JP2002022245A - Air conditioning system - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an air conditioning system which improves an air conditioning efficiency by linking control of an air conditioner for performing indoor cooling and a dehumidifier for performing indoor dehumidification. SOLUTION: The air conditioning system comprises an air conditioner 2 and a dehumidifier 4. In the system, the outside air conditions and the inside air conditions are detected by a sensor. Calculation is made, in the air conditions, in respect of heat pump evaporating temperature Te, exhaust heat temperature Tt and coefficient of performance COP. Further, dehumidifying capacity Qd with respect to the temperature Tt is obtained in the dehumidifier 4. Subsequently, latent heat load and sensible heat load to be treated by the air conditioner 2 are obtained on the basis of the capacity Qd. Thus, operation is performed at the temperature Te and the temperature Tt which can cope with the loads and exert the maximum coefficient of performance COP.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an air-conditioning system capable of efficiently performing indoor cooling and dehumidifying operation.

[0002]

2. Description of the Related Art An air conditioning system using both an air conditioner for performing indoor cooling operation using an evaporator of a heat pump and a dehumidifier for performing indoor dehumidification is known. In this conventional air conditioning system, energy is controlled so that each of them performs indoor cooling and indoor dehumidification independently.

[0003]

In recent years, various attempts have been made to reduce air conditioning energy. The present invention and the like have focused on the point that further energy savings can be achieved by controlling the air conditioner and the dehumidifier in conjunction with each other, and have conducted various studies, and have completed the present invention.

[0004] That is, an object of the present invention is to provide an air conditioning system capable of improving the efficiency of an air conditioning system by linking and controlling an air conditioner for performing indoor cooling and a dehumidifier for performing indoor dehumidification.

[0005]

Accordingly, an air conditioning system according to a first aspect of the present invention provides an air conditioner 2 for performing indoor cooling operation using an evaporator of a heat pump, and a dehumidifying unit for performing indoor dehumidification using exhaust heat of the heat pump. In the air-conditioning system including the air conditioner 4, the maximum coefficient of performance CO according to the sensible heat load and the latent heat load
It is characterized in that the air conditioner 2 and the dehumidifier 4 are operated under the operating conditions where P can be obtained.

In the air conditioning system according to the first aspect of the present invention, an operation that can obtain the best coefficient of performance COP is considered in consideration of the latent heat load borne by the dehumidifier 4 and the latent heat / sensible heat load borne by the air conditioner 2. Since the operation of the air conditioner 2 and the dehumidifier 4 is performed under the condition, it is possible to perform the operation with high energy efficiency.

[0007] The air conditioning system according to claim 2 is based on claim 1.
, The outside air condition and the indoor condition are detected by sensors, and the heat pump evaporation temperature Te and the exhaust heat temperature Tt in this air state are detected.
In addition to calculating the relationship between the coefficient of performance COP and the dehumidifier 4, the dehumidifying capacity Qd with respect to the exhaust heat temperature Tt is determined. Next, the latent heat and the sensible heat load to be processed by the air conditioner 2 are determined based on the dehumidifying capacity Qd. The operation is performed at the heat pump evaporation temperature Te and the exhaust heat temperature Tt that can respond to this load and obtain the maximum coefficient of performance COP.

FIG. 1 shows the outline of the air conditioning system according to the second aspect. As shown in FIG.
, Sensors (not shown) detect outside air conditions (temperature, humidity, etc.) and indoor conditions (temperature, humidity, etc.), and grasp indoor set temperature and humidity. Next, step S1
In step 1, the required sensible heat / latent heat treatment capacity is calculated. In step S12, the heat pump evaporation temperature Te, the exhaust heat temperature Tt, and the coefficient of performance COP in this air state are determined.
Calculate the relationship with Next, in step S13,
The exhaust heat temperature Tt and the dehumidification (latent heat) capability of the dehumidifier 4 are calculated. In step S14, the evaporating temperature Te and the exhaust heat temperature Tt at which the system COP is maximized are calculated, and the set values of the control means of the heat pump to obtain the evaporating temperature Te and the exhaust heat temperature Tt are calculated. (Step S1
5) In step S16, the set value of the control means of the heat pump is set to be the value obtained by the above calculation, and the same control is repeated thereafter. By performing such control, in an air conditioning system including the air conditioner 2 for indoor cooling and the dehumidifier 4 for indoor dehumidification, it is possible to operate in a state where the highest COP is obtained. It can be improved.

