectively, and flows out of the intermediate unit 3. Thereafter, the gas refrigerant flows into the heat source unit 1 again via the low-pressure main pipe 5b. The gas refrigerant that has flowed into the heat source unit 1 passes through the check valve 13d, passes through the first refrigerant flow switch 11 and the accumulator 19, and is sucked into the compressor 10 again.

Next, the flow of the heat medium in the heat medium circuit B will be described with reference to FIG. In the cooling only operation mode, the cold heat of the refrigerant is transmitted to the heat medium in the intermediate heat exchangers 15a and 15b, and the cooled water flows through the heat medium circuit B by the

pumps

21a and 21b. The heat medium pressurized and discharged by the

pumps

21a and 21b flows into the intermediate heat exchangers 15a and 15b, respectively, and is cooled by the refrigerant circulating in the refrigerant circuit A. The heat medium flowing out from the intermediate heat exchanger 15a branches in the middle, flows out from the intermediate unit 3 via the primary side water

flow switching devices

23a and 23b, and flows into the

use side units

2a and 2b, respectively. Similarly, the heat medium flowing out from the intermediate heat exchanger 15b also branches in the middle and flows out from the intermediate unit 3 via the primary side water

flow switching devices

23a and 23b, respectively, to the

use side units

2a and 2b, respectively. Inflow.

The heat medium that has flowed into the

use side units

2a and 2b flows into the use

side heat exchangers

26a and 26b, respectively, and absorbs heat from the air in the air conditioning target space, whereby the air conditioning target space is cooled. And the heat medium which flowed out from use

side heat exchanger

26a, 26b flows out from

use side unit

2a, 2b, respectively, and flows in into intermediate unit 3 via heat medium piping.

The heat medium flowing into the intermediate unit 3 flows into the flow

rate adjusting valves

25a and 25b, respectively. At this time, the flow rate of the heat medium is controlled to a flow rate required to cover the air conditioning load required in the room by the action of the flow

rate adjusting valves

25a and 25b, and flows into the use

side heat exchangers

26a and 26b. The heat medium flowing out from the flow rate adjusting valve 25a branches at the secondary side flow path switching unit 22a and is sucked into the

pumps

21a and 21b, respectively. The water that flows out from the flow rate adjustment valve 25b branches through the flow rate adjustment valve 25b, branches at the secondary side flow path switching unit 22b, and is sucked into the

pumps

21a and 21b, respectively.

(All heating operation mode)
In the heating only operation mode, on the refrigerant circulation circuit A side, the refrigerant flow path is switched so that the refrigerant discharged from the compressor 10 by the first refrigerant flow switching device 11 flows into the intermediate unit 3. The liquid refrigerant supply valve 17a is closed and the gas refrigerant supply valve 17b is opened and closed. Further, the second refrigerant flow switching device 18b is switched to a heating flow channel in which the high-temperature and high-pressure refrigerant that has passed through the gas refrigerant supply valve 17b flows into the refrigerant flow channel of the intermediate heat exchanger 15b. On the other hand, on the heat medium circuit B side, in the intermediate unit 3, the

pumps

side heat exchangers

26a and 26b. The heat medium circulates between the two.

First, the flow of the refrigerant in the refrigerant circuit A will be described. The low-temperature and low-pressure gas refrigerant is compressed by the compressor 10 and discharged as a high-temperature and high-pressure refrigerant. The high-temperature and high-pressure refrigerant discharged from the compressor 10 flows out of the heat source unit 1 through the check valve 13b in the first connection pipe 4a via the first refrigerant flow switching device 11, and passes through the high-pressure main pipe 5a. And flows into the intermediate unit 3.

The high-temperature and high-pressure refrigerant that has flowed into the intermediate unit 3 branches after passing through the gas refrigerant supply valve 17b, and passes through the second refrigerant flow switching units 18a and 18b, respectively, and the intermediate heat exchanger 15a acting as a radiator. , 15b. The high-temperature and high-pressure refrigerant flowing into the intermediate heat exchangers 15a and 15b becomes high-pressure refrigerant while heating water by dissipating heat to the refrigerant circulating in the heat medium circuit B. The high-pressure refrigerant flows out of the intermediate heat exchangers 15a and 15b, flows into the expansion devices 16a and 16b, and is expanded and depressurized to become a low-temperature and low-pressure gas-liquid two-phase refrigerant. This gas-liquid two-phase refrigerant is merged, further expanded and depressurized by the expansion device 9, flows out from the intermediate unit 3, and flows into the heat source unit 1 again through the low-pressure main pipe 5b.

The gas-liquid two-phase refrigerant that has flowed into the heat source unit 1 flows into the heat source side heat exchanger 12 through the check valve 13c in the second connection pipe 4b, and is vaporized while absorbing heat from the outdoor air. It becomes a refrigerant and is sucked into the compressor 10 again via the first refrigerant flow switching device 11 and the accumulator 19.

Next, the flow of the heat medium in the heat medium circuit B will be described with reference to FIG. In the heating only operation mode, the heat of the refrigerant is transmitted to water in both of the intermediate heat exchangers 15a and 15b, and the heated heat medium flows through the heat medium circuit B by the

pumps

21a and 21b. The heat medium pressurized and discharged by the

pumps

21a and 21b flows into the intermediate heat exchangers 15a and 15b, respectively, and is heated by the refrigerant circulating in the refrigerant circuit A. The heat medium flowing out from the intermediate heat exchanger 15a branches in the middle, flows out from the intermediate unit 3 via the primary side water

flow switching devices

23a and 23b, and flows into the

use side units

flow switching devices

23a and 23b, respectively, to the

use side units

2a and 2b, respectively. Inflow.

