Air conditioning system

Abstract

This air conditioning system provides energy-saving and comfortable living at all times by using reverse cycle defrosting during heating mode operation in cold regions or during severe winters to completely and quickly melt frost and ice, improving heating capacity and energy efficiency after reverse cycle defrosting, while minimizing the drop in room temperature and the feeling of cold air during reverse cycle defrosting. [Solution] The indoor unit 17 has an indoor heat exchanger 91, an indoor fan 90, and a louver 94. When the air conditioner A is in heating operation and in reverse cycle defrosting operation, which involves flowing refrigerant in a cooling cycle to defrost the outdoor heat exchanger 99, the indoor fan 90 is operated at maximum airflow, the louver 94 is directed downward, and the return air is passed through the indoor heat exchanger 91 and blown out from the indoor unit 17 downward into the air conditioning unit 15. The conditioned air produced in the air conditioning unit 15 is then blown out from the supply air sections 20, 21, 23, 24, etc., of the living room and non-living room by the operation of the blower 18.

Description

Technical Field

[0001] The present invention relates to an air conditioning system for air conditioning and ventilating a building interior.

Background Art

[0002] Houses are becoming more airtight and highly insulated in order to achieve an energy-saving and comfortable life. On the other hand, the importance of air conditioning and ventilation is increasing in order to achieve a clean and healthy life. Conventionally, many air conditioning systems of this type provide a heat pump type air conditioner in each living room to perform air conditioning such as cooling and heating for each living room. However, due to the heat pump type, during the heating mode operation in winter, by means of a regular reverse cycle defrosting operation, frost and ice attached to the outdoor heat exchanger of the outdoor unit are melted to improve the heating capacity and energy consumption efficiency. However, during operation in the heating mode in cold regions or in severe winter, frost and ice attached to the outdoor heat exchanger grow, and in a single reverse cycle defrosting operation, the frost and ice cannot be completely melted, and the heating capacity and energy consumption efficiency after the reverse cycle defrosting operation may decrease. Also, generally, during the reverse cycle defrosting operation, the indoor fan of the indoor unit is stopped so that cold air does not blow out. Therefore, the heating cycle operation cannot be performed during the reverse cycle defrosting operation, and in some houses, the room temperature drops significantly and comfort is impaired. Therefore, in an outdoor air treatment unit that warms outdoor air and introduces it into the house, during the reverse cycle defrosting operation, under certain conditions (outdoor temperature below a certain temperature, refrigerant suction pressure below a certain value), the indoor fan of the indoor unit operates and blows air, so that the refrigerant passing through the indoor heat exchanger exchanges heat with indoor air and the evaporation capacity is increased, thereby enhancing the reverse cycle defrosting capacity and quickly melting the frost and ice attached to the outdoor heat exchanger completely. This is known (for example, see Patent Document 1). Furthermore, in air conditioners, during reverse cycle defrosting operation, the airflow adjustment vanes at the outlet of the indoor unit are set to a state of diffused airflow, and when the temperature of the indoor heat exchanger falls below a certain temperature, the indoor fan is operated to enhance the reverse cycle defrosting capacity while preventing the airflow from directly hitting people (see, for example, Patent Document 2). Furthermore, in a whole-building air conditioning system, there is an air conditioner A inside a chamber, and another air conditioner B outside the chamber, near the chamber's intake. When air conditioner A is in defrost mode, air conditioner B is operated in heating mode, and the heated air is drawn into the chamber, warming the air inside the chamber. This air is then blown into the room by a fan located in the middle of the duct connecting the chamber and the room, thus enabling heating of the room even when air conditioner A is in defrost mode (see, for example, Patent Document 3). Furthermore, there are known systems in which a house is equipped with an air conditioner and a heat exchange ventilation unit, and the exhaust air from the indoor air that has undergone heat exchange by the heat exchange ventilation unit is drawn into the outdoor heat exchanger of the air conditioner's outdoor unit. This increases heating capacity and energy efficiency when the air conditioner is operating in heating mode in winter, as the exhaust air is at a higher temperature than the outside air, and also improves defrosting capacity during defrosting operation, allowing frost and ice to melt completely and quickly (for example, Patent Document 4). Furthermore, since the outdoor units of air conditioning and heating systems will cease to function if their air vents are blocked or clogged by snowfall, it is known that outdoor units in snowy regions are protected by snow hoods or the like (for example, Patent Document 5). [Prior art documents] [Patent Documents]

[0003] [Patent Document 1] Patent No. 7478523 [Patent Document 2] Patent No. 6274168 [Patent Document 3] Patent No. 6975266 [Patent Document 4] Japanese Patent Publication No. 2006-112684 [Patent Document 5] Japanese Patent Publication No. 2001-182969 [Overview of the project] [Problems that the invention aims to solve]

[0004] However, the outdoor air processing unit described in Patent Document 1 has the problem that, while the indoor unit is performing a cooling cycle operation, it blows out even colder air by drawing in cold outside air, which is then blown out, causing a significant drop in the room temperature inside the house and causing discomfort if the air blows directly on a person. Furthermore, the air conditioner described in Patent Document 2 had the problem that, while the air blown out from the indoor unit was less likely to hit people, it could still hit people depending on how the air conditioner was installed, and if the temperature of the blown air during reverse cycle defrosting operation was not controlled, the temperature of the room in which the unit was installed would also drop after a while during the reverse cycle defrosting operation, which could easily cause discomfort. Furthermore, in the whole-house air conditioning system described in Patent Document 3, it is thought that the capacity of the auxiliary air conditioner B is often smaller than the capacity of air conditioner A, which air conditions the entire house. Also, since the air blown out by air conditioner B is not easily drawn into the chamber, when the outside temperature is low, the air in the chamber does not warm up sufficiently, and when this air is blown into the room, it blows directly on people and causes discomfort. In addition, since the indoor fan of air conditioner A is not actively operated during reverse cycle defrosting, the reverse cycle defrosting capacity is insufficient, which can result in a longer reverse cycle defrosting time or incomplete reverse cycle defrosting. Furthermore, the air conditioning and ventilation system described in Patent Document 4 requires a separate heat exchange unit, and depending on its heat exchange efficiency and airflow, there was a problem that defrosting operation would be incomplete when there was a large amount of frost or ice on the outdoor heat exchanger during snowfall in severe winter. Furthermore, while providing a snow-proof hood, as described in Patent Document 5, has the effect of preventing falling snow from being directly sucked into the outdoor unit, there was also the problem that defrosting operation failures may occur depending on the outside temperature, installation conditions, operating conditions, etc.

[0005] The present invention aims to solve these conventional problems by providing an air conditioning system that enables a consistently energy-efficient and comfortable living environment. This is achieved by completely and quickly melting frost and ice during reverse cycle defrosting operation in heating mode in cold regions and during severe winters, improving heating capacity and energy efficiency after reverse cycle defrosting operation, while minimizing the drop in room temperature and the feeling of cold air during reverse cycle defrosting operation. [Means for solving the problem]

[0006] To achieve the above objectives, the air conditioning system of the present invention provides an air supply section and an exhaust section in multiple living rooms and non-living rooms within a building, supplies conditioned air from the air supply section to the multiple living rooms and non-living rooms, provides a return air path to return the conditioned air from the exhaust section in the multiple living rooms and non-living rooms to a return section, provides a blower and an air conditioner A in the return section, connects the air supply section and the blower, produces the conditioned air using the blower and the air conditioner A and supplies it to the air supply section, and connects the indoor unit and outdoor unit with refrigerant piping and electrical wiring, and is a heat pump The air conditioner has a refrigeration cycle of the type, in which the refrigerant returns to the compressor via a cooling cycle in which the refrigerant passes through a compressor, a four-way valve, an outdoor heat exchanger, an expansion valve, an indoor heat exchanger, and the four-way valve, and the heating cycle in which the refrigerant returns to the compressor via a heating cycle in which the refrigerant passes through the compressor, the four-way valve, the indoor heat exchanger, the expansion valve, the outdoor heat exchanger, and the four-way valve, and the indoor unit has an indoor heat exchanger and an indoor fan, and the air conditioner A operates the indoor fan during reverse cycle defrosting operation in which the refrigerant flows in the cooling cycle to defrost the outdoor heat exchanger. This method allows the indoor fan to be operated during the reverse cycle defrosting operation of air conditioner A, thereby exchanging heat between the refrigerant in the indoor heat exchanger and the return air drawn into the air conditioning unit, which is the return compartment. This increases the evaporation temperature, which in turn increases the condensation temperature, thereby enhancing the reverse cycle defrosting capacity, ensuring complete defrosting, and shortening the reverse cycle defrosting operation time. Furthermore, during reverse cycle defrosting operation, the indoor fan is operated, which cools the air inside the air conditioning unit. However, the blower distributes this cooled air to multiple living and non-living rooms. Since these multiple living and non-living rooms have a volume several times larger than a single living room that a typical air conditioner controls, the temperature drop in these rooms during reverse cycle defrosting operation is reduced. In addition, the airflow velocity from the air supply outlets in the living and non-living rooms is lower than that of a typical air conditioner's outlet, thus mitigating the feeling of cold air that people experience. Furthermore, the reverse cycle defrosting time is shortened, and the heating capacity and energy efficiency after the reverse cycle defrosting operation are improved. Therefore, even if the air conditioning load and power consumption increase to compensate for the temperature drop in living and non-living rooms due to the operation of the indoor fan during the reverse cycle defrosting operation, overall energy savings are achieved.