In the air conditioning system according to a third aspect of the present invention, the exhaust heat of the heat pump is the condensing heat of an evaporative compression heat pump, the condensing heat of an engine driven heat pump, the condensing heat of an absorption heat pump, or the engine driven. It is characterized by exhaust heat of the engine of the heat pump or exhaust heat of the absorber of the absorption refrigerator. Thus, the invention of claim 2 is applicable to many types of heat pumps. Here, the exhaust heat temperature Tt in claim 2 includes the temperature of the gas discharged from the compressor 5 in the evaporative compression heat pump, the engine driven heat pump or the absorption heat pump, the condensation temperature of the condenser 10, and the like. Please note.

[0010]

Next, specific embodiments of the air conditioning system of the present invention will be described in detail with reference to the drawings. FIG. 2 shows a refrigerant circuit diagram of a heat pump system as an air conditioning system according to an embodiment of the present invention.

In FIG. 2, 1 is an outdoor unit, 2 is an air conditioner for performing indoor air conditioning, and 4 is a dehumidifier for performing indoor dehumidification. The outdoor unit 1 includes a compressor 5, a four-way switching valve 9, an outdoor heat exchanger 6, an outdoor fan 7, and an electric expansion valve 8. Further, the air conditioner 2 has an indoor heat exchanger 11 and an indoor fan 13. The dehumidifier 4 includes a heat exchanger (hereinafter, referred to as a heat exchanger) provided downstream of the compressor 5.
For convenience, referred to as a condenser) 10, an adsorption rotor 17,
And a sensible heat rotor 18.

In the above air conditioning system, the discharge side and the suction side of the compressor 5 are connected to the primary port of the four-way switching valve 9, and the secondary port of the four-way switching valve 9 is connected to the outdoor heat exchanger. 6, the electric expansion valve 8, and the indoor heat exchanger 11 are connected in order to form a refrigerant circuit. On the discharge side of the compressor 5, an electromagnetic on-off valve 30 is interposed at a position in front of the four-way switching valve 9. It is connected to the inlet of the condenser 10 of the dehumidifier 4. The outlet of the condenser 10 is connected to the electromagnetic on-off valve 30 by a bypass pipe 40.
And the four-way switching valve 9. In this case, the air conditioner 2 and the dehumidifier 4 are arranged in the same room.

In the air conditioning system, when the electromagnetic on-off valve 30 is open, the refrigerant discharged from the compressor 5 is condensed in the outdoor heat exchanger 6 and evaporated in the indoor heat exchanger 11 to perform a cooling operation. . When the electromagnetic on-off valve 30 is open, the refrigerant discharged from the compressor 5 is
After a certain degree of condensation in the condenser 10 of the dehumidifier 4, it is completely condensed in the outdoor heat exchanger 6 and evaporated in the indoor heat exchanger 11, so that the indoor cooling operation and the indoor dehumidification operation are performed in parallel. Do it. Note that the heating operation can be performed by condensing the refrigerant discharged from the compressor 5 in the indoor heat exchanger 11 and evaporating the refrigerant in the outdoor heat exchanger 6.

