JP5355649B2 - Air conditioning system - Google Patents

Description

  The present invention relates to an air conditioning system including a ventilation device.

  Conventionally, there is an air conditioning system including an air conditioner including a refrigeration cycle and a ventilator. The refrigeration cycle is configured such that a refrigerant circulates by connecting a compressor, a four-way valve, an outdoor heat exchanger, a decompression device, and an indoor heat exchanger in order by piping. During the cooling operation, the high-temperature and high-pressure gas refrigerant compressed by the compressor is sent to the outdoor heat exchanger, and the refrigerant is liquefied by exchanging heat with air by the outdoor heat exchanger. The liquefied refrigerant is decompressed by the decompression device to be in a gas-liquid two-phase state, and is gasified by absorbing heat from ambient air in the indoor heat exchanger. On the other hand, in the indoor heat exchanger, air is deprived of heat by the refrigerant. As a result, the indoor space is cooled. The refrigerant gasified by the indoor heat exchanger returns to the compressor.

  The ventilator performs an operation of replacing indoor air with fresh outdoor air.

  The air conditioning load in the air conditioning system includes the heat load from the outside air introduced from the ventilator (= outdoor total heat load), the heat load generated in the room (= indoor total heat load), and the heat load entering from the building wall ( == once-through load) is dominant. In order to ensure indoor comfort, it is necessary to set the indoor temperature and humidity to the target temperature and humidity. To that end, it is necessary to process the outdoor heat total heat load, the indoor total heat load, and the once-through load. That is, it is necessary to process not only the sensible heat load but also the outdoor heat total heat load and the latent heat load that is a part of the room total heat load. Since dehumidification is particularly important during cooling operation, it is necessary to secure the dehumidification amount by treating the latent heat load. For this reason, the operation is performed at a low evaporation temperature. In this case, there has been a problem that the compressor input increases and the operation efficiency decreases.

  Therefore, conventionally, there is a technique that enables high-efficiency operation while changing the ventilation amount according to the outside air temperature humidity and ensuring the dehumidification amount (see, for example, Patent Document 1).

JP 2001-272086 A (summary)

However, in the technique of Patent Document 1, in order to ensure indoor comfort while performing ventilation during cooling operation, ventilation is not performed when the air conditioning load increases due to ventilation. In other words, in order to perform high-efficiency operation, the operation is performed while ignoring the necessary ventilation. Therefore, ventilation is insufficient, the CO ₂ concentration in the chamber there is a problem that rises.

  The present invention has been made in view of such points, and an object thereof is to provide an air conditioning system capable of improving comfort and improving efficiency while ensuring a necessary ventilation amount during cooling operation. .

The air conditioning system according to the present invention has a refrigeration cycle in which a compressor, an outdoor heat exchanger, an expansion valve, and an indoor heat exchanger are sequentially connected by piping so that the cooling operation can be performed, and a necessary ventilation amount according to the indoor environment is ensured. The air volume is controlled so that the indoor air and the outdoor air are exchanged for ventilation, the indoor temperature detecting device for detecting the indoor temperature, the indoor humidity detecting device for detecting the indoor humidity, and the outdoor air temperature. Detecting outside air temperature detecting device, outside air humidity detecting device for detecting outside air humidity, temperature / humidity setting device for setting target indoor temperature / humidity, and indoor load setting device for setting indoor total heat load and indoor sensible heat load As the temperature difference between the room temperature detected by the room temperature detection device and the target room temperature set in the temperature / humidity setting device becomes smaller, control is performed to increase the target evaporation temperature within a predetermined evaporation temperature range. The control device includes the indoor temperature detection device, the indoor humidity detection device, the outside air temperature detection device, the outside air humidity detection device, and the detected value of the outside air humidity detection device, and the ventilation air volume of the ventilation device. Find the sensible heat load, find the through load from the detected value of the indoor temperature detector, the detected value of the outside air temperature detector, the surface area of the building wall, and the heat transmissivity of the wall. The sensible heat ratio, which is the ratio of the air conditioning sensible heat load in the air conditioning total heat load, is calculated from the sensible heat load, the once-through load, and the indoor total heat load and the indoor sensible heat load set by the indoor load setting device. The maximum value of the predetermined evaporation temperature range is determined based on the sensible heat ratio and the target indoor temperature / humidity set by the temperature / humidity setting device, and the difference between the indoor temperature and the target indoor temperature is greater than a predetermined value. When it becomes smaller, it is detected by the indoor humidity detector. And it corrects the sensible heat ratio according to the difference between the detected value and the target indoor humidity is.

  According to the present invention, the air volume control of the ventilation device is performed independently of the refrigeration cycle, and the necessary ventilation volume is always secured, so that the indoor air quality can be kept good. In addition, control was performed to change the target evaporation temperature according to the temperature difference between the indoor temperature and the target indoor temperature within the range of the maximum evaporation temperature at which the indoor temperature and humidity can be made the target indoor temperature and humidity. It is possible to achieve both comfort and high efficiency.