[0007] Another method involves providing an air supply section and an exhaust section in multiple rooms within the building, supplying conditioned air from the air supply section to the multiple rooms, providing a return air path to return the conditioned air from the exhaust section of the multiple rooms to a return section, and providing a blower and an air conditioner A in the return section. The air supply unit and the blower are connected, the blower and the air conditioner A produce the conditioned air and blow it to the air supply unit, and an air conditioner B is installed in at least one of the multiple rooms. The air conditioner A connects the indoor unit and the outdoor unit with refrigerant piping and electrical wiring, and has a heat pump type refrigeration cycle. The four-way valve allows switching between a cooling cycle in which the refrigerant returns to the compressor after passing through the compressor, four-way valve, outdoor heat exchanger, expansion valve, indoor heat exchanger, and the four-way valve, and a heating cycle in which the refrigerant returns to the compressor after passing through the compressor, four-way valve, indoor heat exchanger, expansion valve, outdoor heat exchanger, and the four-way valve. The indoor unit has the indoor heat exchanger and an indoor fan. When air conditioner A is in reverse cycle defrosting operation, flowing the refrigerant in the cooling cycle to defrost the outdoor heat exchanger, and air conditioner B is in heating operation, the indoor fan is operated. This method allows the indoor fan to be operated during the reverse cycle defrosting operation of air conditioner A, thereby exchanging heat between the refrigerant in the indoor heat exchanger and the return air drawn into the air conditioning unit, which is the return compartment. This increases the evaporation temperature, which in turn increases the condensation temperature, thereby enhancing the reverse cycle defrosting capacity, ensuring complete defrosting, and shortening the reverse cycle defrosting operation time. Furthermore, during reverse cycle defrosting, the indoor fan is operated, which cools the air inside the air conditioning unit. However, the blower distributes this cooled air to multiple rooms. Since these multiple rooms have a volume several times larger than a single room that a typical air conditioner controls, the temperature drop in these rooms during reverse cycle defrosting is reduced. Also, the airflow velocity of the air supplied from the air intake in each room is lower than that of a typical air conditioner's outlet, which reduces the feeling of cold air that people experience. Furthermore, since air conditioner B is installed in at least one of the multiple rooms and operates in heating mode, even if cold conditioned air is blown into that room, the heating operation of air conditioner B will cause almost no temperature drop. As a result, the return air from that room, where no temperature drop occurs, returns to the air conditioning unit, thus reducing the temperature drop of the return air drawn into the air conditioning unit. Furthermore, the reverse cycle defrosting time is shortened, and the heating capacity and energy efficiency after reverse cycle defrosting are improved. Therefore, even if the air conditioning load and power consumption increase due to the indoor fan operating during reverse cycle defrosting to compensate for the drop in room temperature, overall energy savings are achieved.

[0008] Another method involves providing an air supply unit and an exhaust unit in multiple rooms within a building, supplying conditioned air to the multiple rooms from the air supply unit, providing a return air path to return the conditioned air from the exhaust units in the multiple rooms to a return compartment, providing a blower and an air conditioner A in the return compartment, connecting the air supply unit and the blower, producing the conditioned air with the blower and air conditioner A and supplying it to the air supply unit, introducing the outside air into the return air path, the return compartment, or the rooms while exchanging heat between the outside air and the return air from the exhaust unit in an outdoor air introduction path and an indoor air exhaust path connected to the return air path, and exhausting the return air to the outside through a ventilation exhaust unit provided in a non-living room. A vent is provided, and the air conditioner A connects the indoor unit and the outdoor unit with refrigerant piping and electrical wiring, and has a heat pump type refrigeration cycle, in which the refrigerant returns to the compressor via a cooling cycle in which the refrigerant passes through the compressor, four-way valve, outdoor heat exchanger, expansion valve, indoor heat exchanger, and the four-way valve, and the heating cycle in which the refrigerant returns to the compressor via the compressor, four-way valve, indoor heat exchanger, expansion valve, outdoor heat exchanger, and the four-way valve, and the indoor unit has an indoor heat exchanger and an indoor fan, and the indoor fan is operated during reverse cycle defrosting operation in which the air conditioner A flows the refrigerant in the cooling cycle to defrost the outdoor heat exchanger. This method allows the indoor fan to be operated during the reverse cycle defrosting operation of air conditioner A, thereby exchanging heat between the refrigerant in the indoor heat exchanger and the return air drawn into the air conditioning unit, which is the return compartment. This increases the evaporation temperature, which in turn increases the condensation temperature, thereby enhancing the reverse cycle defrosting capacity, ensuring complete defrosting, and shortening the reverse cycle defrosting operation time. Furthermore, during reverse cycle defrosting, the indoor fan is operated, which cools the air inside the air conditioning unit. However, the blower distributes this cooled air to multiple rooms. Since these multiple rooms have a volume several times larger than a single room that a typical air conditioner controls, the temperature drop in these rooms during reverse cycle defrosting is reduced. Also, the airflow velocity of the air supplied from the air intake in each room is lower than that of a typical air conditioner's outlet, which reduces the feeling of cold air that people experience. Furthermore, the heat exchange ventilation unit introduces outside air into the building after heat exchange with the indoor air of non-habitable rooms that do not have an air supply unit for blowing out conditioned air. However, even if the indoor fan operates during reverse cycle defrosting and the conditioned air generated by the air conditioning unit becomes cold, this conditioned air is not blown into non-habitable rooms that do not have an air supply unit, thus maintaining the temperature of the non-habitable rooms at the temperature before the reverse cycle defrosting operation for a while. Since the outside air exchanges heat with the air at that temperature, the outside air after heat exchange is close to the temperature of the indoor air before the reverse cycle defrosting operation, and is higher than the temperature of the air blown out by the indoor unit. As it is blown out from the ventilation air supply vent and drawn into the air conditioning unit through the intake grille, the temperature drop of the conditioned air generated by the air conditioning unit is suppressed. Furthermore, the reverse cycle defrosting time is shortened, and the heating capacity and energy efficiency after reverse cycle defrosting are improved. Therefore, even if the air conditioning load and power consumption increase due to the indoor fan operating during reverse cycle defrosting to compensate for the drop in room temperature, overall energy savings are achieved.

