JP7374633B2 - Air conditioners and air conditioning systems - Google Patents

Description

The present invention relates to an air conditioner and an air conditioning system.

Conventionally, in a unit case with a water heat source heat pump device, a refrigerant-to-air heat exchanger for indoor air conditioning using a heat pump and a water-to-air heat exchanger for indoor air conditioning are installed in parallel, and a common feature is used for both of these heat exchangers. A single ventilation fan is provided, and a switching damper is provided that allows the fan's ventilation path to select one of the heat exchangers or to face both, and the heat source water is connected to the water-to-air heat exchanger and the heat pump. An air-conditioning equipment unit has also been proposed that is provided with piping equipment for supplying and circulating the water to the water-to-refrigerant heat exchanger separately or to both of them (for example, Patent Document 1).

In addition, there is a housing that connects the return air system and the outside air system on the upstream side and the supply air system on the downstream side, forming a ventilation path through which the mixed air of the return air and outside air flows. A water spray humidifier that performs adiabatic humidification and saturated humidification by spraying water into the air, and a water spray humidifier that controls the temperature of the spray water collected after humidifying the mixed air and the volume of return air and outside air supplied to the housing. An air conditioner characterized by being equipped with a spray water temperature sensor that is detected as a control index has also been proposed (for example, Patent Document 2). Patent Document 2 discloses that return air is supplied from a return air system to mixed air whose humidity has been adjusted through a return air system bypass, and the dry bulb temperature of the return air detected by a return air temperature sensor in the return air system is used as a control index. It is stated that the dry bulb temperature of the return air returned from the room to be air conditioned is controlled to a constant level by adjusting the amount of bypass return air supplied into the housing using the second return air damper of the return air system bypass. .

Publication No. 6-15276 JP2012-52722A

Conventionally, in the dehumidifying operation of an air conditioner, if the set temperature is higher than the dew point temperature, the cooled and dehumidified air is reheated to a desired temperature and controlled to be blown into the room. Such control is not energy efficient. A technique has also been proposed in which indoor air is mixed with cooled and dehumidified air to achieve a desired temperature. However, there has been a problem in that it is difficult to improve the accuracy of temperature control, especially since return air whose temperature has not been adjusted is mixed and the air volume is controlled by a damper, which ultimately impairs comfort.

Therefore, an object of the present invention is to provide an air conditioner that has a good balance between comfort and energy saving in dehumidifying operation.

The air conditioner according to the present invention includes a fan coil unit that is provided on the flow path of heat source water and performs heat exchange between the heat source water and the air, and a fan coil unit that is partially provided on the flow path of the heat source water and that exchanges heat between the heat source water and the air. It includes a heat pump unit that exchanges heat with the heat transfer medium and between air and the heat transfer medium. The heat pump unit also includes a first air refrigerant heat exchanger that exchanges heat between air and a heat transfer medium during dehumidification operation, and a second air refrigerant heat exchanger that restricts the inflow of the heat transfer medium during dehumidification operation. and an exchanger.

As described above, among the air refrigerant heat exchangers included in the heat pump unit, the first air refrigerant heat exchanger is used for dehumidifying operation, and the second air refrigerant heat exchanger is not used for dehumidifying operation. In this way, only a part of the air refrigerant heat exchanger (the first air refrigerant heat exchanger) is used for dehumidification, thereby preventing the air passing through the heat pump unit from being excessively cooled. Therefore, for example, energy consumption for reheating can be reduced. On the other hand, since comfort can be obtained through dehumidification, the air conditioner has a good balance between comfort and energy saving during dehumidification operation.

For example, the first air refrigerant heat exchanger exchanges heat between a portion of the air passing through the heat pump unit and the heat transfer medium. In this way, by partially dehumidifying the air, it is possible to avoid excessive cooling of the air even when the air conditioning load is relatively small, and to reduce wasted energy required for reheating. become. Further, the heat pump unit may include a compressor, and the output of the compressor may be controlled based on the relationship between the set indoor dew point temperature and the outlet temperature of the air of the first air refrigerant heat exchanger. For example, desired dehumidification performance can be obtained through such control.