It is the schematic of the air conditioning system in one embodiment of this invention. It is a figure which shows schematic structure of the ventilation apparatus of FIG. It is a figure which shows the various detection apparatuses installed in the air conditioning apparatus of FIG. It is the schematic of the refrigerant circuit of the air conditioning apparatus of FIG. It is explanatory drawing of the determination method of target evaporation temperature Te according to temperature difference (DELTA) T. FIG. 5 is a ph diagram of the refrigeration cycle in FIG. 4. It is a wet air diagram. It is an air line figure for demonstrating the setting method of maximum evaporation temperature Te_max. It is a figure which shows the control flow in the air conditioning system of one embodiment of this invention. It is a figure which shows the control flow of the deformation | transformation process 1 different from FIG. It is a figure which shows the control flow of the deformation | transformation process 2 different from FIG. It is explanatory drawing of the difference in target evaporation temperature Te by the difference in maximum evaporation temperature Te_max. It is a figure which shows the other structural example 1 of the ventilation apparatus of FIG. It is a figure which shows the other structural example 2 of the ventilation apparatus of FIG.

FIG. 1 is a schematic diagram of an air conditioning system according to an embodiment of the present invention, and shows a top view of a room in which the air conditioning system is installed. In FIG. 1 and the drawings to be described later, the same reference numerals denote the same or corresponding parts, which are common throughout the entire specification.
The air conditioning system 100 includes an air conditioning device 1 and a ventilation device 11. The air conditioner 1 includes a plurality of (here, three) indoor units 9 and an outdoor unit 10. The outdoor unit 10 is installed outside, the indoor unit 9 is installed in the room 101, and each of the outdoor unit 10 and each indoor unit 9 is connected to the centralized controller 102 by a transmission line 12. The air conditioning system 100 includes an input unit 33 as a temperature / humidity setting device for the user to set the room temperature and the room humidity, and operates so as to approach the target temperature / humidity set by the input unit 33. Is done.

FIG. 2 is a diagram illustrating a schematic configuration of the ventilation device of FIG. 1.
As shown in FIG. 2, the ventilator 11 includes two blowers 20 here, and keeps the environment (air quality, for example, CO ₂ concentration) in the room 101 good (for example, keeps the CO ₂ concentration at 1000 ppm or less). The central controller 102 controls the rotational speed of the blower 20 so that ventilation is performed with the necessary ventilation amount (air volume Va). The ventilation device 11 includes an outside air temperature detection device 21, an outside air humidity detection device 22, an indoor temperature detection device 23, and an indoor humidity detection device 24, and can detect indoor and outdoor temperature and humidity. The detection values of these detection devices 21 to 24 are output to the centralized controller 102 via the transmission line 12.

FIG. 3 is a diagram showing various detection devices installed in the air conditioner of FIG.
Although not shown in FIG. 1, the air conditioner 1 is provided with various detection devices as shown in FIG. That is, each indoor unit 9 includes an evaporation temperature detection device 31 and an indoor temperature detection device 32.

  In addition, the air conditioning system 100 includes a occupancy number detection device 34 that detects the number of persons existing in each air-conditioning area for each indoor unit 9, and detection by all the occupancy number detection devices 34. By summing up the results, the number of people in the room 101 can be grasped. The occupancy detection device 34 may be any method as long as it can determine the occupancy, an infrared human sensor may be used, or a centralized controller that manually inputs the occupancy from the input unit 33. A method of setting to 102 may be used.

FIG. 4 is a schematic diagram of a refrigerant circuit of the air conditioner of FIG.
The air conditioner 1 includes a compressor 2, a four-way valve 3, an outdoor heat exchanger 4, an expansion valve 5 as a decompression device, and an indoor heat exchanger 6 that are sequentially connected by piping so that the refrigerant circulates. Has a cycle. The air conditioner 1 further includes an outdoor heat exchanger blower 7 and an indoor heat exchanger blower 8. The outdoor unit 10 is provided with a compressor 2, a four-way valve 3, an outdoor heat exchanger 4, and an outdoor heat exchanger blower 7, and the indoor unit 9 is provided with an expansion valve 5, an indoor heat exchanger 6, and an indoor heat exchanger. A blower 8 is installed.

  The air conditioner 1 configured as described above can perform a cooling operation or a heating operation by switching the four-way valve 3. When the four-way valve 3 is switched to the solid line side in FIG. When the evaporator / outdoor heat exchanger 4 becomes a condenser and the cooling operation is performed, and the four-way valve 3 is switched to the dotted line side in FIG. 1, the indoor heat exchanger 6 becomes a condenser and the outdoor heat exchanger 4 becomes an evaporator. Heating operation is performed. The air conditioner 1 is only required to be capable of at least cooling operation. Therefore, the four-way valve 3 is not necessarily an essential configuration and can be omitted.

  Next, operation | movement of the refrigerating cycle of the air conditioning apparatus 1 is demonstrated.