Next, the structure of the dehumidifier 4 will be described. As shown in FIG. 2, the dehumidifier 4 has a relatively flat rectangular parallelepiped casing 31.
Of the pair of side portions 31a and 31b opposed to each other in the longitudinal direction, one side portion 31a has an indoor-side outlet 36 that communicates with the room.
And an indoor-side suction port 37 are formed, and an outdoor-side outlet 38 and an outdoor-side suction port 39 are formed in the other side 31b. The inside of the casing 31 is divided into a dehumidifying passage 32 and a regeneration passage 33 by a partition plate 34 extending in the longitudinal direction, and external air sucked from the outdoor-side suction port 39 passes through the dehumidifying passage 32 to be connected to the indoor side. While being supplied from the outlet 36 into the room, the indoor side suction port 37
The internal air sucked from the inside is exhausted to the outside from the chamber side outlet 38 through the regeneration passage 33. In the installed state, the disk-shaped suction rotor 17 rotating around the horizontal axis is connected to the dehumidifying passage 32 and the regeneration passage 3 by the end surfaces thereof.
3 and so on. Absorption rotor 17
For example, an adsorbent such as silica gel, zeolite, or alumina is formed into a honeycomb shape or a porous granule, and is configured to adsorb moisture from flowing air and release moisture to heated air. I have. Further, the condenser 10 is provided as a heating means on the upstream side of the adsorption rotor 17 in the regeneration passage 33, and in the installed state, a disc-shaped sensible heat rotor 18 rotating around a horizontal axis is provided. 3
2 and a portion downstream of the suction rotor 17 and the regeneration passage 3.
3 and an upstream portion of the condenser 10.

Next, an air flow path in the dehumidifier 4 will be described. First, the outside air OA flowing from the outdoor suction port 39 of the dehumidifying passage 32 is dehumidified by absorbing moisture by the suction rotor 17, and
The temperature is increased by the heat of adsorption. Then, the dehumidified air whose temperature has increased is deprived of heat by the sensible heat rotor 18 to have an appropriate temperature, and the dehumidified air SA is supplied from the indoor side outlet 36 toward the room. On the other hand, the regeneration passage 3
The indoor air RA flowing from the third indoor-side suction port 37 is preheated by the sensible heat rotor 18 and further heated by the condenser 10. Then, moisture is released from the adsorption rotor 17 by the heated air, the adsorption rotor 17 is regenerated, and the regenerated air EA containing the moisture is exhausted from the outdoor outlet 38 to the outside.

The feature of this embodiment lies in the cooperative control when the air conditioner 2 arranged in the same room as the air conditioner 2 performs the cooling operation while the dehumidifier 4 performs the dehumidifying operation. explain. That is, the dehumidifying function is not only provided by the dehumidifier 4 but also provided by the indoor unit 2, and the COP of the refrigerator changes depending on the ratio of the dehumidifying ability of both of them. Therefore, both capacities are controlled so that the operation state has the highest COP. First, FIG. 3A shows the discharge gas temperature (exhaust heat temperature) Tt of the compressor 5 and the CO2 of the refrigerator.
6 is a graph showing a relationship with P (coefficient of performance), and shows the relationship between the two for each evaporation temperature Te. As shown in the figure, if the evaporation temperature Te is constant, the COP of the refrigerator becomes higher as the discharge gas temperature (exhaust heat temperature) Tt of the compressor 5 increases.
(Coefficient of performance) decreases. If the discharge gas temperature (exhaust heat temperature) Tt of the compressor 5 is constant, the COP (coefficient of performance) of the refrigerator decreases as the evaporation temperature Te decreases. On the other hand, FIG. 3B is a graph showing the relationship between the discharge gas temperature (exhaust heat temperature) Tt of the compressor 5 and the dehumidifying capacity Qd of the dehumidifier 4. When the discharge gas temperature Tt of the compressor 5 rises,
The dehumidifying capacity Qd of the dehumidifier 4 tends to gradually increase.
However, when the discharge gas temperature Tt of the compressor 5 rises to some extent, the dehumidifying capacity Qd of the dehumidifier 4 becomes saturated, and a slight rise is observed.