Further, the fan coil unit may include a proportional valve that controls the flow rate of the heat source water, and the opening degree of the proportional valve may be controlled based on the relationship between the set temperature and the room temperature. In this way, the temperature can be precisely controlled by the fan coil unit provided separately from the heat pump unit.

Further, the first air refrigerant heat exchanger and the second air refrigerant heat exchanger may exchange heat between air and a heat transfer medium during cooling operation. In this way, the first air refrigerant heat exchanger and the second air refrigerant heat exchanger are used during the cooling operation, and as mentioned above, only the first air refrigerant heat exchanger, which is a part of the first air refrigerant heat exchanger, is used during the dehumidification operation. It is something that can be done.

An air conditioning system according to another aspect of the present invention may include a plurality of the above-described air conditioners and an outdoor conditioner, and the outdoor conditioner may perform dehumidification using heat source water. Energy consumption efficiency can be improved by dehumidifying the air by using the external air conditioner and further dehumidifying by using the first air refrigerant heat exchanger of the heat pump unit as needed. Therefore, the system can reduce power consumption and realize ZEB (Zero Energy Building).

Note that the contents of the means for solving the above problems can be combined as much as possible without departing from the problems and technical idea of the present invention.

According to the present invention, it is possible to provide an air conditioning unit that provides a good balance between comfort and energy saving during dehumidification operation.

FIG. 1 is a system diagram showing an example of an air conditioner according to this embodiment. FIG. 2 is a diagram showing an example of flow paths of refrigerant and heat source water during dehumidification operation. FIG. 3 is a process flow diagram showing an example of a process during dehumidification operation of the air conditioner 1. FIG. 4 is a process flow diagram showing an example of a process during dehumidification operation of the air conditioner 1. FIG. 5 is a diagram showing the relationship between the outlet temperature T1 of the dehumidifying side air refrigerant heat exchanger 125 and the rotation speed of the inverter of the compressor 121. FIG. 6 is a diagram showing the relationship between the intake air temperature T2 and the opening degree of the two-way valve 111. FIG. 7 is a diagram showing an example of an air conditioning system including a plurality of air conditioners.

Hereinafter, embodiments of an air conditioner including a fan coil unit and a heat pump unit will be described based on the drawings.

FIG. 1 is a system diagram showing an example of an air conditioner according to this embodiment. The air conditioner 1 includes a fan coil unit 11, a heat pump unit 12, and equipment common to these units in one housing. The fan coil unit 11 exchanges heat between heat source water supplied from a chiller or the like and air, and supplies air at a desired temperature to the target space using the blower fan 14. The heat pump unit 12 includes a refrigeration cycle formed by a condenser, an expansion valve, an evaporator, and a compressor, and exchanges heat between a cooling medium (also referred to as a "refrigerant" or a "heat transfer medium") and air. , the blower fan 14 supplies air at a desired temperature to the target space. That is, inside the air conditioner 1, a heat source water flow path 15, a refrigerant flow path 16, and an air flow path 17 are provided. Further, the air conditioner 1 operates based on settings made by the user using the controller 2.

The air conditioner 1 includes a control device 13, an intake temperature/humidity sensor 131, a dehumidifying coil outlet temperature sensor 132, a blower fan 14, and a controller 2 as devices common to the fan coil unit 11 and the heat pump unit 12. Be prepared.

The fan coil unit 11 includes a two-way valve 111, a three-way valve 112, and a fan coil side heat exchanger 113. The two-way valve 111 is a general valve, and in this embodiment is a proportional two-way valve. The two-way valve 111 is provided, for example, near the entrance of the heat source water flow path 15, and controls the flow rate of the heat source water flowing through the heat source water flow path 15 by changing its opening degree. The three-way valve 112 is a general valve, and in this embodiment is a switching three-way valve. The three-way valve 112 allows the heat source water that has entered the air conditioner 1 to flow toward the fan coil unit 11 side or the heat pump unit 12 side. The fan coil side heat exchanger 113 is a heat exchanger that is provided on the heat source water flow path 15 and exchanges heat between the heat source water and air. The air is, for example, indoor air whose temperature is to be controlled.