(Cooling operation)
In the air conditioner 1, during cooling, the refrigerant compressed by the compressor 2 becomes a high-temperature and high-pressure gas refrigerant, which is sent to the outdoor heat exchanger 4 through the four-way valve 3. The refrigerant flowing into the outdoor heat exchanger 4 is liquefied by exchanging heat with the outdoor air conveyed by the outdoor heat exchanger blower 7 and dissipating heat. The liquefied refrigerant is decompressed by the expansion valve 5 to become a gas-liquid two-phase state, and flows into the indoor heat exchanger 6. The refrigerant that has flowed into the indoor heat exchanger 6 exchanges heat with the indoor air conveyed by the indoor heat exchanger blower 8, gasifies by absorbing heat, and is returned to the compressor 2. As described above, the refrigerant circulates through the refrigerant circuit to perform the cooling operation.

(Heating operation)
In the air conditioner 1, during heating, the refrigerant compressed by the compressor 2 becomes a high-temperature and high-pressure gas refrigerant, which is sent to the indoor heat exchanger 6 through the four-way valve 3. The refrigerant flowing into the indoor heat exchanger 6 is liquefied by exchanging heat with the indoor air conveyed by the indoor heat exchanger blower 8 and dissipating heat. The liquefied refrigerant is decompressed by the expansion valve 5 to be in a gas-liquid two-phase state, and flows into the outdoor heat exchanger 4. The refrigerant that has flowed into the outdoor heat exchanger 4 exchanges heat with the outdoor air conveyed by the outdoor heat exchanger blower 7, gasifies by absorbing heat, and is returned to the compressor 2. As described above, the heating operation is performed by circulating the refrigerant through the refrigerant circuit.

Next, specific control in the air conditioning system 100 will be described.
The air conditioning system 100 responds to the difference ΔT between the room temperature Ta_i [° C.] detected by the room temperature detection device 23 of the ventilation device 11 and the target room temperature Ta_tgt [° C.] set by the user from the input unit 33. The target evaporation temperature Te [° C.] is determined, and control of the refrigeration cycle (rotational speed control of the compressor 2, opening control of the expansion valve 5, control of the blower is performed so that the evaporator evaporation temperature becomes the target evaporation temperature Te. Control).

FIG. 5 is an explanatory diagram of a method for determining the target evaporation temperature Te according to the temperature difference ΔT. In FIG. 5, the horizontal axis represents the temperature difference ΔT, and the vertical axis represents the target evaporation temperature Te. FIG. 6 is a ph diagram of the refrigeration cycle of FIG.
The target evaporation temperature Te is determined from the maximum evaporation temperature Te_max [° C.], the minimum evaporation temperature Te_min [° C.], and ΔT using the characteristic shown in FIG.

  Te = {(Te_max−Te_min) / T0 × ΔT} + Te_max (1)

  Here, T0 is a predetermined temperature difference, for example, 1 ° C. The minimum evaporation temperature Te_min is, for example, a temperature at which a sufficient cooling capacity can be ensured, for example, 0 ° C. The maximum evaporation temperature Te_max is an evaporation temperature at which the indoor humidity can achieve the target indoor humidity RH_tgt [%]. A method for setting the maximum evaporation temperature Te_max will be described later.

  As is apparent from FIG. 5, control is performed to increase the target evaporation temperature Te as the temperature difference ΔT decreases. In this way, by increasing the target evaporation temperature Te as the load decreases, the refrigerant state at the inlet of the compressor 2 changes from the point a to the point b as shown in FIG. Thereby, as can be seen from the ph diagram shown in FIG. 6, the input of the compressor 2 is reduced, and high-efficiency operation can be achieved. In the normal operation of the air conditioner, the operation time is long where the temperature difference ΔT is small. Therefore, this high-efficiency operation greatly affects the energy saving effect.

  FIG. 7 is a moist air diagram, and is an explanatory diagram of the relationship between the evaporation temperature, the sensible heat ratio SHF, and the dehumidification amount. In FIG. 7, the vertical axis represents absolute humidity [kg / kg ′], and the horizontal axis represents dry bulb temperature [° C.]. The air state is represented by one point on the wetness diagram from the temperature and humidity, and the air state of the room 101 is point A (hereinafter referred to as air temperature and humidity A). Hereinafter, the relationship among the evaporation temperature, the sensible heat ratio SHF, and the dehumidification amount will be described with reference to FIG.

  First, the sensible heat ratio SHF will be described. The sensible heat ratio SHF is expressed as sensible heat ratio = sensible heat / (sensible heat + latent heat). Therefore, the operation where the sensible heat ratio SHF is 1 means that the dehumidification is not performed at all (that is, the absolute humidity does not change) and the room temperature is lowered. Therefore, in FIG. 7, the operation at a sensible heat ratio of 1 is expressed by a line extending directly from the air temperature and humidity A, and the intersection of the line and the saturation line is the evaporation temperature T3 at the sensible heat ratio of 1. In other words, if the evaporation temperature is T3, an operation with a sensible heat ratio of 1 is performed to lower the room temperature without performing dehumidification at all. In this case, air having a temperature and humidity on the line of sensible heat ratio 1 connecting the air temperature and humidity A and the evaporation temperature T3 flows out from the outlet side of the evaporator.