Now, assuming that the dehumidifying operation is performed at a discharge gas temperature of 70 ° C. and the dehumidifying capacity at that time is Qd70, the remaining dehumidifying load and cooling load obtained by subtracting the dehumidifying capacity Qd70 are required for the air conditioner 2. Will be. Then, the required evaporation temperature Te = 10 ° C. in the indoor heat exchanger 11 is determined according to those loads. At this time, the coefficient of performance COP70 of the refrigerator is obtained from the graph shown in FIG. 3A from the temperature Tt = 70 ° C. of the gas discharged from the compressor 5 and the temperature Te = 10 ° C. from the compressor 5 as described above.

Next, a state in which the discharge gas temperature Tt is reduced to 60 ° C. will be considered. In this state, the dehumidifying capacity Qd60 and the evaporation temperature Te = 4 ° C. are respectively obtained by the same procedure as described above, and the temperature Tt of the discharge gas from the compressor 5 is obtained.
From 60 ° C. and the evaporation temperature Te = 4 ° C., the coefficient of performance COP60 of the refrigerator is obtained from the graph shown in FIG. In this case, since the dehumidifying capacity Qd60 is greatly reduced as compared with the case where the discharge gas temperature Tt is 70 ° C., the dehumidifying capacity required for the indoor unit 2 is increased, and the required evaporation temperature Te is increased.
Is also greatly reduced. As a result, the coefficient of performance COP60 of the refrigerator decreases due to the decrease in the evaporation temperature Te. On the other hand, consider a state in which the discharge gas temperature Tt is raised to 80 ° C. In this state, the dehumidifying capacity Qd80 and the evaporation temperature Te = 12 ° C. are respectively obtained by the same procedure as described above, and from the discharge gas temperature Tt = 80 ° C. from the compressor 5 and the evaporation temperature Te = 12 ° C., The coefficient of performance COP80 of the refrigerator is obtained from the graph shown in FIG. In this case, as compared with the case where the discharge gas temperature Tt is 70 ° C., the dehumidifying capacity Qd80 hardly increases even though the discharge gas temperature Tt is increased. The required dehumidification capacity is hardly reduced. Therefore, the evaporation temperature Te of the indoor heat exchanger 11 still needs to be maintained at a low temperature. Since the evaporating temperature Te needs to be maintained at a low temperature, the coefficient of performance COP80 of the refrigerator decreases. Even if the discharge gas temperature Tt is further raised from 80 ° C., since the dehumidifying capacity of the dehumidifier 4 is saturated, the indoor heat exchanger 11 has the same evaporation temperature Te as before. Therefore, the COP of the refrigerator gradually decreases according to the line of the evaporation temperature Te = 12 ° C. as the discharge gas temperature Tt increases.

As described above, the COP of the vapor compression cycle
And the dehumidifying capacity (desiccant capacity) are in a trade-off relationship, and it is clear that a peak of the system COP exists when the calculation is performed with the same system capacity while changing the discharge gas temperature. This is because as the discharge gas temperature in the vapor compression cycle increases, the dehumidifying capacity increases, and the amount of latent heat treatment in the vapor compression cycle decreases, making it possible to operate at a high COP with an increased evaporation temperature. If the temperature of the discharge gas is further increased, the COP of the vapor compression cycle will be significantly reduced, and the dehumidifying capacity will be saturated (a plateau state). As a result, the COP of the system will be reduced.