The heat pump unit 12 includes a compressor 121, a four-way valve 122, a water refrigerant heat exchanger 123, an expansion valve 124, a dehumidification side air refrigerant heat exchanger 125, and a bypass side air refrigerant heat exchanger 125 on a refrigerant flow path 16. It includes a heat exchanger 126 and a two-way valve 127 to form a refrigeration cycle. The compressor 121 compresses, for example, a refrigerant that is a low-pressure gas into a high-pressure and high-temperature gas. The four-way valve 122 switches the flow path of the refrigerant between cooling and heating. The water-refrigerant heat exchanger 123 is provided on the flow path 15 of the heat source water and on the flow path 16 of the refrigerant. The heat source water is introduced into the water-refrigerant heat exchanger 123 with or without the fan coil side heat exchanger 113 . At the same time, refrigerant compressed by the compressor 121 is introduced into the water/refrigerant heat exchanger 123 via the four-way valve 122 during cooling. At this time, the water-refrigerant heat exchanger 123 functions as a condenser, and condenses, for example, a high-pressure gaseous refrigerant into a high-pressure liquid. Note that during heating, refrigerant expanded by the expansion valve 124 is introduced. At this time, the water-refrigerant heat exchanger 123 functions as an evaporator, and evaporates, for example, a low-pressure liquid refrigerant into a low-pressure gas. The expansion valve 124 is, for example, an electronic expansion valve. Further, the expansion valve 124 reduces the pressure of the refrigerant, which is a high-pressure liquid, to a low-pressure liquid, for example. The dehumidification side air refrigerant heat exchanger 125 and the bypass side air refrigerant heat exchanger 126 are provided in parallel on the refrigerant flow path 16 and on the air flow path 17 blown by the ventilation fan 14, respectively. Furthermore, during cooling, refrigerant whose pressure has been reduced by the expansion valve 124 is introduced into the dehumidifying side air refrigerant heat exchanger 125 and the bypass side air refrigerant heat exchanger 126. At this time, the dehumidifying side air refrigerant heat exchanger 125 and the bypass side air refrigerant heat exchanger 126 function as an evaporator, and evaporate, for example, a low-pressure liquid refrigerant into a low-pressure gas. Note that during heating, refrigerant compressed by the compressor 121 is introduced via the four-way valve 122. At this time, the dehumidifying side air refrigerant heat exchanger 125 and the bypass side air refrigerant heat exchanger 126 function as a condenser, and condense, for example, a high-pressure gas refrigerant into a high-pressure liquid. The two-way valve 127 is a general valve, for example, a solenoid valve. The two-way valve 127 is located in the vicinity of the bypass air refrigerant heat exchanger 126 between the dehumidifying air refrigerant heat exchanger 125 and the bypass air refrigerant heat exchanger 126 that are provided in parallel on the refrigerant flow path 16. , is provided in series with the bypass side air refrigerant heat exchanger 126, and switches whether or not to flow the refrigerant to the bypass side air refrigerant heat exchanger 126. In other words, the two-way valve 127 switches whether or not to allow the refrigerant to flow only through the dehumidifying side air refrigerant heat exchanger 125. Note that the dehumidification side air refrigerant heat exchanger 125 corresponds to the "first air refrigerant heat exchanger" according to the present invention, and the bypass side air refrigerant heat exchanger 126 corresponds to the "second air refrigerant heat exchanger" according to the present invention. This corresponds to a heat exchanger. By passing the refrigerant through both the dehumidifying side air refrigerant heat exchanger 125 and the bypass side air refrigerant heat exchanger 126 and operating the inverter of the compressor 121 at 100% rotation speed, the air conditioner 1 has the rated output. It works. That is, the dehumidification side air refrigerant heat exchanger 125 according to the present embodiment constitutes a part of the air refrigerant heat exchanger of the heat pump unit 12, and according to the dehumidification side air refrigerant heat exchanger 125, the air refrigerant The heat exchanger can be partially operated. Therefore, according to the dehumidifying side air refrigerant heat exchanger 125, it is possible to partially dehumidify the air flowing through the air flow path 17, and at the same time, it is possible to prevent the air flowing through the air flow path 17 from being excessively cooled. energy consumption required for reheating can be suppressed when the air conditioning load is relatively small.