[0009] Another method involves providing an air supply section and an exhaust section in multiple rooms within a building, supplying conditioned air to the multiple rooms from the air supply section, providing a return air path to return the conditioned air from the exhaust section of the multiple rooms to a return section, providing a blower and an air conditioner A in the return section, connecting the air supply section and the blower, the air conditioner A having an indoor unit, the blower's airflow rate being greater than the indoor unit's airflow rate, and using the blower and air conditioner A to create conditioned air with a temperature difference smaller than the temperature difference between the air conditioner A's outlet and the room's temperature, and supplying it to the air supply section, and the air conditioner A having refrigerant piping connecting the indoor unit and the outdoor unit. The system is connected to electrical wiring and has a heat pump type refrigeration cycle, and is characterized in that it can switch between a cooling cycle in which the refrigerant returns to the compressor after passing through the compressor, four-way valve, outdoor heat exchanger, expansion valve, indoor heat exchanger, and the four-way valve, and a heating cycle in which the refrigerant returns to the compressor after passing through the compressor, four-way valve, indoor heat exchanger, expansion valve, outdoor heat exchanger, and the four-way valve, and the indoor unit has the indoor heat exchanger and an indoor fan, and the indoor fan is operated during a reverse cycle defrosting operation in which the air conditioner A flows the refrigerant in the cooling cycle to defrost the outdoor heat exchanger. This method allows the indoor fan to be operated during the reverse cycle defrosting operation of air conditioner A, thereby exchanging heat between the refrigerant in the indoor heat exchanger and the return air drawn into the air conditioning unit, which is the return compartment. This increases the evaporation temperature, which in turn increases the condensation temperature, thereby enhancing the reverse cycle defrosting capacity, ensuring complete defrosting, and shortening the reverse cycle defrosting operation time. Furthermore, during reverse cycle defrosting, the indoor fan is operated, which cools the air inside the air conditioning unit. However, the blower distributes this cooled air to multiple rooms. Since these multiple rooms have a volume several times larger than a single room that a typical air conditioner controls, the temperature drop in these rooms during reverse cycle defrosting is reduced. Also, the airflow velocity of the air supplied from the air intake in each room is lower than that of a typical air conditioner's outlet, which reduces the feeling of cold air that people experience. Furthermore, since the airflow from the fan is greater than the airflow from the indoor unit of air conditioner A, it creates conditioned air with a temperature difference smaller than the temperature difference between the indoor unit's outlet air and the room's temperature, and blows it into the room. As a result, during reverse cycle defrosting operation, the conditioned air becomes significantly hotter than the indoor unit's outlet air, further reducing the temperature drop in the room and mitigating the feeling of cold air. Furthermore, the reverse cycle defrosting time is shortened, and the heating capacity and energy efficiency after reverse cycle defrosting are improved. Therefore, even if the air conditioning load and power consumption increase due to the indoor fan operating during reverse cycle defrosting to compensate for the drop in room temperature, overall energy savings are achieved.

[0010] Another method involves providing an air supply section and an exhaust section in multiple living rooms and non-living rooms within a highly airtight, highly insulated house, supplying conditioned air from the air supply section to the multiple living rooms and non-living rooms, providing a return air passage to return the conditioned air from the exhaust sections in the multiple living rooms and non-living rooms to a return section, providing a blower and an air conditioner A in the return section, connecting the air supply section and the blower, and providing a heat exchange air unit in an outdoor air introduction passage and an indoor air exhaust passage connected to the return air passage, which introduces the outdoor air into the return air passage, the return section, the living room or non-living room while exchanging heat between the outdoor air and the return air from the exhaust section, and exhausting the return air to the outside, wherein the air conditioner A has an indoor unit, the airflow rate of the blower is greater than the airflow rate of the indoor unit, and the air conditioner A and the blower provide the air conditioning The air conditioning unit A produces conditioned air with a temperature difference smaller than the temperature difference between the temperature of the blown air from the unit and the temperatures of the living room and the non-living room, and blows it into the air supply section. The outdoor unit connects the indoor unit and the outdoor unit with refrigerant piping and electrical wiring, and has a heat pump type refrigeration cycle. The four-way valve allows switching between a cooling cycle in which the refrigerant returns to the compressor through the compressor, four-way valve, outdoor heat exchanger, expansion valve, indoor heat exchanger, and the four-way valve, and a heating cycle in which the refrigerant returns to the compressor through the compressor, four-way valve, indoor heat exchanger, expansion valve, outdoor heat exchanger, and the four-way valve. The outdoor unit has an outdoor heat exchanger and an outdoor fan, and the heat exchange unit blows out the heat-exchanged return air so that it is drawn into the outdoor heat exchanger by the outdoor fan. This method ensures that the airflow from the fan is greater than that of the indoor unit of air conditioner A, and that the temperature difference between the temperature of the indoor unit's discharged air and the temperature of the living and non-living rooms is smaller. This air is then distributed to multiple living and non-living rooms within a highly airtight and well-insulated house, resulting in a stable and uniform comfortable temperature and humidity throughout the entire building. Furthermore, because this returned air exchanges heat with the outside air, the returned air exhausted by the heat exchange unit has a higher total heat content and is more stable than the outside air. Furthermore, during heating mode operation, return air with a higher total heat content (higher temperature and humidity) than the outdoor air is blown out by the heat exchange unit. This return air then merges with the outdoor air, creating air with a higher total heat content than the outdoor air. As this air passes through the outdoor heat exchanger, which acts as an evaporator, the evaporation temperature rises, especially at extremely low temperatures. This reduces frost and ice formation on the outdoor heat exchanger, decreasing the frequency and duration of reverse cycle defrosting operation. This improves heating capacity and energy efficiency, resulting in more energy-efficient and comfortable air conditioning. Furthermore, during heating cycle operation, indoor air that is warmer than the outdoor air is drawn into the outdoor heat exchanger, and during cooling cycle operation, indoor air that is warmer than the outdoor air is drawn into the outdoor heat exchanger, where it exchanges heat with the refrigerant. As a result, the evaporation temperature rises during heating cycle operation and the condensation temperature falls during cooling cycle operation, improving energy efficiency and saving energy.

[0011] Another method involves providing the outdoor unit with a sensor for detecting the outdoor temperature, and the control device operating the indoor fan when the outdoor temperature detected by the sensor falls below a certain temperature while the air conditioner A is performing the reverse cycle defrosting operation. This method increases the likelihood that defrosting can be completed completely without needing to operate the indoor fan of air conditioner A or raise the evaporation temperature of the indoor heat exchanger, as the condensation temperature of the outdoor heat exchanger is high when the outdoor temperature is above a certain level during reverse cycle defrosting operation. The indoor fan is only operated when the outdoor temperature is low and there is a possibility that defrosting will be incomplete, so throughout the year there will be little to no feeling of cold air or temperature drop, improving comfort.

[0012] Another means is to provide the air conditioner A with a switch that can switch between stopping the indoor fan and operating the indoor fan during the reverse cycle defrosting operation. This method allows the indoor fan to be operated only when frost or ice buildup is excessive due to the outdoor unit's installation conditions, resulting in incomplete reverse-cycle defrosting. Therefore, the indoor fan can be easily operated on-site during installation or when such conditions arise, enabling complete defrosting.

[0013] Another method involves providing a snow cover on the outdoor unit of the air conditioner A, and blowing out a portion of the return air that has undergone heat exchange by the heat exchange unit onto the outdoor air intake side of the snow cover. This method allows for the installation of a snow cover on the outdoor unit of air conditioner A, with the exhaust from the heat exchange unit blown out to the intake side. This makes it easy to install the unit so that the exhaust is blown out to the back and side of the intake of the outdoor unit. The exhaust from the heat exchange unit is reliably drawn into the outdoor heat exchanger of the outdoor unit, preventing snow and ice from accumulating on the outdoor heat exchanger during severe winter conditions, and preventing the outdoor heat exchanger from freezing during heating mode operation.