The above-described calculation of the COP is performed for each further subdivided discharge gas temperature Tt, and the highest C
The operation of the air-conditioning system is performed at the discharge gas temperature Tt at which the OP can be obtained.
Is shown in First, in step S20, a sensor (not shown) detects an outside air condition (temperature and humidity) and an indoor condition (temperature and humidity), and grasps a set indoor temperature and humidity. Next, in step S21, the required sensible heat / latent heat (dehumidification) processing capacity is calculated. In step S22, the evaporating temperature T of the refrigerator in this air state is determined.
e, discharge gas temperature Tt (or condensation temperature) and coefficient of performance CO
The relationship with P is calculated (FIG. 3A). Next, in step S23, the discharge gas temperature Tt in the dehumidifier 4
(Or condensation temperature) and dehumidification (latent heat) capacity are calculated (Fig. 3
(B)). In step S24, the evaporating temperature Te and the discharge gas temperature Tt (or condensing temperature) at which the system COP becomes maximum are calculated, and the evaporating temperature Te and the discharging gas temperature Tt (or condensing temperature) are obtained. The rotation speed of the compressor 5, the opening degree of the electric expansion valve 8, the airflow of the indoor fan 13, and the like are calculated (step S25). In step S26, the rotation speed of the compressor 5, the opening degree of the electric expansion valve 8, the indoor fan 13 is set to a value obtained by the above calculation, and the same control is repeated thereafter.

By performing the above-described control, an air-conditioning system including an air conditioner 2 for indoor cooling and a dehumidifier 4 for indoor dehumidification can be operated in a state where the highest COP is obtained. Thus, it is possible to improve system efficiency.

FIG. 5 shows another embodiment of a vapor compression heat pump capable of performing the above control.
This includes a plurality of air conditioners 2, 3 for cooling and heating a plurality of rooms,
This is an example of a multi-type heat pump system including a dehumidifier 4 for performing indoor dehumidification. In FIG. 5, 1 is an outdoor unit, 2
Denotes a first air conditioner for performing indoor air conditioning, 3 denotes a second air conditioner for performing indoor air conditioning, and 4 denotes a dehumidifier for performing indoor dehumidification. The outdoor unit 1 includes a compressor 5, an outdoor heat exchanger 6, an outdoor fan 7, and a main electric expansion valve 8. Each of the air conditioners 2 and 3 includes an indoor heat exchanger 1.
1, 12; indoor fans 13, 14;
5 and 16. The dehumidifier 4 has a heat exchanger (hereinafter, referred to as a condenser for convenience) 10 provided downstream of the compressor 5, an adsorption rotor 17, and a sensible heat rotor 18. Since the structure and the operation state of the dehumidifier 4 are the same as those described in FIG. 2, the same reference numerals are given to the same functional parts, and the description thereof will be omitted. In FIG. 5, reference numerals 21 and 22 denote refrigerant switching units.

Next, an operation state of the multi-type heat pump system (air conditioning system) will be described. First,
The flow of the refrigerant when performing the heating operation in each of the air conditioners 2 and 3 will be described. At this time, each of the refrigerant switching units 21, 2
2 is a state in which each of the indoor heat exchangers 11 and 12 communicates with a gas pipe 20 connected to the discharge side of the compressor 5. Further, the first on-off valve 23 between the discharge side of the compressor 5 and the outdoor heat exchanger 6 is closed, and the second on-off valve 24 between the suction side of the compressor 5 and the outdoor heat exchanger 6 is opened. The outdoor heat exchanger 6 is connected to the suction side of the compressor 5 in advance. The refrigerant discharged from the compressor 5 is condensed in the indoor heat exchangers 11 and 12, while the refrigerant is evaporated in the outdoor heat exchanger 6 and returned to the compressor 5 while controlling the main electric expansion valve 8. Perform heating operation. Next, the flow of the refrigerant when performing the cooling operation in each of the air conditioners 2 and 3 will be described. At this time, each of the refrigerant switching units 21 and 22 connects each of the indoor heat exchangers 11 and 12 to the compressor 5.
In communication with the suction side. The compressor 5
The first on-off valve 23 between the discharge side of the compressor and the outdoor heat exchanger 6 is opened, and the second on-off valve 24 between the suction side of the compressor 5 and the outdoor heat exchanger 6 is closed to open the outdoor heat exchanger. 6 is communicated with the discharge side of the compressor 5. Then, while the refrigerant discharged from the compressor 5 is condensed in the outdoor heat exchanger 6, each indoor heat exchanger 11, while controlling the electric expansion valves 15, 16 on the air conditioner side,
A cooling operation is performed by evaporating the refrigerant at 12 and returning it to the compressor 5.