The intake temperature/humidity sensor 131 and the dehumidifying coil outlet temperature sensor 132 are existing temperature sensors or temperature/humidity sensors. The intake temperature/humidity sensor 131 is provided at the intake port of the air conditioner 1 and measures the temperature of intake air. The dehumidifying coil outlet temperature sensor 132 is provided at the outlet of the air passing through the dehumidifying air refrigerant heat exchanger 125, and measures the temperature of the air passing through. Note that the intake temperature/humidity sensor 131 and the dehumidification side coil outlet temperature sensor 132 output signals corresponding to the measured temperatures to the control device 13, which will be described later.

Further, the control device 13 includes a processing device such as a microcontroller and a processor, and is connected to a temperature sensor, a valve, etc. provided in the air conditioner 1 by a signal line or wirelessly. Further, the control device 13 acquires a signal indicating temperature from a temperature sensor, and controls opening/closing of a valve and its opening degree.

The blower fan 14 is commonly used by the fan coil unit 11 and the heat pump unit 12. That is, the ventilation fan 14 takes in, for example, indoor air whose temperature is to be controlled, and sends the air, which has been adjusted to a predetermined temperature by the fan coil unit 11 and the heat pump unit 12, into the room.

FIG. 2 is a diagram showing an example of the flow path 15 of refrigerant and heat source water during dehumidification operation. The air conditioner 1 closes the two-way valve 127 to stop the refrigerant from flowing into the bypass air refrigerant heat exchanger 126, and performs dehumidification using only the dehumidification air refrigerant heat exchanger 125. At this time, the indoor dew point temperature set value obtained from the temperature and humidity target values (also referred to as "indoor temperature set value" and "indoor relative humidity set value, respectively") set by the user using the controller 2, and the dehumidifying side coil The rotation speed of the inverter of the compressor 121 is controlled based on the relationship with the temperature measured by the outlet temperature sensor 132. By using some of the plurality of air refrigerant heat exchangers, the dehumidification-side air refrigerant heat exchanger 125 and the bypass-side air refrigerant heat exchanger 126 in the dehumidification operation, the temperature of the air is blown out during the dehumidification operation and the set temperature of the air is adjusted. You can prevent it from dropping too low. Therefore, there is no need for reheating to obtain a desired temperature, resulting in improved energy savings. Note that even if the size of one air refrigerant heat exchanger is reduced, a desired rated output cannot be obtained, for example, when the load is large during cooling. Therefore, a bypass side air refrigerant heat exchanger 126 is provided in which the inflow of refrigerant is bypassed during dehumidification, and a plurality of air refrigerant heat exchangers are provided. That is, during cooling, the air conditioner 1 also causes the refrigerant to flow through the bypass air refrigerant heat exchanger 126, and controls the compressor 121 according to the magnitude of the load.

Furthermore, the air conditioner 1 can control the temperature by adjusting the opening degree of the two-way valve 111 during dehumidification operation. That is, the opening degree of the two-way valve 111 is controlled based on the relationship between the room temperature setting value set by the user using the controller 2 and the intake temperature (room temperature) measured by the intake temperature/humidity sensor 131, and the opening degree of the two-way valve 111 is controlled. change the flow rate. In this way, since the air conditioner 1 includes the fan coil unit 11 and the heat pump unit 12, the temperature can be controlled independently of the humidity control. Furthermore, if the flow rate of the heat source water in the fan coil unit 11 is proportionally controlled, the accuracy of temperature control can be improved compared to the case where the desired temperature is obtained by adjusting the amount of air to be mixed by adjusting the opening degree of a damper, for example. This improves comfort.

<Dehumidification control>
3 and 4 are process flow diagrams showing an example of the process during dehumidification operation of the air conditioner 1. The control device 13 of the air conditioner 1 starts processing as shown in FIG. 3 when the controller 2 selects the dehumidifying operation. It is assumed that the indoor temperature set value Ts (° C.) and the indoor relative humidity set value Hs (%), which are target values for the indoor temperature and humidity, are set when the dehumidifying operation is selected.