[0014] Another method involves providing an air supply section and an exhaust section in the living room and non-living room of a highly airtight and well-insulated building, supplying conditioned air from the air supply section to the living room and non-living room, and providing a return air passage to return the return air from the exhaust section in the living room and non-living room back to the air conditioning unit, providing an intake section and the indoor unit of air conditioner A above the air conditioning unit, providing a blower below the air conditioning unit, connecting the air supply section and the blower, drawing in the return air from the intake section, and using the blower and air conditioner A to create the conditioned air and supply it to the air supply section, with air conditioner A having an indoor unit and an outdoor unit connected by refrigerant piping and electrical wiring, and having a heat pump type refrigeration cycle, where the refrigerant returns to the compressor after passing through a compressor, a four-way valve, an outdoor heat exchanger, an expansion valve, an indoor heat exchanger, and the four-way valve. The four-way valve allows switching between a cooling cycle and a heating cycle in which the refrigerant passes through the compressor, the four-way valve, the indoor heat exchanger, the expansion valve, the outdoor heat exchanger, and the four-way valve back to the compressor. The indoor unit has an indoor heat exchanger, an indoor fan, and louvers. When the air conditioner A is in heating operation and in reverse cycle defrosting operation, where the refrigerant is circulated in the cooling cycle to defrost the outdoor heat exchanger, the indoor fan is operated at maximum airflow, the louvers are directed downward, the return air passes through the indoor heat exchanger, and is blown out downward from the indoor unit into the air conditioning unit. The conditioned air produced in the air conditioning unit is then blown out from the supply air section between the living room and the non-living room by the operation of the blower. This method allows the indoor fan to operate at maximum airflow, exchanging a large amount of heat with the warm indoor air, which is the room temperature during heating operation. As a result, the evaporation temperature of the indoor heat exchanger rises more quickly, the condensation temperature of the outdoor heat exchanger 99 rises more quickly, the condensation capacity increases, defrosting can be performed more quickly and completely, and because the evaporation temperature rises, the temperature of the airflow blown out from the indoor unit increases, reducing the difference with the room temperature. This reduces the temperature drop in multiple living and non-living rooms during reverse cycle defrosting operation, and also alleviates the feeling of cold air that people perceive. Furthermore, during reverse cycle defrosting operation, because the indoor unit's louvers are facing downwards, even when the indoor fan of the indoor unit, located above the air conditioning unit, operates at its maximum airflow for a long reach, the airflow from the indoor unit does not flow out of the air conditioning unit from the intake, also located above the air conditioning unit. As a result, the space in front of the air conditioning unit does not experience a temperature drop, and if a person is present, they will not feel the cold air directly hitting them.

[0015] Another means is an air conditioning system in which an air supply unit and an exhaust unit are provided in at least one of the air-insulated and airtight spaces in the attic, under the floor, or between floors of the building, and the conditioned air produced by the air conditioning unit is blown out from the air supply unit by a blower, wherein the amount of air blown out per unit volume of the conditioned air blown out from the air supply unit of at least one of the air-insulated and airtight spaces in the attic, under the floor, or between floors is greater than the amount of air blown out per unit volume of the conditioned air blown out from the air supply unit of each of the living room and the non-living room. This method ensures that the capacity per unit volume of conditioned air in frequently occupied and non-occupied rooms is lower than the capacity per unit volume of conditioned air in areas where people rarely occupy, such as attics, crawl spaces, or between floors. As a result, the temperature drop between occupied and non-occupied rooms is smaller, and the feeling of cold air is less pronounced. Furthermore, the conditioned air blown into the attic, crawl space, or between floors experiences minimal temperature changes after heating operation due to heat transfer from the roof, floor, and insulation materials surrounding the insulated and airtight space within the attic, crawl space, or between floors. As a result, even if the conditioned air flows into other rooms through the exhaust, those rooms are less likely to feel cold.

[0016] Another method involves connecting the blower and the air supply unit with an airtight chamber, the chamber being insulated by being covered with at least one of the following: an air-conditioned room, an air-conditioned space, or an insulating material. This method allows conditioned air to be blown into living and non-living rooms through a chamber (air duct) of a certain volume. As the air passes through the chamber (air duct), it is surrounded by rooms or spaces that are air-conditioned above and below during heating operation, and surrounded on all sides by outer walls with insulating material. The temperature of the conditioned air rises due to the transfer of heat stored in the insulated chamber (air duct), resulting in less temperature drop in living and non-living rooms.

[0017] Another method involves providing an air supply section and an exhaust section in both the living room and non-living room of a highly airtight and well-insulated building, supplying conditioned air from the air supply section to the living room and non-living room, providing a return air passage to return the return air from the exhaust section in the living room and non-living room back to the air conditioning unit, providing an intake section and the indoor unit of the air conditioner D above the air conditioning unit, providing a blower below the air conditioning unit, connecting the air supply section and the blower, drawing in the return air from the intake section, and using the blower and the air conditioner D to create the conditioned air, which is then supplied to the air supply section. The air conditioner D connects the indoor unit and the outdoor unit with refrigerant piping and electrical wiring, and has a heat pump type refrigeration cycle, and the four-way valve allows switching between a cooling cycle in which the refrigerant returns to the compressor after passing through the compressor, four-way valve, outdoor heat exchanger, expansion valve A, indoor heat exchanger B, expansion valve B, indoor heat exchanger A, and the four-way valve, and a heating cycle in which the refrigerant returns to the compressor after passing through the compressor, four-way valve, indoor heat exchanger A, expansion valve B, indoor heat exchanger B, expansion valve A, outdoor heat exchanger, and the four-way valve. The indoor unit comprises the indoor heat exchanger A, the expansion valve B, the indoor heat exchanger B, an indoor fan, and a louver. When the air conditioner D is in heating operation and in reverse cycle defrosting operation, where the refrigerant is circulated in the cooling cycle to defrost the outdoor heat exchanger, the expansion valve A is fully opened, the expansion valve B is opened to an appropriate degree, the indoor fan is operated at maximum airflow, the louver is directed downward, the return air is passed through the indoor heat exchanger A and the indoor heat exchanger B, and blown downward from the indoor unit into the air conditioning unit. The conditioned air produced in the air conditioning unit is then blown out from the supply air section between the living room and the non-living room by the operation of the blower. With this method, during reverse cycle defrosting operation, only indoor heat exchanger A functions as an evaporator, resulting in a reduced evaporation capacity. However, indoor heat exchanger B functions as a condenser, and since the indoor fan is operated at maximum airflow, the condensation capacity of indoor heat exchanger B increases. As a result, the condensation temperature of the outdoor heat exchanger rises more quickly, increasing the condensation capacity and enabling faster and complete defrosting. Furthermore, only indoor heat exchanger A functions as an evaporator, resulting in reduced evaporation capacity and less temperature drop in the air passing through indoor heat exchanger A. Indoor heat exchanger B, which functions as a condenser, essentially acts as a reheater, and the air passing through it does not experience a temperature drop. As a result, these airs are mixed, and the discharged airflow shows almost no temperature drop relative to the room temperature, resulting in almost no temperature difference between living and non-living spaces, and virtually no feeling of cold air perceived by people.

[0018] Another method involves providing an air supply section and an exhaust section in both the living room and the non-living room within a highly airtight and well-insulated building, supplying conditioned air from the air supply section to the living room and the non-living room, providing a return air passage to return the return air from the exhaust section in the living room and the non-living room back to the air conditioning unit, providing an intake section and the indoor unit of the air conditioner A above the air conditioning unit, providing a blower below the air conditioning unit, connecting the air supply section and the blower, drawing in the return air from the intake section, and using the blower and the air conditioner A to create the conditioned air, which is then supplied to the air supply section. The air conditioner A connects the indoor unit and the outdoor unit with refrigerant piping and electrical wiring, and has a heat pump type refrigeration cycle, and the four-way valve allows switching between a cooling cycle in which the refrigerant returns to the compressor after passing through the compressor, four-way valve, outdoor heat exchanger, expansion valve, indoor heat exchanger, and the four-way valve, and a heating cycle in which the refrigerant returns to the compressor after passing through the compressor, four-way valve, indoor heat exchanger, expansion valve, outdoor heat exchanger, and the four-way valve. The indoor unit has an indoor heat exchanger, an indoor fan, and louvers. When the air conditioner A is in heating operation and in reverse cycle defrosting operation, which involves flowing the refrigerant in the cooling cycle to defrost the outdoor heat exchanger, the amount of air blown by the blower is greater than the amount of air blown out by the indoor unit. The blower draws in the return air from the intake, operates the indoor fan at maximum airflow, directs the louvers downward, and allows the return air to pass through the indoor heat exchanger. The air blown out from the indoor unit downward into the air conditioning unit is mixed with the return air drawn in from the intake and bypass airflow that does not pass through the indoor heat exchanger. This mixes the air-conditioned air with a temperature difference smaller than the temperature difference between the temperature of the air blown out by the indoor unit and the temperature of the return air, and this air-conditioned air is blown out from the supply air outlets between the living room and the non-living room. This method ensures that the airflow from multiple fans is greater than the airflow from the indoor unit of air conditioner A. As a result, conditioned air with a temperature difference smaller than the temperature difference between the indoor unit's outlet airflow and the living / non-living rooms is created and blown into the living / non-living rooms. Therefore, during reverse cycle defrosting operation, the conditioned air becomes significantly hotter than the indoor unit's outlet airflow, resulting in less temperature drop between the living / non-living rooms and further mitigating the feeling of cold air. [Effects of the Invention]