The refrigerant discharged from the compressor 5 is always supplied to the condenser 10 of the dehumidifier 4 through the gas pipe 20 as long as the dehumidifier on-off valve 19 is open. The condensed refrigerant evaporates in each of the air conditioners 2 and 3 when the air conditioners 2 and 3 perform the cooling operation, and evaporates in each of the air conditioners 2 and 3 when the air conditioners 2 and 3 perform the heating operation. Then, the condensed refrigerant flowing out of each of the air conditioners 2 and 3 evaporates in the outdoor heat exchanger 6.

The flow of the refrigerant when the first air conditioner 2 performs the cooling operation and the second air conditioner 3 performs the heating operation will be described. First, each of the refrigerant switching units 21 and 22 communicates the first indoor heat exchanger 11 with the suction side of the compressor 5 and the second indoor heat exchanger 12 with the discharge side of the compressor 5 as shown in the figure. State. At this time, when the dehumidifier on-off valve 19 is closed and the dehumidifier 4 is not used, the first on-off valve 23 between the discharge side of the compressor 5 and the outdoor heat exchanger 6 is closed,
The second on-off valve 24 between the suction side of the compressor 5 and the outdoor heat exchanger 6 is closed to shut off the communication between the outdoor heat exchanger 6 and the compressor 5. The refrigerant discharged from the compressor 5 is supplied to the second
The first air conditioner 2 is condensed in the indoor heat exchanger 12 while being evaporated in the first indoor heat exchanger 11 and returned to the compressor 5 while controlling the electric expansion valve 15 on the first air conditioner side.
Performs the cooling operation, and performs the heating operation with the second air conditioner 3. On the other hand, when the dehumidifier on-off valve 19 is open and the dehumidifier 4 is in use, the first on-off valve 23 between the discharge side of the compressor 5 and the outdoor heat exchanger 6 is closed, and the compressor 5 Suction side and outdoor heat exchanger 6
The second open / close valve 24 is opened to connect the outdoor heat exchanger 6 to the suction side of the compressor 5. The refrigerant discharged from the compressor 5 is condensed in the condenser 10 and the second indoor heat exchanger 12, while controlling the main electric expansion valve 8 and the electric expansion valve 15 on the first air conditioner side to exchange outdoor heat. The cooling operation is performed by the first air conditioner 2 and the heating operation is performed by the second air conditioner 3 by evaporating in the heat exchanger 6 and the first indoor heat exchanger 11 and returning the vapor to the compressor 5.

According to the above air conditioning system, the dehumidifier 4 and the first or second air conditioners 2 and 3 are arranged in the same room, so that the dehumidifying operation can be performed while performing the cooling and heating operation. In such a case, the same control as the control described with reference to FIGS. 3 and 4 can be performed.

In the above description, an example is shown in which the exhaust heat of the condenser 10 of the vapor compression heat pump is used, but the heat of condensation or exhaust heat of the engine driven heat pump or the heat of condensation of the absorption heat pump is used. In any of the absorber exhaust heat, there is a trade-off relationship between the exhaust heat temperature and the cooling COP, and there is an optimum point for the dehumidifying operation and the air conditioning operation based on the same principle as described above. Hereinafter, examples of application to an engine-driven heat pump and an absorption heat pump will be described.