The control device 13 opens the three-way valve 112 to the fan coil side heat exchanger 113 side, and introduces the heat source water to the fan coil side heat exchanger 113. Further, the control device 13 closes the two-way valve 127, stops the flow of refrigerant into the bypass side air refrigerant heat exchanger 126, and introduces the refrigerant only into the dehumidification side air refrigerant heat exchanger 125 (FIG. 3: S1). In this step, flow paths for heat source water and refrigerant are formed as shown in FIG. 2.

Further, the control device 13 acquires the outlet temperature T1 of the dehumidifying side air refrigerant heat exchanger 125 from the dehumidifying coil outlet temperature sensor 132, and acquires the intake air temperature T2 and the intake air humidity H2 from the intake air temperature/humidity sensor 131 (Fig. 3:S2). In this embodiment, it is assumed that the intake air is return air from the room, and the intake air temperature is the room temperature.

Furthermore, the control device 13 branches the process based on the relationship between the outlet temperature T1 of the dehumidifying side air refrigerant heat exchanger 125 and the indoor dew point temperature set value Tdpsp (FIG. 3: S3). Note that the indoor dew point temperature setting value Tdpsp is calculated based on a preset indoor temperature setting value Ts (° C.) and an indoor relative humidity setting value Hs (%). That is, the temperature at which air containing water vapor in an amount equal to the indoor relative humidity setting value Hs (%) at the indoor temperature setting value Ts (° C.) starts to condense is set as the indoor dew point temperature setting value Tdpsp. In this step, the control device 13 sets the target outlet temperature T1 of the dehumidifying side air refrigerant heat exchanger 125 to the indoor dew point temperature set value Tdpsp-1 (°C) at which dehumidification is performed, and brings it within a predetermined allowable range. The inverter output of the compressor 121 is controlled so that the For example, when the outlet temperature T1 of the dehumidifying side air refrigerant heat exchanger 125 is smaller than the indoor dew point temperature set value Tdpsp-1-α (°C), the rotation speed of the inverter of the compressor 121 is decreased (see FIG. 3). S4). Note that α is a predetermined value representing the allowable range of dew point temperature. Further, when the outlet temperature T1 of the dehumidifying side air refrigerant heat exchanger 125 is equal to or higher than the indoor dew point temperature set value Tdpsp-1-α (°C) and is equal to or lower than the indoor dew point temperature set value Tdpsp-1+α (°C), The rotation speed of the inverter of the compressor 121 is maintained (FIG. 3: S5). Further, when the outlet temperature T1 of the dehumidifying side air refrigerant heat exchanger 125 is higher than the indoor dew point temperature setting value Tdpsp-1+α (° C.), the rotation speed of the inverter of the compressor 121 is increased (FIG. 3: S6). After S4 to S6, the process transitions to the process shown in FIG. 4 via connector A.

FIG. 5 is a diagram showing the relationship between the outlet temperature T1 of the dehumidifying side air refrigerant heat exchanger 125 and the rotation speed of the inverter of the compressor 121. When the outlet temperature T1 of the dehumidifying side air refrigerant heat exchanger 125 is smaller than the indoor dew point temperature set value Tdpsp-1-α (°C), in S4 of FIG. 3, the rotation speed of the inverter of the compressor 121 is proportionally controlled. and decrease. Further, when the outlet temperature T1 of the dehumidifying side air refrigerant heat exchanger 125 is equal to or higher than the indoor dew point temperature set value Tdpsp-1-α (°C) and is equal to or lower than the indoor dew point temperature set value Tdpsp-1+α (°C), In S5 of FIG. 3, the rotation speed of the inverter of the compressor 121 is maintained and becomes constant. Further, when the outlet temperature T1 of the dehumidification side air refrigerant heat exchanger 125 is higher than the indoor dew point temperature setting value Tdpsp-1+α (° C.), the rotation speed of the inverter of the compressor 121 is proportionally controlled in S6 of FIG. Increase up to 100%.