[0019] According to the present invention, in reverse cycle defrosting operation during heating mode operation in cold regions or during severe winter, frost and ice are completely and quickly melted, improving heating capacity and energy consumption efficiency after reverse cycle defrosting operation, while minimizing the drop in room temperature and the feeling of cold air during reverse cycle defrosting operation. This provides an air conditioning and ventilation system that can always provide an energy-saving and comfortable living environment. Furthermore, in cold regions or during severe winter conditions, this system prevents snow and ice from accumulating on the outdoor heat exchanger while simultaneously preventing the outdoor heat exchanger from freezing during heating mode operation, thus providing an energy-saving and comfortable heating mode operation. Furthermore, we can provide an air conditioning system that is energy-efficient and maintains a comfortable temperature throughout the year. [Brief explanation of the drawing]

[0020] [Figure 1] Cross-sectional view of a building showing the configuration of the air conditioning system in Embodiment 1 of the present invention. [Figure 2] Vertical cross-sectional view of the air conditioning unit in Embodiment 1 of the present invention [Figure 3] Vertical cross-sectional view of the indoor unit of air conditioner A in Embodiment 1 of the present invention [Figure 4] Horizontal cross-sectional view of the outdoor unit and snow cover of air conditioner A in Embodiment 1 of the present invention. [Figure 5] Perspective view of the outdoor unit and snow cover of air conditioner A in Embodiment 1 of the present invention [Figure 6] Refrigeration cycle diagram of air conditioner A in Embodiment 1 of the present invention [Figure 7] Timing chart for reverse cycle defrosting operation of an air conditioning system in Embodiment 1 of the present invention [Figure 8] Timing chart for reverse cycle defrosting operation of an air conditioning system in Embodiment 2 of the present invention [Figure 9] Timing chart for reverse cycle defrosting operation of an air conditioning system in Embodiment 3 of the present invention [Figure 10] Timing chart for reverse cycle defrosting operation of an air conditioning system in Embodiment 4 of the present invention [Figure 11] Timing chart for reverse cycle defrosting operation of an air conditioning system in Embodiment 5 of the present invention [Figure 12] Cross-sectional view of a building showing the configuration of the air conditioning system in Embodiment 6 of the present invention. [Figure 13] Vertical cross-sectional view of the air conditioning unit in Embodiment 6 of the present invention [Figure 14] Vertical cross-sectional view of the indoor unit of the air conditioner D in Embodiment 6 of the present invention [Figure 15] Refrigeration cycle diagram of air conditioner D in Embodiment 6 of the present invention [Figure 16] Timing chart for reverse cycle defrosting operation of an air conditioning system in Embodiment 6 of the present invention [Modes for carrying out the invention]

[0021] (Embodiment 1) Figure 1 is a cross-sectional view of a building showing the configuration of an air conditioning system in Embodiment 1 of the present invention. As shown in the diagram, the air conditioning system 2 installed in building 1, a highly airtight and highly insulated house, provides air conditioning and ventilation to living rooms 4, bedrooms 5, children's rooms (not shown), bathrooms 6, washrooms 7, toilets 8, kitchens (not shown), attics 9, entrance halls 10, stair landings 11, corridors (not shown), underfloor spaces 12, storage rooms (not shown), walk-in closets (not shown), and other habitable and non-habitable rooms within building 1. In this case, a habitable room refers to a room continuously used for living, working, organizing, meeting, recreation, or other similar purposes, while a non-habitable room refers to any other room. However, for rooms whose use makes it difficult to determine whether they are habitable, the determination should be made according to their actual use. Building 1 is completely covered with insulation (not shown) and airtight sheets (not shown) to seal the exterior envelope. The roof (not shown) is insulated, the foundation (not shown) is insulated, the windows are insulated sashes such as triple-glazed resin sashes (not shown), and the doors are insulated doors (not shown). The entire interior of Building 1, including the attic (insulated space) 9 and the crawl space (insulated space) 12, is an insulated space, encompassing both habitable and non-habitable rooms. There are two main types of insulation: external insulation and internal insulation. The choice of insulation method depends on the advantages and disadvantages of each. However, this study focuses on Building 1, which has no insulation defects in its exterior envelope and meets at least the ZEH (Zero Energy House) insulation performance standards. Regarding airtightness performance, although it depends on the specifications of the airtight sheet, the target building is one that maintains the continuity of the airtight layer by applying airtight tape or similar to the seams of the airtight sheet, and clears at least a C value of 1.0.

[0022] An air conditioning unit (return section) 15 is provided on the stair landing 11 as a return section that creates conditioned air and blows it to living rooms, non-living rooms, etc. The air conditioning unit 15 is provided with an intake grille 16 into which the conditioned air from living rooms and non-living rooms etc. flows in as return air, an air conditioner A13 having an indoor unit 17 connected to an outdoor unit 19 installed outside by refrigerant piping and electrical wiring (not shown) and having an indoor heat exchanger (not shown) and an indoor fan (not shown) inside, and a plurality of blowers 18 that blow conditioned air to living rooms and non-living rooms etc. The air conditioner A13 has a remote control (not shown) that can operate / stop, switch between cooling / heating / dehumidifying modes, set airflow, set temperature, set air outlet direction, etc.

[0023] In this embodiment, the return compartment is an air conditioning unit 15 that is sealed and covered with walls and insulation, and is located on the landing 11 of the stairs. However, it may also be located in the attic 9, under the floor 12, under the stairs (not shown), etc., as long as it is in the return air passage where the conditioned air from the living room and non-living room returns as return air. Furthermore, the return area may be a compact enclosure covered with sheet metal or insulation, and as long as uniform conditioned air can be produced by the positional relationship between the indoor unit 17 and the blower 18 of the air conditioner A13, it may also be a partially open space, such as a stair landing 11, entrance 10, or corridor.

[0024] In the ceilings or floors of the living rooms (4), bedrooms (5), attics (9), underfloor spaces (12), and bathrooms (6), there are air supply units (20, 21, 23, 24) and a bathroom air supply unit (22) that blow out conditioned air produced by the air conditioning unit (15). There are also 6 other air supply units in the other habitable and non-habitable rooms, for a total of 11 units in the building. The air supply unit 20 and other components are generally installed in the ceiling, but they may also be installed in the walls or floor if it prevents the conditioned air from directly hitting people and improves the temperature distribution between living and non-living spaces. Multiple blowers 18, air supply units 20, 21, 23, 24, and bathroom air supply unit 22 are connected in a one-to-one-to-one configuration by multiple ducts 30, 31, 33, 34, and duct 32. Eleven blowers 18 and ducts 30, etc., are provided. Each blower 18 has a switch (not shown) that allows for temperature control by adjusting the airflow and starting / stopping the blowers 18. The airflow rate of each fan 18 is determined by the volume of the living room and the non-living room, respectively. The airflow rate required for air conditioning is 2.5 m³ for both the living room and the non-living room. 3 At least 8 meters 3 / h or more, ideally 20m 3 A rate of at least / h is desirable, and the airflow rate is adjusted according to the size of the living and non-living rooms and the air conditioning load such as solar radiation. The blower 18 rotates a sirocco fan (not shown) with a highly efficient DC motor (not shown), so the rotation speed of the sirocco fan (not shown) is controlled by the electrical unit (not shown) or the like according to the air conditioning load, etc. In addition, the air supply units 20 and others are basically installed in all habitable rooms within the building 1 and in non-habitable rooms other than the so-called dirty zones such as the washroom 7 and toilet 8. However, if the floor area is too small and the airflow of the blower 18 at the lowest setting is too much, resulting in loud exhaust noise and a feeling of draft, two air supply units 20 and others may be installed in the adjacent habitable room or non-habitable room. In the washroom 7 and toilet 8, where the air supply units 20 and others are not installed, ventilation exhaust units 61 and 62 are provided so that the air is exhausted outside by the heat exchange ventilation unit 50, which will be described later. As a result, the conditioned air generated in the air conditioning unit 15 is blown by the air blower 18 through the duct 30 and other ducts that run entirely through the insulated space, and is then blown out from the air supply unit 20 and other ducts and the bathroom air supply unit 22 to the living room 4, bedroom 5, attic 9, underfloor space 12, bathroom 6 and other areas, forming an air conditioning air supply path (not shown).