The heat medium that has flowed into the use-

side units

2a and 2b flows into the use-

side heat exchangers

26a and 26b, respectively, and dissipates heat to the air in the air-conditioning target space, thereby heating the air-conditioning target space. And the heat medium which flowed out from use

side heat exchanger

26a, 26b flows out from

use side unit

The heat medium flowing into the intermediate unit 3 flows into the flow

rate adjusting valves

25a and 25b, and flows into the use

side heat exchangers

26a and 26b. ing. The heat medium flowing out from the flow rate adjustment valve 25a branches through the flow rate adjustment valve 25a, branches at the secondary water flow path switch 22a, and is sucked into the

pumps

21a and 21b, respectively. The heat medium flowing out from the flow rate adjustment valve 25b branches through the flow rate adjustment valve 25b, branches at the secondary water flow path switch 22b, and is sucked into the

pumps

21a and 21b, respectively.

(Cooling operation mode)
In the air-conditioning apparatus 100 shown in FIG. 1, the cooling main operation mode will be described by taking as an example a case where a cooling load is generated in the use side heat exchanger 26a and a heating load is generated in the use side heat exchanger 26b. . In the cooling main operation mode, the refrigerant flow path is switched so that the refrigerant discharged from the compressor 10 by the first refrigerant flow switch 11 flows into the heat source side heat exchanger 12. Further, the opening / closing control is performed so that the expansion device 16a is fully opened, the liquid refrigerant supply valve 17a is opened, and the gas refrigerant supply valve 17b is opened. In the intermediate unit 3, the

pumps

21a and 21b are driven, the flow rate adjusting means 25a and 25b are opened, and the heat medium is circulated between the intermediate heat exchangers 15a and 15b and the use

side heat exchangers

26a and 26b. Like to do.

First, the flow of the refrigerant in the refrigerant circuit A will be described with reference to FIG.
The low-temperature and low-pressure gas refrigerant is compressed by the compressor 10 and discharged as a high-temperature and high-pressure refrigerant. The high-temperature and high-pressure refrigerant discharged from the compressor 10 flows into the heat source side heat exchanger 12 via the first refrigerant flow switching unit 11 and dissipates heat to the outdoor air, while the temperature of the high-pressure refrigerant decreases. It flows out from the heat source unit 1 through the check valve 13a, and flows into the intermediate unit 3 through the high-pressure main pipe 5a.

The high-pressure refrigerant that has flowed into the intermediate unit 3 flows into the intermediate heat exchanger 15b that acts as a radiator via the gas refrigerant supply valve 17b and the second refrigerant flow switch 18b. The high-pressure refrigerant radiates heat to the heat medium circulating in the heat medium circuit B through the intermediate heat exchanger 15b. As a result, the high-pressure refrigerant heats the heat medium and becomes a high-pressure refrigerant whose temperature is further lowered. The high-pressure refrigerant flowing out of the intermediate heat exchanger 15b is expanded and depressurized by the expansion device 16b to become a low-temperature and low-pressure gas-liquid two-phase refrigerant, and passes through the expansion device 16a to the intermediate heat exchanger 15a acting as an evaporator. By flowing in and absorbing heat from the heat medium circulating in the heat medium circuit B, the heat medium evaporates while cooling, and becomes a low-temperature and low-pressure gas refrigerant. The gas refrigerant that has flowed out of the intermediate heat exchanger 15a flows out of the intermediate unit 3 via the second refrigerant flow switching device 18a, and flows into the heat source unit 1 again via the low-pressure main pipe 5b. The gas refrigerant flowing into the heat source unit 1 passes through the check valve 13d, passes through the first refrigerant flow switching device 11 and the accumulator 19, and is sucked into the compressor 10 again.

Next, the flow of the heat medium in the heat medium circuit B will be described with reference to FIG. In the cooling main operation mode, the cold heat of the refrigerant is transmitted to the heat medium in the intermediate heat exchanger 15a, and the cooled heat medium flows through the heat medium circuit B by the pump 21a. In the cooling main operation mode, the warm heat of the refrigerant is transmitted to the heat medium in the intermediate heat exchanger 15b, and the warmed heat medium is circulated in the heat medium circuit B by the pump 21b.

The heat medium pressurized and discharged by the pump 21a flows into the intermediate heat exchanger 15a and becomes a heat medium cooled by the refrigerant circulating in the refrigerant circuit A. The heat medium pressurized and discharged by the pump 21b flows into the intermediate heat exchanger 15b and becomes a heat medium heated by the refrigerant circulating in the refrigerant circuit A. The heat medium flowing out from the intermediate heat exchanger 15a flows out from the intermediate unit 3 via the primary side water flow path switch 23a and flows into the use side unit 2a. The heat medium flowing out from the intermediate heat exchanger 15b flows out from the intermediate unit 3 via the primary side water flow path switch 23b and flows into the use side unit 2b.

The cooled heat medium flowing into the use side unit 2a flows into the use side heat exchanger 26a, and the warmed heat medium flowing into the use side unit 2b flows into the use side heat exchanger 26b. The heat medium flowing into the use-side heat exchanger 26a absorbs heat from the air in the air-conditioning target space, thereby cooling the air-conditioning target space. On the other hand, the heat medium flowing into the use side heat exchanger 26b dissipates heat to the air in the air-conditioning target space, thereby heating the air-conditioning target space. Then, the heat medium that has flowed out of the use-side heat exchanger 26a and whose temperature has risen flows out of the use-side unit 2a, and flows into the intermediate unit 3 through the

heat medium pipes

27 and 28. On the other hand, the heat medium having flowed out of the use side heat exchanger 26b and having a lowered temperature flows out of the use side unit 2b and flows into the intermediate unit 3 through the

heat medium pipes

27 and 28.