  Here, consider a case where the temperature difference ΔT decreases and the target evaporation temperature Te is increased from T1 to T2. In this case, as described above, by increasing the target evaporation temperature Te, high-efficiency operation is achieved, but since the sensible heat ratio SHF increases from 0.6 to 0.7, the latent heat capacity (dehumidification amount) decreases, The room humidity increases. Therefore, as described above, even if the target evaporation temperature Te is increased with a decrease in the temperature difference ΔT in order to improve the operation efficiency, the indoor humidity becomes the target indoor humidity RH_tgt by increasing the target evaporation temperature Te. It is necessary not to exceed it.

  That is, the upper limit (maximum evaporation temperature Te_max) of the target evaporation temperature Te needs to be within a range where the target indoor humidity RH_tgt can be achieved, and the upper limit of the target evaporation temperature Te needs to be determined. In other words, if the target evaporation temperature Te is equal to or lower than the maximum evaporation temperature Te_max, the indoor humidity can be set within the target indoor humidity RH_tgt. As described above, the target evaporation temperature Te of the air conditioning system is controlled in accordance with the temperature difference ΔT within a range equal to or less than the maximum evaporation temperature Te_max, thereby ensuring both necessary dehumidification and high-efficiency operation. It can be realized. As for ventilation, since the ventilator 11 performs ventilation with the required ventilation amount independently of the air conditioning device 1, the air conditioning system of the present embodiment can only provide dehumidification and high-efficiency operation. It is also possible to secure ventilation.

FIG. 8 is an air diagram for explaining a method of setting the maximum evaporation temperature Te_max. Hereinafter, the concept for setting the maximum evaporation temperature Te_max will be described first.
In the present embodiment, the purpose is to perform high-efficiency control of the refrigeration cycle while ensuring the necessary ventilation, and when setting the maximum evaporation temperature Te_max, the target indoor temperature Ta_tgt and target Set so that indoor humidity RH_tgt can be achieved.

  As described above, the air conditioning load is a heat load from outside air introduced from the ventilator 11 (= outdoor total heat load), a heat load generated indoors (= indoor total heat load), and a building wall. There is a thermal load (= once-through load). Therefore, the sensible heat ratio SHF in this air conditioning load is obtained, and the sensible heat ratio SHF is set as the maximum sensible heat ratio SHFmax that can handle the latent heat load. Then, as shown in the air diagram of FIG. 8, a straight line having an inclination determined by the sensible heat ratio SHFmax is extended from the target room temperature and humidity, and a point where the straight line and the saturation curve intersect is defined as the maximum evaporation temperature Te_max.

  By determining the maximum evaporation temperature Te_max in this way, it is possible to determine the maximum evaporation temperature Te_max that can achieve the target indoor humidity Ta_tgt and RH_tgt while maintaining the necessary ventilation. Then, by setting the target evaporation temperature Te below the maximum evaporation temperature Te_max and operating, the explanation will be repeated. However, the latent heat load can be sufficiently processed, and the indoor humidity can reach the target indoor humidity RH_tgt. The efficiency is improved, and a high-efficiency operation is possible in which the target evaporation temperature Te is increased according to the load, thereby improving the energy saving performance.

Next, a specific method for calculating the maximum evaporation temperature Te_max will be described.
As described above, the maximum evaporation temperature Te_max is determined from the sensible heat ratio SHFmax of the air conditioning total heat load, the target indoor temperature Ta_tgt, and the target indoor humidity RH_tgt.

(Calculation of SHFmax)
In order to calculate SHFmax, first, an outdoor air total heat load Ql_o [kW], an indoor total heat load Ql_i [kW], and a once-through load Ql_k [kW] are obtained.

1. Outside air total heat load Ql_o
The external heat total heat load Ql_o due to the intrusion of the external air by ventilation is expressed by Expression (2).

Ql_o = Va * [rho] a * (Ia_o-Ia_i) / 3600 (2)
here,
Va [m ³ / h]: Ventilation air volume of the ventilator 11 ρa [kg / m ³ ]: Air density Ia_i [kJ / kg]: Indoor air enthalpy calculated from Ta_i [° C.] and RH_i [%] Ia_o [kJ / kg]: Outdoor air enthalpy calculated from Ta_o [° C.] and RH_o [%] RH_i [%]: Detection value of the indoor humidity detection device 24 RH_o [%]: Detection value of the outdoor air humidity detection device 22

2. Outside air sensible heat load Ql_os
An outside air sensible heat load Ql_os [kW] due to the entry of outside air by ventilation is expressed by Expression (3).
Ql_os = Va × ρa × (Ta_o−Ta_i) / 3600 (3)
here,
Ta_o [° C.]: Detection value of the outside air temperature detection device 21 Ta_i [° C.]: Detection value of the indoor temperature detection device 23

3. Indoor total heat load Ql_i, indoor sensible heat load Ql_is
The total indoor heat load Ql_i is the sum of the total total heat load Ql_m generated from the human body in the room 101 and the total heat load Ql_inp generated from the heat generating devices such as OA devices and lighting devices. The total total heat load Ql_m [kW] generated from the human body in the room is expressed by Expression (4). For example, ql_ms is 70 [W / person] and ql_ml is 50 [W / person].