When the outlet temperature T1 (°C) of the dehumidifying side air refrigerant heat exchanger 125 becomes smaller than the indoor dew point temperature setting value Tdpsp (°C), moisture in the air condenses in the dehumidifying side air refrigerant heat exchanger 125, and dehumidification is performed. . In the above example, the indoor dew point temperature set value Tdpsp-1 (°C) is set as the target, and a tolerance range of α is set above and below, but the target need only be a temperature lower than the indoor dew point temperature set value Tdpsp, and the indoor dew point temperature The value may be Tdpsp-2 (°C) or the like.

Then, in S7 of FIG. 4, the control device 13 branches the process based on the relationship between the intake air temperature T2 and the room temperature set value T2sp (FIG. 4: S7). When the intake air temperature T2 is smaller than the room temperature set value T2sp-β, the opening degree of the two-way valve 111 is decreased (FIG. 4: S8). Note that β is a predetermined value representing an allowable range of room temperature. Further, when the intake air temperature T2 is equal to or higher than the room temperature set value T2sp-β (°C) and lower than the room temperature set value T2sp+β (°C), the opening degree of the two-way valve 111 is maintained (FIG. 4: S9). Further, when the intake air temperature T2 is higher than the room temperature set value T2sp+β (° C.), the opening degree of the two-way valve 111 is increased (FIG. 4: S10). After S8 to S10, the process returns to S2 in FIG. 3 via connector B.

FIG. 6 is a diagram showing the relationship between the intake air temperature T2 and the opening degree of the two-way valve 111. When the intake air temperature T2 is smaller than the room temperature set value T2sp+β (° C.), the opening degree of the two-way valve 111 is proportionally controlled and lowered in S8 of FIG. Further, when the intake air temperature T2 is equal to or higher than the room temperature set value T2sp-β (°C) and equal to or lower than the room temperature set value T2sp+β (°C), the opening degree of the two-way valve 111 is maintained in S9 of FIG. Further, when the intake air temperature T2 is higher than the room temperature set value T2sp+β (° C.), the opening degree of the two-way valve 111 is proportionally controlled in S10 of FIG. 4, and increases with an upper limit of 100%.

In this embodiment, medium-temperature cold water of about 15° C. is supplied to the fan coil unit 11 as heat source water. When the intake air temperature T2 (°C) is lower than the room temperature set value T2sp (°C) by more than a predetermined tolerance range β, the two-way valve 111 is opened because there is no need to cool the air blown from the air conditioner 1 any further. reduce the degree of On the other hand, when the intake air temperature T2 (°C) is higher than the room temperature set value T2sp (°C) by more than the predetermined allowable width β, the fan coil unit 11 increases the opening degree of the two-way valve 111, and the air conditioner cooling the blown air.

<Effect>
The control in FIG. 5 and the control in FIG. 6 are independently executed by the heat pump unit 12 and the fan coil unit 11, respectively. Therefore, the air conditioner 1 can precisely control the set temperature by particularly controlling the opening degree of the two-way valve 111 of the fan coil unit 11. In addition, the bypass side air refrigerant heat exchanger 126, which is a part of the air refrigerant heat exchanger included in the heat pump unit 12, is bypassed during dehumidification operation, and the other part, the dehumidification side air refrigerant heat exchanger 125, dehumidifies the air. I do. That is, the air passing through the bypass side air refrigerant heat exchanger 126 is not cooled, but is mixed with the air dehumidified by the dehumidification side air refrigerant heat exchanger 125 and blown out by the air conditioner 1, so that the heat pump unit 12 dehumidifies the air. Excessive cooling of the air during operation can be avoided, and energy waste required for reheating can be suppressed.

<Air conditioning system>
FIG. 7 is a diagram showing an example of an air conditioning system including a plurality of air conditioners. In the example of FIG. 7, a plurality of air conditioners 1 are provided on each floor or in a living room. The air conditioner 1 is, for example, the device shown in FIG. The system also includes an outside conditioner 3, an air-cooled chiller 4, and a variable flow rate pump 5. The outside air conditioner 3 takes in clean air into the system. The air-cooled chiller 4 produces, for example, medium-temperature cold water of about 15° C. as heat source water. Further, the pump 5 supplies heat source water to each of the plurality of air conditioners 1. Moreover, each of the outdoor conditioner 3 and the air conditioner 1 is equipped with a proportional two-way valve 111, and the amount of heat source water introduced is variable.