The heat medium flowing into the intermediate unit 3 from the use side heat exchanger 26a flows into the flow rate adjusting means 25a, and the heat medium flowing into the intermediate unit 3 from the use side heat exchanger 26b flows into the flow rate adjusting means 25b. At this time, the flow rate of the heat medium is controlled to a flow rate required to cover the air conditioning load required in the room by the action of the flow

rate adjusting valves

25a and 25b, and flows into the use

side heat exchangers

26a and 26b. ing. The heat medium flowing out from the flow rate adjustment valve 25a is sucked into the pump 21a again via the secondary side water flow path switch 22a. On the other hand, the heat medium flowing out from the flow rate adjusting means 25b is again sucked into the pump 21b via the secondary water flow path switch 22b. As described above, in the cooling main operation mode, the heat medium having different temperatures is not mixed by the action of the primary side water flow path switching unit 23 and the secondary side water flow path switching unit 22, respectively, and the cooling load, It flows into the use side heat exchanger 26 with a thermal load.

(Heating main operation mode)
In the air conditioner 100 shown in FIG. 1, the heating main operation mode will be described by taking as an example a case where a heat load is generated in the use side heat exchanger 26a and a heat load is generated in the use side heat exchanger 26b. . In the heating main operation mode, in the heat source unit 1, the refrigerant discharged from the compressor 10 by the first refrigerant flow switching unit 11 flows into the intermediate unit 3 without passing through the heat source side heat exchanger 12. The refrigerant flow path is switched so that The expansion device 16a is controlled to be fully opened, the liquid refrigerant supply valve 17a is closed, and the gas refrigerant supply valve 17b is opened. Then, in the intermediate unit 3, the

pumps

21a and 21b are driven, the flow

rate adjusting valves

25a and 25b are opened, and a heat medium is provided between the intermediate heat exchangers 15a and 15b and the use

side heat exchangers

26a and 26b, respectively. I try to circulate.

First, the flow of the refrigerant in the refrigerant circuit A will be described with reference to FIG. The low-temperature and low-pressure gas refrigerant is compressed by the compressor 10 and discharged as a high-temperature and high-pressure refrigerant. The high-temperature and high-pressure refrigerant discharged from the compressor 10 flows out of the heat source unit 1 through the check valve 13b in the first connection pipe 4a via the first refrigerant flow switching device 11, and passes through the high-pressure main pipe 5a. And flows into the intermediate unit 3.

The high-temperature and high-pressure refrigerant that has flowed into the intermediate unit 3 flows into the intermediate heat exchanger 15b that acts as a radiator via the gas refrigerant supply valve 17b and the second refrigerant flow switching unit 18b. By radiating heat to the circulating heat medium, the heat medium is heated and becomes a high-pressure refrigerant. The high-pressure refrigerant flowing out from the intermediate heat exchanger 15b is expanded and depressurized by the expansion device 16b, and becomes a low-temperature and low-pressure gas-liquid two-phase refrigerant. The low-temperature and low-pressure gas-liquid two-phase refrigerant flows into the intermediate heat exchanger 15a acting as an evaporator via the expansion device 16a, and cools the heat medium by absorbing heat from the heat medium circulating in the heat medium circuit B. However, it becomes a refrigerant whose temperature has risen. The refrigerant that has flowed out of the intermediate heat exchanger 15a flows out of the intermediate unit 3 through the second refrigerant flow switching device 18a, and flows into the heat source unit 1 again through the low-pressure main pipe 5b.

The refrigerant flowing into the heat source unit 1 passes through the check valve 13c in the second connection pipe 4b, flows into the heat source side heat exchanger 12, vaporizes while absorbing heat from the outdoor air, and becomes a low-temperature and low-pressure gas refrigerant. The refrigerant is sucked again into the compressor 10 via the first refrigerant flow switching device 11 and the accumulator 19.

Next, the flow of the heat medium in the heat medium circuit B will be described with reference to FIG. In the heating main operation mode, the cold heat of the refrigerant is transmitted to the heat medium in the intermediate heat exchanger 15a, and the cooled heat medium flows through the heat medium circuit B by the pump 21a. In the heating main operation mode, the heat of the refrigerant is transmitted to the heat medium in the intermediate heat exchanger 15a, and the heated heat medium is circulated in the heat medium circuit B by the pump 21b.

The heat medium pressurized and discharged by the pump 21a flows into the intermediate heat exchanger 15a and becomes a heat medium cooled by the refrigerant circulating in the refrigerant circuit A. The heat medium pressurized and discharged by the pump 21b flows into the intermediate heat exchanger 15b and becomes a heat medium heated by the refrigerant circulating in the refrigerant circuit A. The heat medium flowing out from the intermediate heat exchanger 15a flows out from the intermediate unit 3 via the primary side water flow path switch 23b and flows into the use side unit 2b. The heat medium flowing out from the intermediate heat exchanger 15b flows out from the intermediate unit 3 via the primary side water flow path switch 23a and flows into the use side unit 2a.

The heat medium flowing into the use side unit 2a flows into the use side heat exchanger 26a, and the heat medium flowing into the use side unit 2b flows into the use side heat exchanger 26b. The heat medium flowing into the use side heat exchanger 26a dissipates heat to the air in the air conditioning target space, thereby heating the air conditioning target space. On the other hand, the heat medium flowing into the use-side heat exchanger 26b absorbs heat from the air in the air-conditioning target space, thereby cooling the air-conditioning target space. Then, the heat medium having flowed out of the use side heat exchanger 26a and having a lowered temperature flows out of the use side unit 2a and flows into the intermediate unit 3 via the

heat medium pipes

27 and 28. On the other hand, the heat medium that has flowed out of the use side heat exchanger 26b and whose temperature has risen flows out of the use side unit 2b and flows into the intermediate unit 3 through the

heat medium pipes

27 and 28.