[0025] In this embodiment, the air blower 18, the air supply unit 20 and others, and the duct 30 and others are connected in a one-to-one-to-one relationship. Changing the airflow rate of the air blower 18 directly changes the airflow rate of the air supply unit 20 and others, making it easy to control air conditioning such as temperature adjustment. However, since the building 1 is highly airtight and well-insulated, for example, a large air blower with a large airflow rate could be connected to a thick duct and then branched into multiple thinner ducts. Alternatively, instead of ducts, chambers made of wood, metal, etc., that prevent air leakage could be used inside the building, such as between floors, in the ceiling, under the floor, or in the walls. Multiple air supply units 20 and others could also be provided in a single room. As long as the airflow is smooth, stable, and has minimal resistance to the conditioned air, and uniformly air-conditions the room, these changes should be decided based on the relative positions of the air blower, air supply unit, etc. within the building 1, considering material costs, constructability, and maintenance. Furthermore, the blower 18 in this embodiment is an integrated type with an intake grille (not shown) on the surface of the main body, a fan (not shown), a motor (not shown), and an electrical unit (not shown) inside, and a duct connection part. However, an intake box consisting only of an intake grille (not shown) and the main body may be provided with a duct connection port, installed inside the air conditioning unit, and connected to a duct to create an intermediate duct type blower between the intake box and the air supply unit, which has a fan (not shown), a motor (not shown), and an electrical unit (not shown) inside the main body and a duct connection part. These modifications should be determined based on ease of installation, maintenance, specifications, etc.

[0026] In the living room 4, bedroom 5, attic 9, underfloor space 12, and other areas, which have air supply units 20 and others, exhaust units 40, 41, 43, 44, and others are provided, such as undercuts in doors and vents. The conditioned air blown out from the air supply units 20 and others becomes return air after conditioned the living and non-living spaces, and flows into the corridor (not shown) from the exhaust units 40 and others, and returns to the air conditioning unit (return section) 15 through the entrance 10 and stair landing 11, passing through the intake grille 16. As a result, a return air passage (not shown) is formed, which is an airflow path that returns to the air conditioning unit (return section) 15 from the corridor (not shown), entrance hall 10, stair landing 11, etc., through the exhaust sections 40 and other parts of the living and non-living rooms. Then, the air conditioning duct and the return duct are connected to form a circulation path (not shown). The intake grille 16 is equipped with a filter (not shown) to remove dust and other particles from the return air and purify it. The return air is usually almost the same temperature and humidity as the room, and the CO2 concentration is slightly higher in rooms where people are present. However, since the fan 18 is constantly running and the conditioned air, return air, and fresh outside air introduced into building 1 (described later) are circulating within building 1, the air quality of the return air, other than that of the blown-out conditioned air, is not degraded. Living room 4 is equipped with the indoor unit 46 of air conditioner B45, which is connected to the outdoor unit (not shown) and operates as needed in the event of a malfunction of air conditioner A13 or when heating the entire building 1 during severe winter conditions, as described later.

[0027] A heat exchange ventilation unit 50 is installed in the ceiling space 9 to introduce outside air into the room and, when exhausting indoor air to the outside, recover all the heat from the indoor air into the outside air, thereby ventilating the entire building 1. The amount of outdoor air introduced and the amount of indoor air discharged, or so-called ventilation airflow, by the heat exchange ventilation unit 50 can be calculated, for example, for a floor area of ​​approximately 100m². 2 For a ceiling height of 2.5m and a ventilation rate of 0.5 times / hour, the 24-hour ventilation airflow is 125m³. 3 It becomes / h. In this embodiment, the heat exchange ventilation unit 50 has a 24-hour ventilation airflow of 125 m³. 3 / h, strong notch ventilation airflow 250m 3 At a rate of / h, the total heat exchange rate is approximately 70%. In the bathroom 7 and toilet 8 within building 1, ventilation and exhaust units 61 and 62, such as exhaust grilles, are installed in the ceilings to exhaust air from the respective non-habitable rooms, and are connected to exhaust ducts A66 and A67, respectively. Exhaust ducts A66 and A67 are connected to exhaust duct B71 at a junction 70, and exhaust duct B71 is connected to a heat exchange ventilation unit 50. A ventilation fan 60 is installed in the ceiling of bathroom 6, and an outdoor exhaust hood 75 is provided in a penetration hole in the exterior wall of building 1, connected by a duct 65. In this embodiment, a bathroom air supply unit 22 is provided in the bathroom 6, but if clothes drying or the like is not performed in the bathroom 6, it is not necessary to provide the bathroom air supply unit 22. Furthermore, the ventilation fan 60 is provided along with the bathroom air supply unit 22 to prevent the conditioned air blown into the bathroom 6, along with the odor and moisture contained within the bathroom, from flowing out through the bathroom ventilation unit 85 or gaps in the bathroom door into the washroom 7, etc., and causing adverse effects on surrounding living and non-living rooms such as condensation and mold growth.

[0028] An exhaust duct C76 is connected to the exhaust side of the heat exchange ventilation unit 50, passes through the insulated space inside the building 1, descends to the first floor, and connects to a penetrating duct 72 in the exterior wall. A snow cover 74, connected to the exterior wall side of the penetrating duct 72 and the connecting duct 73, is installed to surround the outdoor unit 19. The heat exchange ventilation unit 50 includes an introduction fan (not shown) for introducing outdoor air, an exhaust fan (not shown) for exhausting indoor air, a motor (not shown), a heat exchange element 51 for recovering the total heat from the indoor air into the outdoor air, and a pre-filter (not shown) for the element, which is positioned on the indoor air inlet side of the heat exchange element 51 to prevent dust and other particles from the indoor air from adhering to the element. Furthermore, by providing a maintenance-accessible space around the heat exchange ventilation unit 50 and an inspection hatch in the ceiling below, the heat exchange element 51 and the element pre-filter (not shown) can be easily maintained through periodic cleaning. As a result, indoor air passes from the ventilation exhaust section 61 and others through the exhaust duct A66 and others, the confluence section 70, and the exhaust duct B71, where all the heat is recovered in the heat exchange ventilation unit 50, and then through the exhaust duct C76, the through duct 72, and the connecting duct 73, before being blown out from the snow-proof cover 74 that surrounds the outdoor unit 19, and drawn into the outdoor heat exchanger (not shown) of the outdoor unit 19, thus forming an indoor air discharge path. In the indoor air exhaust passage, a pre-filter for the element (not shown) is provided before the air enters the heat exchange unit 50. However, other filters may be provided in addition to or together with the pre-filter for the element. Also, an exhaust fan for the heat exchange unit 50 is provided in the indoor air exhaust passage. However, other exhaust fans may be provided in addition to or together with the exhaust fan.

[0029] An outdoor air supply hood 77 is installed in a penetration hole in the exterior wall of building 1, and is connected to a heat exchange ventilation unit 50 by an air supply duct A78. In the middle of the air supply duct A78, a filter box 79 containing an outside air purification filter (not shown) for purifying the incoming outside air is installed in the attic 9, with an inspection opening provided in the ceiling below to facilitate maintenance such as cleaning the filter. On the ceiling of the stair landing 11, a ventilation air inlet 80 is provided in front of the intake grille 16 of the air conditioning unit 15 to blow outside air into the building 1, and is connected to the heat exchange ventilation unit 50 by an air supply duct B81. It is desirable to install the ventilation air supply opening 80 near the intake grille 16 of the air conditioning unit 15, such as in front of the intake grille 16 of the air conditioning unit 15, so that fresh outside air is introduced uniformly throughout the entire building 1 without being concentrated in some rooms or non-habitable rooms. As a result, outdoor air is introduced from the outdoor air supply hood 77, passes through the air supply duct A78, is purified in the filter box 79, recovers total heat in the heat exchange unit 50, and is introduced into the room through the ventilation air inlet 80 via the air supply duct B81.