Ql_m = (ql_ms + ql_ml) × N (4)
here,
ql_ms [kW / person]: Predetermined sensible heat load per person ql_ml [kW / person]: Predetermined latent heat load per person N (person): In-room occupancy detection device 34 in the air conditioning system 100 Total number of people detected in

  Further, the total sensible heat load Ql_ms [kW] generated from the human body in the room is expressed by Expression (5).

 Ql_ms = ql_ms × N (5)

  Further, since the amount of heat generated from the indoor heat generating device is determined by the equipment, the total heat load Ql_inp [kW] by the heat generating device can be input to the centralized controller 102 in advance.

  From the above, the indoor total heat load Ql_i is expressed by Expression (6).

 Ql_i = Ql_m + Ql_inp (6)

  Moreover, since Ql_inp [kW] is only sensible heat, the indoor sensible heat load Ql_is [kW] is expressed by Expression (7).

 Ql_is = Ql_ms + Ql_inp (7)

4). Through-flow load Ql_K [kW]
Since the through-flow load Ql_K is determined by the intrusion heat from the wall, the wall surface area A (m ² ), the wall heat-through rate K (kW / (m ² · K)), the outside air temperature Ta_o [° C.], the room It is expressed by equation (8) using the temperature Ta_i [° C.]. Ql_K [kW] is only sensible heat.

 Ql_K = A * K * (Ta_o-Ta_i) (8)

  As described above, the outdoor sensible heat load Ql_os, the indoor sensible heat load Ql_is, and the once-through load Ql_K are calculated, and the sensible heat ratio SHF of the air-conditioning total heat load is calculated by the equation (9).

SHF = (Ql_os + Ql_is + Ql_K) / (Ql_o + Ql_i + Ql_K)
... (9)

  The sensible heat ratio SHF calculated in this way is determined as the sensible heat ratio SHFmax. Then, as described above, a straight line having an inclination determined by SHFmax is extended from the target indoor temperature and humidity, and a point where the straight line and the saturation curve intersect is defined as the maximum evaporation temperature Te_max.

FIG. 9 is a diagram showing a control flow in the air conditioning system according to the embodiment of the present invention.
First, the target indoor temperature Ta_tgt and the target indoor humidity RH_tgt are set, and the cooling operation is started (S1). Then, the outside air temperature Ta_o, the outside air humidity RH_o, the room temperature Ta_i, and the room humidity RH_i are detected, and the number N of people in the room is further detected (S2). Subsequently, the air conditioning load (outside air total heat load, outside air sensible heat load, indoor total heat load, indoor sensible heat load, through-flow load) is calculated, and the sensible heat ratio SHFmax is calculated from the above equation (9) (S3). Then, the maximum evaporation temperature Te_max is calculated as described above from the sensible heat ratio SHFmax, the target indoor temperature Ta_tgt [° C.], and the target indoor humidity RH_tgt [%] (S4).

  Then, the target evaporation temperature Te is calculated from the temperature difference ΔT between the room temperature Ta_i [° C.] and the target room temperature Ta_tgt [° C.] by the above equation (1) (S5), and the evaporation temperature in the evaporator becomes the target evaporation temperature Te. Control of the refrigeration cycle (rotational speed control of the compressor 2, opening control of the expansion valve 5, control of the blowers 7 and 8, etc.) is performed so as to become (S6). Then, it is determined whether the outside air temperature / humidity or the number of people in the room has changed or the target temperature / humidity has not been changed (S7). Returning to S3, the load and SHFmax are calculated again, and the maximum evaporation temperature Te_max is updated so that the operation control is performed (S4).

  If none of the outside air temperature humidity, the number of people in the room, and the target temperature / humidity change have been changed or changed in step S7, it is determined whether or not the operation has been completed (S8). And the target evaporation temperature Te is calculated from the temperature difference ΔT according to the above equation (1) (S5). At this time, if the temperature difference ΔT is decreased by the operation of the refrigeration cycle, the target evaporation temperature Te is set to a temperature higher than the current state according to FIG. 5 as described above. If it is determined in step S8 that the operation has been completed, the operation is terminated (S9).