The heat medium flowing into the intermediate unit 3 from the use side heat exchanger 26a flows into the flow rate adjusting means 25a, and the heat medium flowing into the intermediate unit 3 from the use side heat exchanger 26b flows into the flow rate adjusting means 25b. At this time, the flow rate of the heat medium is controlled to a flow rate necessary to cover the air conditioning load required in the room by the action of the flow rate adjusting means 25a, 25b, and flows into the use

side heat exchangers

26a, 26b. ing. The heat medium flowing out from the flow rate adjusting means 25a is sucked into the pump 21b again via the secondary side water flow path switch 22a. On the other hand, the heat medium flowing out from the flow rate adjusting means 25b is sucked into the pump 21a again via the secondary side water flow path switch 22b. As described above, in the heating main operation mode, the heat mediums having different temperatures are respectively mixed with the cooling load without being mixed by the action of the primary side water flow path switching unit 23 and the secondary side water flow path switching unit 22, and It flows into the use side heat exchanger 26 with a thermal load.

In addition, in the above four operation modes, although the

use side units

2a and 2b showed the case where both performed the air_conditioning | cooling operation | movement or heating operation, use of either of the some

use side units

2a and 2b is shown. When the

side units

2a and 2b are in the operation stop state, the flow rate adjusting means 25 is closed and the air conditioning operation is not performed.

(Configuration of control means)
The air conditioner 100 of FIG. 1 includes a heat source unit control means 51, usage-side unit control means 52a and 52b, and an intermediate unit control means 53. The heat source unit 1 is provided with a heat source unit control means 51, each use side unit 2 is provided with use side unit control means 52 a and 52 b, and the intermediate unit 3 is provided with an intermediate unit control means 53. The control means 51 to 53 can communicate with each other by communication means (wired or wireless) (not shown), and control each unit while communicating information with the communication means.

Each control means 51 to 53 is configured by a microcomputer or a DSP (Digital Signal Processor) or the like, and the whole operation of the air conditioner 100 is controlled by each control means 51 to 53. Each of the control means 51 to 53 may perform self-sustained dispersion emphasis control that performs independent control corresponding to each unit (the heat source unit 1, the

use side units

2a and 2b, and the intermediate unit 3). Alternatively, any one of the units may be provided with a control unit, and the control unit may collectively control the actuators of the units.

Each of the control means 51 to 53 described above has a function of performing condensation suppression control. Here, the dew condensation suppression control refers to whether or not dew condensation occurs in each of the

use side units

2a and 2b, and when it is determined that dew condensation occurs or there is a risk of dew condensation, It is control which produces | generates a different thermal refrigerant and flows into the utilization

side heat exchanger

26a, 26b of applicable

utilization side unit

2a, 2b. Here, the thermal refrigerants having different temperatures for suppressing condensation are generated by one or more of the adjustment intermediate heat exchangers 15b among the plurality of intermediate heat exchangers 15a and 15b. Note that which intermediate heat exchanger is assigned to the adjusting intermediate heat exchanger is set in advance in each of the control means 51 to 53.

The heat source unit control means 51 controls the refrigerant flow path, pressure state, and temperature state in the heat source unit 1. Specifically, the heat source unit control means 51 performs a calculation process on the basis of pressure information and temperature information detected by a pressure sensor and a temperature sensor (not shown respectively), and then controls the frequency of the compressor 10. Control of the fan rotation speed of the blower 12a, flow path switching control of the first refrigerant flow path switch 11, and the like are performed.

FIG. 2 is a block diagram showing an example of the usage-side unit control means 52a and 52b. The use side unit control means 52a and 52b are illustrated as having the same configuration. The use side unit control means 52a and 52b mainly perform dew condensation suppression control, operation control, and thermo control. The usage-side unit control means 52a, 52b includes a target model determination means 520, a target determination means 521, and a dew point temperature calculation means 522 for performing dew condensation suppression control.

The target model discriminating means 520 stores the model information of the

use side units

2a and 2b themselves. The target determination unit 521 determines whether or not the unit is a usage-side unit that is subject to condensation suppression control based on the model information, temperature information, and humidity information. Specifically, the target determination unit 521 determines whether or not to perform dew condensation suppression control from the model information of the usage-

side units

2a and 2b. For example, when the use

side heat exchangers

26a and 26b are heat exchangers using natural convection such as a chilled beam, the target determination unit 521 is a model in which the

use side units

2a and 2b are targets of dew condensation suppression control. Is determined.

Further, the target determination unit 521 receives the suction temperature information detected by the suction temperature sensor 32 and the suction humidity information detected by the suction humidity sensor 33. For example, the target determination unit 521 has a preset threshold value, and determines that the model is a target of condensation suppression control when the suction temperature information is smaller than the set temperature threshold value. Similarly, when the suction humidity information is larger than the set threshold value, the target determination unit 521 determines that the model is a target of dew condensation suppression control.

The dew point temperature calculation means 522 calculates the dew point temperature based on the suction temperature information detected by the suction temperature sensor 32 and the suction humidity information detected by the suction humidity sensor 33. A known method can be used for calculating the dew point temperature. For example, the water vapor pressure (= saturated water vapor pressure) is obtained from the relative humidity (absolute humidity) detected by the sensor, and the dew point temperature is calculated from the water vapor pressure.

The dew point temperature calculation means 522 outputs dew point temperature information to the intermediate unit control means 53 when the object determination means 521 determines that the object is the object of the condensation control control. The target determination unit 521 determines whether or not the target device is based on the temperature information and the humidity information. However, the dew point suppression control is performed based on the dew point temperature calculated by the dew point temperature calculation unit 522. You may make it discriminate | determine whether it performs.