FIG. 6 shows an embodiment in which the exhaust heat of the engine in the engine driven heat pump is used. This is because, as shown in the drawing, the exhaust heat of the engine 41 that drives the compressor 5 is supplied to the pipes 42 and 43 through the same dehumidifier
Is supplied to the condenser 10 for dehumidification. This dehumidifier 4 is the same as that described in FIG. 2, the refrigerant circuit in the air conditioner 2 is substantially the same as that shown in FIG. 2, and the compressor 5, the four-way switching valve 9, the outdoor heat exchanger 6, the electric expansion valve 8, the indoor heat exchanger 11
have. In addition, 7 is an outdoor fan and 13 is an indoor fan. FIG. 7 shows a control flowchart in this case. First, in step S30, the outside air condition (temperature and humidity) and the indoor condition (temperature and humidity) are detected by a sensor (not shown), and the indoor set temperature and humidity are grasped. Next, in step S31, the required sensible heat / latent heat (dehumidification) processing capacity is calculated. In step S32, the relationship between the refrigerator evaporation temperature Te in this air state, the engine exhaust heat temperature (or condensation temperature), and the coefficient of performance COP is calculated. Next, in step S33, the engine exhaust heat temperature (or condensation temperature) and the dehumidification (latent heat) capability of the dehumidifier 4 are calculated. In step S34, the evaporating temperature Te and the engine exhaust heat temperature (or condensing temperature) at which the system COP is maximized are calculated.
The number of revolutions of the engine 41, the opening degree of the electric expansion valve 8, the air volume of the indoor fan 13, and the like are calculated so as to obtain e and the engine exhaust heat temperature (or condensation temperature) (step S35). The rotation speed of 41, the opening degree of the electric expansion valve 8, the airflow of the indoor fan 13, and the like are set to values obtained by the above calculation, and the same control is repeated thereafter.

By performing the above control, the engine-driven heat pump system including the air conditioner 2 for indoor cooling and the dehumidifier 4 for indoor dehumidification can be operated in a state where the highest COP is obtained. Therefore, the system efficiency can be improved.

FIG. 8 shows an embodiment in which the exhaust heat of the absorber is used in the absorption refrigerator 44, and FIG. 9 shows a case where the local heat source 45 is used in the absorption refrigerator. FIG. In each figure, 4
Denotes a dehumidifier, and 10 denotes a condenser, respectively. This dehumidifier 4 is substantially the same as that shown in FIG.
FIG. 10 shows a control flowchart in this case.
First, in step S40, a sensor (not shown) detects an outside air condition (temperature and humidity) and an indoor condition (temperature and humidity) and grasps an indoor set temperature and humidity. Next, in step S41, the required sensible heat / latent heat (dehumidification) processing capacity is calculated. In step S32, the relationship between the evaporator temperature Te in this air state, the absorber temperature (or condensation temperature), and the coefficient of performance COP is calculated. Next, in step S43, the absorber temperature (or condensation temperature) and the dehumidification (latent heat) capability of the dehumidifier 4 are calculated. In step S44, the evaporating temperature Te and the absorber temperature (or condensing temperature) at which the system COP is maximized are calculated, and the generator that can obtain the evaporating temperature Te and the absorber temperature (or condensing temperature) is obtained. The heating amount, the opening degree of the electric expansion valve, the air volume of the indoor fan, etc. are calculated (step S45),
In step S46, the heating amount of the generator, the opening degree of the electric expansion valve, the air volume of the indoor fan, and the like are set to the values obtained by the above calculation, and the same control is repeated thereafter.

By performing the above control, the absorption chiller including the air conditioner for indoor cooling and the dehumidifier 4 for indoor dehumidification can be operated in a state where the highest COP is obtained. Therefore, it is possible to improve system efficiency.

Although the embodiment of the air conditioning system according to the present invention has been described above, the present invention is not limited to the above-described embodiment, and can be implemented with various modifications. That is, in the above embodiment, the dehumidifier 4 uses the suction rotor 17, but the dehumidifier 4 may be configured using a cooling and suction element. In the dehumidifier 4 in each of the above embodiments, the heat exchanger provided on the downstream side of the compressor is referred to as a condenser.
It should be noted that the main purpose is not the condensing action for liquefying the gas refrigerant, but the main purpose is to utilize the sensible heat of the refrigerant discharged from the compressor and to heat the air by this sensible heat.