  As described above, according to the present embodiment, the air volume control of the ventilator 11 is performed independently of the air conditioner 1 to always ensure the necessary ventilation amount, so that the indoor air quality is kept good. Can do. Then, after ensuring the necessary ventilation, the target evaporating temperature Te is set to a temperature difference between the indoor temperature Ta_i and the target indoor temperature Ta_tgt within a range below the maximum evaporating temperature Te_max that can achieve the target indoor temperature Ta_tgt and the target indoor humidity RH_tgt. Since the control to change according to ΔT is performed, the indoor temperature and humidity can be brought close to the target value with high efficiency, and both improvement in comfort and high efficiency can be realized.

  In addition, since changes in the outside air temperature humidity, the number of people in the room, and changes in the target temperature and humidity are detected, the maximum evaporation temperature Te_max is updated by recalculating the sensible heat ratio SHFmax according to the changes and changes. In addition, driving while maintaining comfort and energy saving is possible. In addition, during operation, changes in the outside temperature and humidity, the number of people in the room, and changes in the target temperature and humidity are repeatedly checked, so it is possible to quickly respond to these changes and changes.

  In addition, since the occupant number detected by the occupant number detection device 34 is used to calculate the indoor sensible heat load Ql_is and the indoor total heat load Ql_i, it is possible to calculate with high accuracy according to the current situation. As a result, it is possible to contribute to improvement of comfort and high efficiency.

(Deformation process 1)
In the above description, the indoor sensible heat load Ql_is and the total indoor heat load Ql_i are obtained using the number of people in the room detected by the number of people in the room detection device 34, but may be given in advance as constant values. In this case, the occupancy detection device 34 is unnecessary, and in the above equation (9) for calculating the sensible heat ratio SHF, the indoor sensible heat load Ql_is and the indoor total heat load Ql_i are constant values. The control flow in this case is as shown in FIG.

  FIG. 10 differs from FIG. 9 in the processing of step S2a and step S7a, and the other processing is the same as in FIG. That is, detection of the number of people in the room is omitted in step S2a in FIG. 10, and detection of a change in the number of people in the room is omitted in step S7a. Therefore, the indoor load setting device according to claim 1 may set the indoor total heat load Ql_is and the indoor sensible heat load Ql_i using the detection result of the occupant number detection device 34, or set in advance as a constant value. It may be.

  Even if it is set as such a process, the effect similar to the above can be acquired.

(Deformation process 2)
The control flow as shown in FIG. 11 may be performed by correcting the sensible heat ratio SHFmax using the correction coefficient α so as to reliably reach the target indoor temperature and humidity.

  First, the target indoor temperature Ta_tgt and the target indoor humidity RH_tgt are set and the operation is started (S11), and the correction coefficient α is set to 1 which is an initial value (S12). In the same manner as described above, the outside air temperature Ta_o, the outside air humidity RH_o, the room temperature Ta_i, and the room humidity RH_i are detected, and the number N of people in the room is further detected (S13). Subsequently, the air conditioning load (outside air total heat load, outside air sensible heat load, indoor total heat load, indoor sensible heat load, flow through load) is calculated, and the sensible heat ratio SHF is calculated from the above equation (9). A value obtained by multiplying the ratio SHF by the correction coefficient α is defined as a sensible heat ratio SHFmax (S14). Then, the maximum evaporation temperature Te_max is calculated from the sensible heat ratio SHFmax, the target indoor temperature Ta_tgt [° C.], and the target indoor humidity RH_tgt [%] (S15).

  Then, the target evaporation temperature Te is calculated from the temperature difference ΔT between the room temperature Ta_i [° C.] and the target room temperature Ta_tgt [° C.] by the above equation (1) (S16), and the evaporation temperature in the evaporator is equal to the target evaporation temperature Te. Thus, control of the refrigeration cycle (rotational speed control of the compressor 2, opening control of the expansion valve 5, control of the blower, etc.) is performed (S17). Then, it is determined whether the outside air temperature humidity and the number of people in the room have changed or the target temperature and humidity have not been changed (S18). If at least one has been changed or changed, the air conditioning load after the change or the change is changed. Returning to S14, the load and SHFmax are calculated again, and the maximum evaporation temperature Te_max is updated so that the operation control is performed (S15).

  If none of the outside air temperature humidity, the number of people in the room, and the target temperature / humidity change is changed or changed, it is determined whether the temperature difference ΔT is smaller than a predetermined value Tset. If the temperature difference ΔT is equal to or greater than Tset, the room temperature is not yet stable, so the process returns to step S16 and the operation of changing the target evaporation temperature Te according to the temperature difference ΔT is continued. On the other hand, if the temperature difference ΔT is smaller than Tset, it is determined that the room temperature is stable, and the process proceeds to the next step S20. Note that the value of Tset is, for example, 0.5.

  In step S20, it is determined whether the absolute value of the humidity difference between the target indoor humidity RH_tgt and the indoor humidity RH_i is smaller than a predetermined value RHset (eg, “5”). If it is smaller than RHset, it is determined that the humidity has reached the target indoor humidity RH_tgt, and the process returns to step S16. If it is equal to or higher than RHset, the room temperature has reached the target, but the humidity has reached the target. Therefore, the process proceeds to the process of determining the correction coefficient α.