Furthermore, the usage-side unit control means 52a, 52b includes a comparison calculation means 523, a thermo determination means 524, and an operation signal transmission means 525 in order to perform operation control and thermo control. The operation signal transmission means 525 outputs an operation signal for requesting cold water supply or hot water supply to the intermediate unit control means 53 based on the operation request information transmitted from the control panel 526 (or remote controller) by wired or wireless communication means. To do. The comparison calculation means 523 transmits temperature difference information to the thermo determination means 524 from the suction temperature information detected by the suction temperature sensor 32 and the set temperature information transmitted from the control panel 526. The thermo determination means 524 determines whether to continue the operation (thermo ON) or to interrupt the operation (thermo OFF), and transmits the thermo determination information to the intermediate unit control means 53.

FIG. 3 is a block diagram showing an example of the intermediate unit control means 53. The intermediate unit control means 53 of FIG. 3 includes a maximum dew point temperature detection means 53a, a heat medium circuit control means 53b, and a refrigerant circuit control means 53c. The maximum dew point temperature detecting means 53a detects the maximum dew point temperature Tmax which is the highest temperature from the dew point temperature information of the

usage side units

2a and 2b acquired from the plurality of usage side unit control means 52a and 52b. . Further, the maximum dew point temperature detecting means 53a has a function of determining whether or not the dew point temperature information corresponding to the plurality of

usage side units

2a and 2b has been acquired. When the dew point temperature information cannot be acquired from any of the

usage side units

2a and 2b, the maximum dew point temperature detecting means 53a ends the process of receiving the dew point temperature information. On the other hand, the maximum dew point temperature detection means 53a calculates the maximum dew point temperature information having the largest dew point temperature from the dew point temperature information when the dew point temperature information is acquired from any of the

use side units

2a and 2b.

The heat medium circuit control means 53 b controls the heat medium circuit B side in the refrigerant-intermediate unit 3. The heat medium circuit control means 53b controls the flow rate based on the heat medium temperature T detected by the temperature detection means 31a and 31b and the outlet water temperature information detected by the outlet water temperature sensor 34 in the various operation modes described above. In the dew condensation suppression control, the heat medium circuit control unit 53b connects the heat medium flow paths of all the use side heat exchangers 26b that have received the dew point temperature information to the adjustment intermediate heat exchanger 15b so as to connect the primary side switch 23b. And the secondary side switch 22b is controlled.

The refrigerant circuit control means 53c controls the refrigerant circuit A side in the refrigerant-intermediate unit 3. The refrigerant circuit control means 53c receives the refrigerant pressure information detected by the

pressure sensors

36a and 36b and the refrigerant temperature information detected by the first refrigerant temperature sensor 35 and the second

refrigerant temperature sensors

37a and 37b. The refrigerant circuit control means 53c outputs a throttle device opening command, a refrigerant flow path switching command, a gas refrigerant supply valve command, and a liquid refrigerant supply valve command to each actuator based on the received refrigerant pressure information and refrigerant temperature information. It is.

In the dew condensation suppression control, the refrigerant circuit control unit 53c performs intermediate heat exchange based on the maximum dew point temperature Tmax detected by the maximum dew point temperature detection unit 53a and the heat medium temperature T detected by the temperature detection unit 31b. It has a function of controlling the expansion device 26b and the second refrigerant flow switching unit 18b connected to the container 15b.

Specifically, the refrigerant circuit control means 53c acquires the maximum dew point temperature Tmax detected by the maximum dew point temperature detection means 53a. As described above, the use-side heat exchanger 26b that has output the dew point temperature information is already connected to the adjustment intermediate heat exchanger 15b under the control of the heat medium circuit control means 53b. Therefore, the refrigerant circuit control means 53c acquires the heat medium temperature T flowing in the adjustment intermediate heat exchanger 15b from the temperature detection means 31b.

The target temperature setting means 53x of the refrigerant circuit control means 53c calculates the target water temperature Tt of the heat medium temperature T flowing into the use side heat exchanger 26b by the following formula (1) using the maximum dew point temperature Tmax.
Target water temperature Tt = Maximum dew point temperature Tmax + α (1) (α: predetermined temperature)
Note that α is a parameter for determining flow path switching at a temperature higher than the maximum dew point temperature Tmax so that condensation does not occur reliably. Then, the refrigerant circuit control unit 53c sets the target set temperature range Tr to the maximum dew point temperature Tmax ≦ the heat medium temperature T ≦ the target water temperature Tt + β (β: predetermined temperature) with reference to the maximum dew point temperature Tmax.

Here, when the maximum dew point temperature Tmax ≦ the heat medium temperature T ≦ the target water temperature Tt + β (β: a predetermined temperature) is satisfied, the refrigerant circuit control means 53c determines whether or not the expansion device 16b is based on the difference between the heat medium temperature T and the target water temperature Tt. Control the amount of aperture. Β is a parameter for preventing frequent switching operations in the flow path switching unit and preventing problems such as switching failure and unstable refrigerant temperature due to insufficient differential pressure. It is. By controlling the throttle amount, the refrigerant circuit control means 53c performs control so that the heat medium temperature T falls within the target set temperature range Tr.

As a result, in the use side heat exchanger 26b where the maximum dew point temperature Tmax ≦ the heat medium temperature T and no condensation has occurred yet, but there is a possibility that condensation will occur, the occurrence of condensation is maintained while maintaining the operation mode. Can be suppressed. As described above, when it is determined that the dew condensation suppression control is unnecessary on the use side unit control means 52b side, the control of the throttle amount by the dew condensation occurrence control is ended.