[0033]

As described above, in the air conditioning system according to the first aspect, the best coefficient of performance C is obtained in consideration of the latent heat load borne by the dehumidifier and the latent heat / sensible heat load borne by the air conditioner.
Since the operation of the air conditioner and the dehumidifier is performed under the operating condition that can obtain the OP, it is possible to perform the operation with high energy efficiency.

Further, in the air conditioning system according to the second aspect, in an air conditioning system including an air conditioner for indoor cooling and a dehumidifier, it is possible to operate in a state where the highest COP is obtained, thereby improving system efficiency. It becomes possible.

Further, the air conditioning system of claim 2 is applicable to many types of heat pumps as in claim 3.

[Brief description of the drawings]

FIG. 1 is a flowchart for explaining the outline of claim 2 of the present invention.

FIG. 2 is a refrigerant circuit diagram illustrating the air conditioning system according to the first embodiment of the present invention.

FIG. 3 is a graph for explaining a control method of the air-conditioning system according to the embodiment; FIG.
7 is a graph showing the relationship between P and P, and (b) is a graph showing the relationship between the discharge gas temperature and the dehumidifying capacity.

FIG. 4 is a flowchart for explaining a control method in the embodiment.

FIG. 5 is a refrigerant circuit diagram illustrating an air conditioning system according to a second embodiment of the present invention.

FIG. 6 is a refrigerant circuit diagram illustrating an air conditioning system according to a third embodiment of the present invention.

FIG. 7 is a flowchart for explaining a control method in the embodiment.

FIG. 8 is a refrigerant circuit diagram illustrating an air conditioning system according to a fourth embodiment of the present invention.

FIG. 9 is a refrigerant circuit diagram illustrating an air conditioning system according to a fifth embodiment of the present invention.

FIG. 10 is a flowchart for explaining a control method in each of the embodiments.

[Explanation of symbols]

 2 air conditioner 4 dehumidifier 5 compressor 10 condenser

 ──────────────────────────────────────────────────続 き Continued on the front page F term (reference) 3L053 BC03 BC09 3L060 AA03 CC01 CC02 CC03 CC04 DD02 DD08 EE01 EE21 EE25 EE45 4D052 AA08 CB02 DA03 DB01 FA06 GA01 GB06 HA01 HA02 HA03 HB02

Claims (3)

[Claims] An air conditioning system comprising: an air conditioner (2) for performing indoor cooling operation using an evaporator of a heat pump; and a dehumidifier (4) for performing indoor dehumidification by using exhaust heat of the heat pump. The air conditioner (2) under operating conditions in which the maximum coefficient of performance (COP) is obtained according to the sensible heat load and the latent heat load
And an operation of the dehumidifier (4). 2. An outside air condition and an indoor condition are detected by a sensor.
In this air state, the relationship between the heat pump evaporation temperature (Te), the exhaust heat temperature (Tt), and the coefficient of performance (COP) is calculated, and the dehumidifier (4) further dehumidifies the exhaust heat temperature (Tt) with respect to the exhaust heat temperature (Tt). And then the dehumidifying capacity (Q
The latent heat and the sensible heat load to be processed by the air conditioner (2) are obtained on the premise of d), and the heat pump evaporation temperature (T) at which the load can be satisfied and the maximum coefficient of performance (COP) is obtained.
2. The air conditioning system according to claim 1, wherein the operation is performed at e) and the exhaust heat temperature (Tt). 3. The exhaust heat of the heat pump is condensed heat of an evaporative compression refrigerator, condensed heat of an engine driven heat pump, condensed heat of an absorption refrigerator, engine exhaust heat of an engine driven heat pump, or absorption refrigeration. 3. The air conditioning system according to claim 2, wherein the heat is exhaust heat from the absorber of the machine.