[0030] The outdoor air intake passage is formed between the outdoor air supply hood 77 and the ventilation air inlet 80, and is comprised of an air supply duct A78, a filter box 79, a heat exchange air unit 50, and an air supply duct B81. The outdoor air intake passage is equipped with an outside air purification filter in the filter box 79, but other filters may be provided in addition to or together with the outside air purification filter. The outdoor air intake passage is also equipped with an intake fan for the heat exchange air unit 50, but other intake fans may be provided in addition to or together with the intake fan. The washroom 7, toilet 8, and bathroom 6 are equipped with ventilation supply sections 86, 87 and a bathroom ventilation section 85, which are undercuts in the doors and use a heat exchange ventilation unit 50 and a ventilation fan 60 to draw some of the return air into each non-living room. These are connected to a return air passage (not shown) that brings the air back to the air conditioning unit (return section) 15 from the washroom 7, corridor (not shown), entrance 10, stair landing 11, etc. Furthermore, the bathroom ventilation unit 85 is equipped with a door that allows its opening to be opened and closed.

[0031] Exhaust ducts A66, 67 and exhaust duct B71 are exhaust ducts installed in the insulated space between the ventilation exhaust sections 61 and 62 and the heat exchange ventilation unit 50. Therefore, to prevent dust and moisture from passing through the ducts and accumulating on the inside of the ducts, and to prevent water absorption, they are non-insulated ducts made only of polypropylene, without any insulation material or nonwoven fabric on the inside of the ducts. The exhaust duct C76 and the supply air duct A78 are installed in the insulated space between the through-duct 72, the outdoor supply air hood 77, and the heat exchange ventilation unit 50. Because they are ducts that come into contact with the outside air, they are designed to be highly insulated, moisture-resistant, and flexible. Duct 65 is also the same duct as above because it is the duct between the outdoor exhaust hood 75 and the ventilation fan 60. The supply air duct B81 is installed in the insulated space between the ventilation air inlet 80 and the heat exchange air unit 50, and therefore has high thermal insulation, moisture resistance, and flexibility. Since the heat exchange ventilation unit 50, exhaust duct C76, and supply air duct A78 are in contact with the outside air, there is a possibility of condensation and the intrusion of dust from outside. Therefore, an inspection opening should be provided nearby to allow for regular cleaning and replacement. Furthermore, regarding the ventilation fan 60 and duct 65 connected to bathroom 6, in the event of condensation inside, moisture should not accumulate, so the duct should be routed vertically as much as possible, and an inspection opening should be provided so that the inside of the duct can be cleaned and replaced.

[0032] Figure 2 is a longitudinal cross-sectional view of the air conditioning unit 15 in Embodiment 1 of the present invention. The air conditioning unit 15, which is sealed by walls (including a sealed door) and insulation, is installed on the stair landing 11. An intake grille 16 is provided above the sealed door (not shown) adjacent to the stair landing 11, through which air conditioned from the living room and non-living rooms flows in as return air, and is equipped with a filter 25. The indoor unit 17 of the air conditioner A13 is located in front of the intake grille 16, at a distance from the back, and the multiple blowers 18 are located in the lower part of the air conditioning unit 15, with their main bodies embedded in the vertical shaft 35 on the back side of the air conditioning unit 15. The indoor unit 17 draws in a portion of the air (a mixture of return air from living and non-living rooms and introduced outdoor air at the stair landing 11) from the intake grille 16 by the blower 18, and uses an indoor fan (not shown) to draw in air from the intake ports 82 on the top and front, cleans it with the indoor unit filter 83, and blows out the air that has exchanged heat with the refrigerant in the indoor heat exchanger (not shown) downwards from the outlet 84. An air purifier 88 is installed between the indoor unit 17, the intake grille 16, and the blower 18, so as to partition the upper and lower parts of the air conditioning unit 15. Below the air purifier 88 and in front of the blower 18 is the mixing section 89, where the air drawn in from the intake grille 16 (air mixed at the stair landing 11 with return air from living and non-living rooms and introduced outdoor air) is mixed with the bypass airflow 47 that bypasses the indoor unit 17 and flows in instead of being drawn in, and the discharge airflow 48 blown out from the indoor unit 17 of the air conditioner A13. The fan (not shown) of the blower 18 blows out the discharge airflow 48 from the indoor unit 17 and the bypass airflow 47 that bypasses the intake louver 16 and flows into the indoor unit 17 without being drawn in, and passes them through the air purifier 88 to purify the air. The conditioned air mixed in the mixing unit 89 is then drawn in through the intake port 55, further purified by the blower filter 56, and flows into the ducts 30, 31, 32, 33, 34, etc. Therefore, fresh outdoor air from the heat exchange ventilation unit 50 and the returned conditioned air are converted into fresh, clean conditioned air with a temperature difference smaller than the temperature difference between the temperature of the air blown out by the indoor unit 17 and the temperature of the living room, non-living room, etc., by the air conditioner A13 and blower 18 in the return compartment, the air conditioning unit 15, and sent to the living room and non-living room for air conditioning. Furthermore, the air purifier 88 may be omitted if it affects the airflow rate of the blower 18 due to airflow resistance, etc.

[0033] Figure 3 is a longitudinal cross-sectional view of the indoor unit 17 of the air conditioner A13 in Embodiment 1 of the present invention. Air drawn in from the intake ports 82 on the top and front of the indoor unit 17's casing is purified by the indoor unit filter 83, heat is exchanged with the refrigerant in the indoor heat exchanger 91, and then blown out by the indoor fan 90 through the outlet 84 in the direction the louvers 94 are facing. The A13 air conditioner has three operating modes: cooling, heating, and reheat dehumidification. The indoor heat exchanger 91 is designed so that the characteristics of the refrigerant flowing through it change depending on the operating mode, and its role switches accordingly. In other words, during cooling cycle operation, the indoor heat exchanger 91 functions as an evaporator through which low-temperature, low-pressure refrigerant flows, and during heating cycle operation, the indoor heat exchanger 91 functions as a condenser through which high-temperature, high-pressure refrigerant flows. Furthermore, during winter heating mode operation, when frost forms on the outdoor heat exchanger (not shown) of the outdoor unit (not shown), the indoor heat exchanger 91 functions as an evaporator through which low-temperature, low-pressure refrigerant flows during the reverse cycle defrosting operation to melt the frost. When the surface temperature of the indoor heat exchanger 91 (evaporator) falls below the dew point temperature of the intake air during cooling cycle operation or reverse cycle defrosting operation, the temperature and absolute humidity of the air that passes through it decrease, and the condensed water (dehumidified water) that forms on the surface of the heat exchanger 91 (evaporator) flows into the drain pan 93 below the heat exchanger 91 (evaporator) and is drained outside via a drain hose (not shown). The indoor heat exchanger 91 is equipped with an indoor heat exchanger temperature sensor 92 that detects the temperature of the indoor heat exchanger 91 as the temperature of the refrigerant, and is connected to an electrical transmission unit (not shown) inside the indoor unit 17.

[0034] Figure 4 is a horizontal cross-sectional view of the outdoor unit 19 and snow cover 74 of the air conditioner A13 in Embodiment 1 of the present invention. The casing of the outdoor unit 19, when viewed from above, is divided into left and right spaces by a partition plate 96. The right side contains a compressor 97, an expansion valve (not shown), a four-way valve 98, etc., which are connected to the outdoor heat exchanger 99 (described later) by piping, and to the indoor unit 17 by refrigerant piping, through which the refrigerant flows. Above these is an electrical unit (not shown) that drives and controls the compressor 97, etc. The left side contains the outdoor heat exchanger 99 and an outdoor fan 100. The outdoor fan 100 draws in outdoor air from the intake port 101, exchanges heat with the refrigerant in the outdoor heat exchanger 99, and blows it out from the outlet port 102. The snow cover 74 is installed to surround the casing of the outdoor unit 19 and is divided into an upper cover (not shown), a rear cover 105, and a side cover 106. It is connected in the order of an exhaust duct C (not shown), a through duct (not shown), a connecting duct (not shown), and the upper cover (not shown). The exhaust from the heat exchange ventilation unit (not shown) flows into the snow cover 74, flows from the upper cover to the rear cover 105 and the side cover 106, and together with the outdoor air, passes through the intake port 101, undergoes heat exchange in the outdoor heat exchanger 99, and is blown out from the outlet port 102. An outdoor temperature sensor 110 is provided at the intake port 101 of the outdoor unit 19 to detect the temperature of the outdoor air being drawn in, and is connected to the electrical unit.