When the heat medium temperature T is less than the maximum dew point temperature Tmax (heat medium temperature T <maximum dew point temperature Tmax), the refrigerant circuit control unit 53c uses the refrigerant circuit A of the adjustment intermediate heat exchanger 15b as a heating flow path. Thus, the second refrigerant flow switching device 18b is controlled. Then, the heat medium temperature T of the heat medium exchanged with the refrigerant flowing in the heating flow path rises. Control is performed so that the heat medium temperature T falls within the target set temperature range Tr. In other words, when it is determined that the heat medium temperature T <the maximum dew point temperature max and the occurrence of condensation occurs, the intermediate heat exchanger for adjustment is used to quickly eliminate the condensation that has occurred in the heat exchanger. 15b switches to a heating flow path and removes condensation on the use side heat exchanger 26b. When the heat medium temperature T rises and enters the target set temperature range Tr, the above operation may be continued until the heat medium temperature to be described later <target water temperature + β, or switched to the cooling channel again. Thus, the control may be switched to the control based on the aperture amount.

When the heat medium temperature> the target water temperature + β, the refrigerant circuit control means 53c determines whether or not the adjustment intermediate heat exchanger 15b is connected to the heating flow path. When the adjustment intermediate heat exchanger 15b is connected to the heating flow path, the refrigerant circuit control means 53c sets the second refrigerant flow switching device 18b so that the intermediate heat exchanger 15b is connected to the cooling flow path. Control. Then, the refrigerant circuit control means 53c performs control so that the heat medium temperature T falls within the target set temperature range Tr. Then, when it is determined that the dew condensation suppression control is unnecessary on the use side unit control means 52b side, the control of the throttle amount by the dew condensation occurrence control is ended.

In addition, although the case where the refrigerant circuit control means 53c performs dew condensation suppression control on the refrigerant circulation circuit A side is illustrated, the heat medium circuit control means 53b performs heat condensation on the heat medium circulation circuit B side in accordance with the dew condensation suppression control. The flow rate may be adjusted. For example, when the inflow heat refrigerant temperature T is greatly deviated from the target set temperature range Tr, the heat medium circuit control means 53b causes the flow rate adjustment means 25a to increase the flow rate of the heat refrigerant flowing from the adjustment intermediate heat exchanger 15b. 25b may be controlled. Alternatively, when the inflowing heat refrigerant temperature T is slightly deviated from the target set temperature range Tr, the heat medium circuit control unit 53b is configured to adjust the flow rate so that the flow rate of the heat refrigerant flowing from the adjustment intermediate heat exchanger 15b becomes small. 25a and 25b may be controlled. As a result, it is possible to increase the speed and optimize the condensation suppression control in which the inflow heat refrigerant temperature T is set to the target set temperature range Tr.

Further, although the case where the target set temperature range Tr is set to the maximum dew point temperature Tmax ≦ the heat medium temperature T ≦ the target water temperature Tt + β is illustrated, the maximum dew point temperature Tmax is used as it is, and the maximum dew point temperature Tmax ≦ the heat medium temperature. You may set to T <= Tmax + (beta). In this case, it is determined whether or not the heat medium temperature> the target water temperature + β and the heat medium temperature T> the maximum dew point temperature Tmax + β.

(Condensation suppression control method of the air conditioner 100)
4 is a flowchart showing an operation example of the usage-side unit control means 52 in the dew condensation suppression control of the air conditioning apparatus 100. FIG. 5 is a flowchart showing an operation example of the intermediate unit control means 53 in the dew condensation suppression control of the air conditioning apparatus 100. A description will be given of an example of the dew condensation suppression control method with reference to FIGS. First, the control operation of the usage-side unit control means 52 in the dew condensation suppression control will be described with reference to FIG.

The usage-side unit control means 52 receives the target indoor unit discrimination information from the target model discrimination means 520, and receives the suction temperature information detected by the suction temperature sensor 32 and the suction humidity information detected by the suction humidity sensor 33. (Step S1). Based on the target indoor unit determination information, the target determination unit 521 is not in a state where the flow rate adjustment unit 25 is not operating due to the closed state and is not a use side unit 2 that is not suitable for dew condensation suppression control. It is determined whether or not it is a control target for the dew condensation suppression control (step S2). As a result of the determination, when the use side unit 2 is a control target, the use side unit control means 52 calculates the dew point temperature (step S3) and transmits it to the intermediate unit control means 53 (step S4). On the other hand, if it is not a control target, the usage-side unit control means 52 ends the condensation suppression control process. In the following, a case where dew point temperature information is output from the usage-side unit control means 52b and not output from the usage-side unit control means 52a will be exemplified.

Next, the control operation of the intermediate unit control means 53 in the dew condensation suppression control will be described with reference to FIG. The intermediate unit control means 53 receives the dew point temperature information from the use side unit control means 52b by the processing shown in the following steps S21 to S24 (step S11). Specifically, the intermediate unit control means 53 receives dew point temperature information from the intermediate unit control means 52b (step S21). The intermediate unit control means 53 determines whether or not the dew point temperature information corresponding to the usage side unit 2 has been received from the usage side unit control means 52 (step S22).

As a result of the determination, if the dew point temperature information corresponding to one of the

usage side units

2a, 2b cannot be received, the intermediate unit control means 53 ends the dew point temperature information reception process (step S23). On the other hand, when the dew point temperature information corresponding to any of the usage-side units 2b is received, the intermediate unit control means 53 connects the usage-side heat exchanger 26b of the usage-side unit 2b to the adjustment intermediate heat exchanger 15b ( Step S23).

Thereafter, the intermediate unit control means 53 counts the number of usage-side units 2b that have received the dew point temperature information (step S12). As a result, if the count is one or more, the intermediate unit control means 53 calculates the maximum dew point temperature Tmax having the largest dew point temperature from the received dew point temperature information (step S13). In the present embodiment, the dew point temperature on the use side unit 2b side is the maximum dew point temperature Tmax. Thereafter, the intermediate unit control means 53 calculates the target water temperature Tt of the heat medium temperature T flowing into the use side unit 2b corresponding to the maximum dew point temperature Tmax by the above formula (1) (step S14). And the intermediate unit control means 53 performs various switching of a refrigerant circuit with the heat-medium temperature T (step S15).