  That is, the indoor humidity RH_i is compared with the target indoor humidity RH_tgt (S21). If the indoor humidity RH_i is smaller than the target indoor humidity RH_tgt, the indoor humidity RH_i is too low. That is, the sensible heat ratio SHFmax calculated in step S14 is smaller than the actual sensible heat ratio. Specifically, for example, in the example of FIG. 7, when the actual sensible heat ratio is 0.7 but is set to 0.6, for example, the evaporation temperature at the sensible heat ratio 0.6 The operation was performed with T1 as the maximum evaporation temperature Te_max. That is, as shown in FIG. 12, the target evaporation temperature Te when the sensible heat ratio is 0.6 is operated at a lower evaporation temperature than when the sensible heat ratio is 0.7, and the dehumidification amount is It will be driven in many states. Therefore, the indoor humidity RH_i is too low.

  In such a case, in order to approach the actual sensible heat ratio, α is corrected by adding α to a predetermined value α1 (S22). Conversely, when the indoor humidity RH_i is equal to or higher than the target indoor humidity RH_tgt, the humidity is not sufficiently lowered, and the sensible heat ratio calculated in step S14 is larger than the actual sensible heat ratio. In order to reduce the heat ratio SHFmax, the value of α is corrected by subtracting a predetermined value α1 (S23). Thereafter, in step S24, it is determined whether or not the operation has been completed. If the operation has not been completed, the process returns to step S16 to detect the outside air temperature and humidity and determine the number of people in the room again. Thus, by setting the correction coefficient α and correcting the sensible heat ratio SHFmax, it becomes possible to reach the target temperature and humidity more reliably. If it is determined in step S24 that the operation has been completed, the operation is terminated (S25).

  Thus, by feeding back the indoor temperature and humidity, it is possible to reach the set temperature and humidity more reliably, and to perform operation while maintaining comfort and energy saving in a wider range. The deformation process 2 can be combined with the deformation process 1, and the indoor sensible heat load Ql_is and the indoor total heat load Ql_i may be given as constant values in advance.

  Moreover, in the said embodiment, although indoor temperature Ta_i was made into the detected value of the indoor temperature detection apparatus 23 of the ventilation apparatus 11, it is good also as detection value Ta_r of the indoor temperature detection apparatus 32. FIG. Since there are a plurality of room temperature detection devices 32 in the room 101, the detection values of any one of the room temperature detection devices 32 may be used, or all the detection values may be averaged and used.

  Moreover, the structure of the ventilator 11 is not restricted to the structure shown in FIG. 2, It is good also as a structure shown in the following FIG. 13, FIG.

FIGS. 13A and 13B are diagrams showing another configuration example 1 of the ventilation device of FIG. 1, in which FIG. 13A is a front view and FIG. 13B is a cross-sectional view.
As shown in FIG. 13, it is good also as a structure further provided in the ventilation apparatus 11 with the 1st heat exchanger 41 which performs heat exchange with indoor air and outdoor air. In this case, when calculating the outside air total heat load Ql_o and the outside air sensible heat load Ql_os, the detection value of the outside air temperature detection device 21 and the detection value of the outside air humidity detection device 22 cannot be used as they are. Therefore, in addition to the detection value of the outside air temperature detection device 21 and the detection value of the outside air humidity detection device 22, the detection value of the indoor temperature detection device 23, the detection value of the indoor humidity detection device 24, and the first heat exchanger 41 is used to predict the temperature and humidity of the air supplied to the room, and the predicted temperature and humidity are used as the outside air temperature and humidity to calculate the outside air total heat load Ql_o and the outside air sensible heat load Ql_os.

14A and 14B are diagrams showing another configuration example 2 of the ventilation device of FIG. 1, in which FIG. 14A is a front view and FIG. 14B is a cross-sectional view.
As shown in FIG. 14, in the ventilation apparatus 11, the 1st heat exchanger 41 which performs heat exchange with indoor air and outdoor air, and the 2nd heat exchanger 42 which performs heat exchange with a refrigerant | coolant and air, It is good also as a structure further provided. The second heat exchanger 42 is installed in the air passage after the outdoor air passes through the first heat exchanger 41, and performs heat exchange between the outdoor air and the refrigerant after passing through the first heat exchanger 41. Do. Specifically, the 2nd heat exchanger 42 can be set as the structure connected through the branch pipe from the refrigerating cycle of the air conditioning apparatus 1. FIG.

  Even when the second heat exchanger 42 is provided in addition to the first heat exchanger 41 as described above, when the outside air total heat load Ql_o and the outside air sensible heat load Ql_os are calculated, the detection by the outside air temperature detection device 21 is performed. The value and the detection value of the outside air humidity detection device 22 cannot be used as they are. Therefore, in addition to the detection value of the outdoor air temperature detection device 21 and the detection value of the outdoor air humidity detection device 22, the detection value of the indoor temperature detection device 23, the detection value of the indoor humidity detection device 24, and the first heat Using the characteristics of the exchanger 41 and the characteristics of the second heat exchanger 42, the temperature and humidity of the air supplied to the room are predicted, and the predicted temperature and humidity are used as the outside air temperature and humidity, so that the outside air total heat load Ql_o and outside air sensible heat load Ql_os are calculated.