By making the flow rate of the heat source water variable, the energy required for pumping water can be reduced compared to when a constant flow rate continues to flow. Further, the outside air conditioner 3 also performs dehumidification using the heat source water of medium temperature cold water produced by the air-cooled chiller 4. The remaining latent heat that cannot be dehumidified by the external conditioner 3 is processed by the dehumidifying side air refrigerant heat exchanger 125 of the heat pump unit 12. In this way, the system can reduce energy consumption and realize ZEB (Zero Energy Building).

<Others>
The embodiments and modified examples are merely examples, and the present invention is not limited to the configurations described above. The contents of the embodiments and modifications can be combined as much as possible without departing from the problems and technical ideas of the present invention.

The air conditioner 1 may further perform load reset control that calculates the indoor dew point temperature based on the suction temperature and suction humidity, and changes the set value so that the outlet temperature does not fall below the dew point temperature. In this way, dew condensation at the air outlet of the air conditioner 1 can be prevented.

Temperature control in the fan coil unit 11 is performed by connecting proportional control of the two-way valve 111 and VAV (Variable Air Volume) control of the blower fan 14 in series to form one feedback loop, and performing cascade control based on the outlet temperature of the air conditioner 1. Control may also be performed.

Heat pump unit 12 may include three or more air refrigerant heat exchangers. In this case as well, dehumidification operation is performed using some air refrigerant heat exchangers.

Moreover, the above-mentioned system can also be used in further combination with radiant air conditioning, heat storage tanks, and other devices.

1 Air conditioner 11 Fan coil unit 111 Two-way valve (proportional two-way valve)
112 Three-way valve (switching three-way valve)
113 Fan coil side heat exchanger 12 Heat pump unit 121 Compressor 122 Four-way valve 123 Water-refrigerant heat exchanger 124 Expansion valve 125 Dehumidification-side air-refrigerant heat exchanger 126 Bypass-side air-refrigerant heat exchanger 127 Two-way valve 13 Control device 131 Suction Temperature and humidity sensor 132 Dehumidification side coil outlet temperature sensor 14 Blow fan 15 Heat source water flow path 16 Refrigerant flow path 17 Air flow path 2 Controller 3 Outdoor conditioner 4 Air-cooled chiller 5 Pump

Claims (4)

a fan coil unit provided on a flow path of heat source water and including a proportional valve for exchanging heat between the heat source water and air and controlling the flow rate of the heat source water ;
a heat pump unit that is partially provided on a flow path of the heat source water and performs heat exchange between the heat source water and the heat transfer medium and between the air and the heat transfer medium;
Equipped with
The heat pump unit includes a first air refrigerant heat exchanger that exchanges heat between the air and the heat transfer medium during dehumidification operation, and a second air refrigerant heat exchanger that restricts the inflow of the heat transfer medium during dehumidification operation. Equipped with a refrigerant heat exchanger and a compressor ,
The heat pump unit controls the output of the compressor based on the relationship between the set indoor dew point temperature and the air outlet temperature of the first air refrigerant heat exchanger, and the fan coil unit controls the A process of controlling the opening degree of the proportional valve based on the relationship between temperature and room temperature is independently executed during dehumidification operation.
Air conditioner. The air conditioner according to claim 1, wherein the first air refrigerant heat exchanger exchanges heat between a portion of the air passing through the heat pump unit and the heat transfer medium. The air conditioner according to claim 1 or 2 , wherein the first air refrigerant heat exchanger and the second air refrigerant heat exchanger exchange heat between the air and the heat transfer medium during cooling operation. Machine. A plurality of air conditioners according to any one of claims 1 to 3 ,
An outside conditioning machine,
Equipped with
The outdoor conditioner dehumidifies using the heat source water. The air conditioning system.

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