Specifically, when it is determined that the temperature is lower than the maximum dew point temperature Tmax (heat medium temperature <maximum dew point temperature + β), the adjustment intermediate heat exchanger 15b is switched from the cooling channel to the heating channel on the warm water side (step S16). ). Then, the heat medium whose temperature has increased by the intermediate heat exchanger 15a flows into the use-side heat exchanger 26a, and the occurrence of condensation can be suppressed.

When it is determined that the maximum dew point temperature Tmax ≦ the heat medium temperature T ≦ the target water temperature + β (β: a predetermined temperature), the refrigerant circuit control unit 53c determines whether or not the expansion device 16b uses the difference between the heat medium temperature T and the target water temperature Tt. The aperture amount is controlled (step S17). Thereby, in the use side heat exchanger 26b in which condensation has not yet occurred but condensation may occur, it is possible to suppress the occurrence of condensation while maintaining the operation mode.

When the heat medium temperature> the target water temperature + β is satisfied, and the heat medium temperature T <the target water temperature Tt + β, the refrigerant circuit control unit 53c determines whether or not the adjustment intermediate heat exchanger 15b is connected to the heating flow path. Judgment is made (step S18). When the adjustment intermediate heat exchanger 15b is connected to the heating flow path, the refrigerant circuit control means 53c sets the second refrigerant flow switching device 18b so that the intermediate heat exchanger 15b is connected to the cooling flow path. Control (step S19).

The control operation of the intermediate unit control means 53 in the dew condensation suppression control as described above is performed on a regular basis, but the execution time interval may be determined optimally according to the system. Further, the predetermined temperature α necessary for calculating the target water temperature and the predetermined temperature β used in the comparison calculation of the heat medium temperature T may be determined optimally according to the system.

According to the above embodiment, when condensation occurs or is likely to occur in the use

side heat exchangers

26a and 26b, the temperature of the refrigerant flowing in the adjustment intermediate heat exchanger 15b is increased to increase the temperature. Condensation can be removed or condensation can be prevented without interfering with the operation of the use side heat exchanger 26a. In particular, when a natural convection heat exchanger such as a chilled beam is used as the use

side heat exchangers

26a and 26b, the heat exchange amount of the use

side heat exchangers

26a and 26b becomes small. For this reason, when indoor dew point temperature is high, there exists a possibility that use

side unit

2a, 2b itself may condense. Even in such a case, it is possible to increase the temperature of the refrigerant flowing through the adjustment intermediate heat exchanger 15b to remove dew condensation or prevent the dew condensation from occurring. Furthermore, for example, even when performing a high sensible heat operation in which only the temperature (sensible heat) is lowered so as to remove moisture in the room air as much as possible, condensation can be reliably removed or the occurrence of condensation can be prevented. .

Further, as shown in FIG. 5, by controlling the operation of the adjustment intermediate heat exchanger 15b based on the maximum dew point temperature Tmax, among the plurality of usage side heat exchangers requiring dew condensation suppression control, the most due to dew condensation. Condensation suppression control is performed based on the use side heat exchangers that are adversely affected, so it is possible to reliably suppress the occurrence of condensation in any of the multiple usage side heat exchangers that require condensation suppression control. it can. It should be noted that when the temperature becomes appropriate in the use side heat exchanger other than the use side heat exchanger 26b having the maximum dew point temperature Tmax, the primary side flow switching device 23b and the primary side flow switching device 23a return to the normal operation. It may be controlled to. Furthermore, if at least one adjustment intermediate heat exchanger 15b is provided, it is possible to perform dew condensation suppression control of a plurality of usage-side units, so a heat medium having a different temperature is used for each usage-side heat exchanger. Since it is not necessary to generate, dew condensation suppression control can be performed efficiently.

The embodiment of the present invention is not limited to the above embodiment. For example, FIG. 1 illustrates a case where a plurality of usage-

side units

2a and 2b have the same configuration, but usage-

side units

2a and 2b having different configurations may be installed. Even in this case, the dew point temperature information is output from the

use side units

2a and 2b to the intermediate unit control means 53 (see FIG. 3), and control for preventing condensation is performed.

Moreover, in FIG. 1, although the case where the temperature detection means 34a and 34b are provided for every intermediate | middle heat exchanger 15a and 15b is illustrated, when it is a utilization side heat exchanger which does not require dew condensation suppression control, No temperature detection means is required.

Furthermore, although the case where two intermediate heat exchangers 15a and 15b are provided in FIG. 1 is illustrated, two or more may be provided. As described above, since the heat exchange characteristics can be changed for each of the intermediate heat exchangers 15a and 15b, heat media having different temperatures can be generated for each of the intermediate heat exchangers. Therefore, in the above embodiment, the dew condensation suppression control is performed by using one adjustment intermediate heat exchanger 15b. However, when the intermediate unit 3 includes three or more intermediate heat exchangers. Condensation suppression control may be performed using two or more adjustment intermediate heat exchangers.