  DESCRIPTION OF SYMBOLS 1 Air conditioning apparatus, 2 compressor, 3 way valve, 4 outdoor heat exchanger, 5 expansion valve, 6 indoor heat exchanger, 7 outdoor heat exchanger blower, 8 indoor heat exchanger blower, 9 indoor unit, 10 outdoor unit , 11 Ventilation device, 12 Transmission line, 20 Blower, 21 Outside air temperature detection device, 22 Outside air humidity detection device, 23 Indoor temperature detection device, 24 Indoor humidity detection device, 31 Evaporation temperature detection device, 32 Indoor temperature detection device, 33 input Part 34 occupancy detection device 41 first heat exchanger 42 second heat exchanger 100 air conditioning system 101 indoor 102 centralized controller.

Claims (8)

A refrigeration cycle in which a compressor, an outdoor heat exchanger, an expansion valve, and an indoor heat exchanger are sequentially connected by piping to enable cooling operation;
A ventilation device that controls the air volume so as to ensure the necessary ventilation volume according to the indoor environment, ventilates the room air and the outdoor air, and performs ventilation.
An indoor temperature detecting device for detecting the indoor temperature;
An indoor humidity detection device for detecting indoor humidity;
An outside air temperature detecting device for detecting the outside air temperature;
An outside air humidity detecting device for detecting outside air humidity;
A temperature and humidity setting device for setting a target indoor temperature and humidity;
An indoor load setting device for setting the indoor total heat load and the indoor sensible heat load;
As the temperature difference between the room temperature detected by the room temperature detection device and the target room temperature set in the temperature / humidity setting device becomes smaller, control is performed to increase the target evaporation temperature within a predetermined evaporation temperature range. A control device,
The control device includes:
From the detected values of the indoor temperature detecting device, the indoor humidity detecting device, the outside air temperature detecting device and the outside air humidity detecting device, and the ventilation air volume of the ventilator, the outside air total heat load and the outside air sensible heat load are obtained. ,
Obtaining the through load from the detection value of the indoor temperature detection device, the detection value of the outside air temperature detection device, the surface area of the wall of the building, and the heat flow rate of the wall,
Air conditioning sensible heat load in the air conditioning total heat load from the outside air total heat load, the outside air sensible heat load, the once-through load, the indoor total heat load and the indoor sensible heat load set by the indoor load setting device Calculate the sensible heat ratio, which is the ratio of
Determining the maximum value of the predetermined evaporation temperature range based on the calculated sensible heat ratio and the target indoor temperature and humidity set by the temperature and humidity setting device ;
When the difference between the room temperature and the target room temperature is smaller than a predetermined value, the sensible heat is determined according to the difference between the detected value detected by the room humidity detection device and the target room humidity. An air conditioning system characterized by correcting the ratio . When the indoor humidity is lower than the target indoor humidity and the indoor humidity is lower, the sensible heat ratio is corrected to be increased, and when the indoor humidity is higher, the sensible heat ratio is decreased. The air conditioning system according to claim 1 , wherein the air conditioning system corrects the direction. The controller recalculates the sensible heat ratio and updates the maximum value of the predetermined evaporation temperature range when any of the outside air temperature, the outside air humidity, the target room temperature, or the target room humidity changes during operation. The air conditioning system according to claim 1 or 2 , characterized by the above. The indoor load setting device includes a occupant number detecting device for detecting the occupant number in the room, and the total indoor heat load and the sensible heat in the room in consideration of the occupant number detected by the occupant number detecting device. air conditioning system according to any one of claims 1 to 3, characterized in that setting the load. The controller recalculates the sensible heat ratio and updates the maximum value of the predetermined evaporation temperature range when the occupant number detected by the occupant number detector changes during operation. The air conditioning system according to claim 4 . The ventilator includes a first heat exchanger that performs heat exchange between outdoor air and room air,
Wherein the controller, upon determining the outside air total heat load and the outside air sensible heat load, to any one of claims 1 to 5, characterized in that considering the characteristics of the first heat exchanger The air conditioning system described. The ventilator further includes a second heat exchanger that exchanges heat between outdoor air after passing through the first heat exchanger and refrigerant passing through the refrigeration cycle,
7. The air conditioning system according to claim 6 , wherein the control device further takes into account the characteristics of the second heat exchanger when determining the outside heat total heat load and the outside air sensible heat load. 2. The four-way valve for switching the flow path so that the indoor heat exchanger becomes an evaporator during cooling operation and the outdoor heat exchanger becomes a condenser, and vice versa during heating operation. Item 8. The air conditioning system according to any one of Items 7 .

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