1 heat source unit, 2, 2a, 2b usage side unit, 3 intermediate unit, 4a first connection pipe, 4b second connection pipe, 5a high pressure main pipe, 5b low pressure main pipe, 9 throttling device, 10 compressor, 11 first refrigerant flow Path switch, 12 heat source side heat exchanger, 12a blower, 13 flow path forming part, 13a-13d check valve, 15, 15a, 15b intermediate heat exchanger, 16, 16a, 16b throttle device, 17a liquid refrigerant supply valve , 17b Gas refrigerant supply valve, 18, 18a, 18b Second refrigerant flow switch, 19 Accumulator, 21, 21a, 21b Pump, 22, 22a, 22b Secondary water flow switch, 23, 23a, 23b Primary Side water flow switching device, 25, 25a, 25b Flow rate adjusting means, 26, 26a, 26b Use side heat exchanger, 27, 28 Heat medium piping 31, 31a, 31b Heat medium temperature sensor, 32, 32a, 32b Suction temperature sensor, 33, 33a, 33b Suction humidity sensor, 34, 34a, 34b Outlet water temperature sensor, 35, 35a, 35b First refrigerant temperature sensor, 36, 36a, 36b Pressure sensor, 37, 37a, 37b Second refrigerant temperature sensor, 51 Heat source unit control means, 52a, 52b Use side unit control means, 53 Intermediate unit control means, 53a Maximum dew point temperature detection means, 53b Heat medium circuit control Means, 53c refrigerant circuit control means, 53d arithmetic processing circuit, 100 air conditioner, 520 target model determination means, 521 target determination means, 522 dew point temperature calculation means, 523 comparison calculation means, 524 thermo determination means, 525 operation signal transmission means 526 Control panel, A cold Circulation circuit, B heat medium circulation circuit, T heating medium temperature, Tr target setting temperature range, Tt target water temperature, Tmax maximum dew point temperature.

Claims

A heat source side unit including a compressor that compresses the refrigerant, and a heat source side heat exchanger that performs heat exchange between the air and the refrigerant;
A plurality of usage-side units including usage-side heat exchangers for exchanging heat between air and a heat medium;
A plurality of intermediate heat exchangers that are connected to the heat source side unit by a refrigerant pipe and connected to the user side unit by a heat medium pipe, and perform heat exchange between the refrigerant and the heat medium;
A heat medium flow switching device that switches a combination of connections between each of the use side units and each of the intermediate heat exchangers;
Object determination means for respectively determining whether or not to perform dew condensation suppression control for detecting dew condensation in each use side unit and suppressing dew condensation for each use side unit;
Temperature detection means for detecting, as the heat medium temperature, the temperature of the heat medium flowing into the use side unit determined to perform the dew condensation suppression control by the target determination means;
The use side unit determined to perform the dew condensation suppression control by the target determination unit is connected to the adjustment intermediate heat exchanger allocated for the dew condensation suppression control among the plurality of intermediate heat exchangers. A heat medium circuit control means for controlling the heat medium flow path switch;
Refrigerant circuit control means for controlling the temperature of the refrigerant flowing into the adjustment intermediate heat exchanger so that the heat medium temperature detected by the temperature detection means falls within a predetermined target set temperature range. An air conditioner characterized.
A refrigerant throttle device for expanding or depressurizing the refrigerant flowing into the adjustment intermediate heat exchanger;
2. The air conditioner according to claim 1, wherein the refrigerant circuit control means controls the temperature of the refrigerant by adjusting a throttle amount of the refrigerant throttle device.
The refrigerant circuit control means, when the heat medium temperature is in the target set temperature range, controls the refrigerant throttling device so that the heat medium temperature falls within the target set temperature range. 2. The air conditioning apparatus according to 2.
The heat source side unit is capable of heating operation and cooling operation,
A refrigerant flow path switch that switches the flow path of the refrigerant flowing into the adjustment intermediate heat exchanger between a heating flow path during heating operation and a cooling flow path during cooling operation;
The refrigerant circuit control means controls the temperature of the refrigerant flowing into the adjustment intermediate heat exchanger by switching the flow path of the adjustment intermediate heat exchanger with the refrigerant flow path switch. The air conditioner according to any one of claims 1 to 3, wherein
When the heat medium temperature is lower than the target set temperature range, the refrigerant circuit control means changes the refrigerant flow path flowing into the adjustment intermediate heat exchanger by the refrigerant flow path switch to the heating flow path. The air conditioner according to claim 4, wherein the air conditioner is set.
When the heat medium temperature is higher than the target set temperature range, the refrigerant flow rate control means changes the refrigerant flow path flowing into the adjustment intermediate heat exchanger by the refrigerant flow path switch to the cooling flow path. 6. The air conditioner according to claim 4, wherein the air conditioner is set.
Suction temperature detection means for detecting the temperature of air sucked into the use side unit;
Suction humidity detection means for detecting the humidity of the air sucked into the use side unit;
Further comprising
Whether or not the object determination means detects the dew condensation state by using the suction temperature detected by the suction temperature detection means and the suction humidity detected by the suction humidity detection means to perform the condensation suppression control. The air conditioner according to any one of claims 1 to 6, wherein the air conditioner is determined.
Suction temperature detection means for detecting the temperature of air sucked into the use side unit;
Suction humidity detection means for detecting the humidity of the air sucked into the use side unit;
Dew point temperature calculating means for calculating dew point temperature using the suction temperature detected by the suction temperature detecting means and the suction humidity detected by the suction humidity detecting means, and
8. The refrigerant circuit control means sets the predetermined target set temperature range with reference to the dew point temperature calculated by the dew point temperature calculation means. Item 1. An air conditioner according to item 1.
The refrigerant circuit control means detects a maximum dew point temperature having the highest dew point temperature from among the dew point temperatures in the use side unit that is determined to perform the dew condensation suppression control, and the predetermined dew point based on the detected maximum dew point temperature. The air conditioning apparatus according to claim 7 or 8, wherein a target set temperature range is set.
A flow rate adjusting means for adjusting the flow rate of the heat medium flowing through the adjustment intermediate heat exchanger and the use side unit;
A heat medium circuit control means for controlling the operation of the flow rate adjusting means,
The heat medium circuit control means controls the flow rate adjusting means so that the heat medium temperature falls within the predetermined target set temperature range. The air conditioning apparatus according to item.