[0035] Figure 5 is a perspective view of the outdoor unit 19 and snow cover 74 of the air conditioner A13 in Embodiment 1 of the present invention, taken from diagonally above the rear. The snow cover 74 is installed to surround the casing of the outdoor unit 19, and the upper cover 107, the rear cover 105, and the side cover 106 are internally connected. The upper cover 107 is connected to the through duct 72, which is connected to the exhaust duct C (not shown), by a weather-resistant and heat-insulating connecting duct 73. The rear cover 105 has an opening on the lower rear side of the outdoor unit 19, and the side cover 106 also has an opening on the lower side of the outdoor unit 19. When the outdoor fan (not shown) is operated, outdoor air is drawn in through these openings, and the exhaust from the heat exchange ventilation unit (not shown) that flows into the interior of the upper cover 107 merges with this outdoor air. Together, they pass through the intake port 101 and undergo heat exchange in the outdoor heat exchanger 99. The snow cover 74 is generally used to cover the outdoor heat exchanger 99 from above in order to prevent a decrease in heating capacity and energy consumption efficiency when snow directly adheres to the outdoor heat exchanger 99 during snowfall in cold regions, freezes, and grows, preventing air from passing through the outdoor heat exchanger 99. However, in Embodiment 1 of the present invention, the structure is designed to efficiently draw the exhaust air after heat exchange from the heat exchange ventilation unit (not shown) into the outdoor heat exchanger 99.

[0036] Figure 6 is a refrigeration cycle diagram of air conditioner A13 in Embodiment 1 of the present invention. Air conditioner A13 has an indoor unit 17 and an outdoor unit 13 connected by refrigerant piping and electrical wiring, and has a heat pump type refrigeration cycle. In other words, the refrigerant is connected by piping so that it passes through the compressor 97, the four-way valve 98, the outdoor heat exchanger 99 or the indoor heat exchanger 91, the expansion valve 103, the indoor heat exchanger 91 or the outdoor heat exchanger 99, and the four-way valve 98, and returns to the compressor 97, thus forming a refrigeration cycle. During cooling cycle operation in cooling mode, the four-way valve 98 is controlled so that the refrigerant follows the solid arrow. The compressor 97 is driven to discharge high-pressure, high-temperature gaseous refrigerant, which enters the outdoor heat exchanger 99. The outdoor fan 100 operates to convert the refrigerant into high-pressure, low-temperature liquid refrigerant in the outdoor air. This is then reduced in pressure by the expansion valve 103 to become low-pressure, low-temperature two-phase refrigerant, which enters the indoor heat exchanger 91. The indoor fan 90 operates to exchange heat with the indoor air to a low temperature, converting it back into low-pressure, low-temperature gaseous refrigerant, which returns to the compressor 97 via the four-way valve 98. This process is repeated. During heating mode operation, the system operates in a heating cycle, controlling the four-way valve 98 so that the refrigerant follows the dotted arrow. The compressor 97 drives the discharge of high-pressure, high-temperature gaseous refrigerant, which enters the indoor heat exchanger 91. The indoor fan 90 operates to heat-exchange the indoor air to a high temperature, converting the refrigerant into high-pressure, low-temperature liquid refrigerant. This is then reduced in pressure by the expansion valve 103, becoming low-pressure, low-temperature two-phase refrigerant, which enters the outdoor heat exchanger 99. The outdoor fan 100 operates to convert the refrigerant back into low-pressure, low-temperature gaseous refrigerant in the outdoor air, and this process is repeated, returning to the compressor 97 via the four-way valve 98. Furthermore, in winter when the outdoor temperature is low, if the heating mode operation continues and the heating cycle operation is continued, the evaporation temperature of the outdoor unit heat exchanger 99 will decrease, and frost or ice will gradually form. Even if the outdoor fan 100 is operated, the flow of outdoor air will worsen, and the frost or ice on the outdoor heat exchanger 99 will grow. When the entire outdoor heat exchanger 99 is covered in frost and ice, the evaporation temperature and condensation temperature will also decrease, and the heating capacity and energy consumption efficiency will decrease, so a reverse cycle defrosting operation is performed. In addition to reverse cycle defrosting operation, there are other methods of defrosting operation such as hot gas defrosting operation, but in the embodiment of the present invention, it basically refers to a reverse cycle, that is, a reverse cycle defrosting operation that changes the flow of the refrigerant from a heating cycle to a cooling cycle. In reverse cycle defrosting operation, the refrigerant is circulated in the cooling cycle, so the four-way valve 98 is controlled so that the refrigerant follows the solid arrow, and the compressor 97 is driven to discharge high-pressure, high-temperature gaseous refrigerant, which enters the outdoor heat exchanger 99, stopping the outdoor fan 100 and further raising the condensation temperature. The total heat generated when the refrigerant becomes high-pressure, low-temperature liquid refrigerant melts the frost and ice that has accumulated on the outdoor heat exchanger 99, and the refrigerant is depressurized by the expansion valve 103 to become low-pressure, low-temperature two-phase refrigerant, which enters the indoor heat exchanger 91, usually stopping the indoor fan 90, and the refrigerant becomes low-pressure, low-temperature gaseous refrigerant due to the indoor air surrounding the indoor heat exchanger 91, and returns to the compressor 97 from the four-way valve 98, and this process is repeated. In heating mode operation, the interval between the heating cycle operation time and the reverse cycle defrosting operation time is at least 50 minutes for the heating cycle operation and 10 minutes for the reverse cycle defrosting operation. In the case of heavy snowfall during the harsh winter, and under poor installation conditions for the outdoor unit 19, frost and ice on the outdoor heat exchanger 99 can grow rapidly. After 50 minutes of heating cycle operation, frost and ice may protrude from the surface of the outdoor heat exchanger 99, causing the outdoor unit 19 to resemble a snowman. In such cases, the subsequent 10 minutes of reverse cycle defrosting operation will not completely melt the frost and ice on the outdoor heat exchanger 99, and restarting the heating cycle operation will worsen the frost and ice formation even further than described above. If the outdoor heat exchanger 99 is in such a poor state of frost and ice formation, even if the outdoor fan 100 is operated, the outdoor air cannot pass through the outdoor heat exchanger 99. As a result, the refrigerant inside the outdoor heat exchanger 99 cannot exchange heat with the outdoor air, and the evaporation temperature drops before returning to the compressor 97. The condensation temperature also drops, and both heating capacity and energy efficiency decrease significantly. Therefore, in reverse cycle defrosting situations like this, by operating the indoor fan, heat exchange is performed between the indoor air and the refrigerant in the indoor heat exchanger 90, raising the evaporation temperature, which is then returned to the compressor 97, raising the condensation temperature, and allowing the frost and ice on the outdoor heat exchanger 99 to melt quickly and completely. An outdoor temperature sensor 110 for detecting the outdoor temperature is provided on the intake side of the outdoor heat exchanger 99, and an indoor heat exchanger temperature sensor 92 for detecting the temperature of the indoor heat exchanger 91 is provided on the indoor heat exchanger 91, and both are connected to an electrical unit (not shown).

[0037] The air conditioner A13 selects its capacity and number of units according to the air conditioning load of Building 1. When selecting the capacity, it is desirable to select an air conditioner or the like that can continue to operate the compressor (not shown) at a lower frequency (around 30 Hz) with a higher COP and has a capacity (appropriate rated capacity, at most 100% of the air conditioning load of the building). This is because it will operate continuously at a lower frequency during stable operation, resulting in more energy savings and stable temperature and humidity without hunting. In the air conditioning unit 15, the blower fan (not shown) of the blower 18 ensures that the blown airflow 48 blown out from the indoor unit 17 and the bypass airflow 47 that bypasses and flows into the indoor unit 17 from the suction gallery 16 without being sucked into the indoor unit 17 are thoroughly mixed in the mixing section 89. An air conditioner with a temperature difference smaller than the temperature difference between the blown air temperature of the indoor unit 17 and the living and non-living rooms is created, and the air volume of the indoor unit 17 is desirably set to 50% or less of the air volume of the blower 18 so that the temperature difference of the air conditioner is within 5K during cooling and within 10K during heating with respect to the target temperatures of the living and non-living rooms.

[0038] The air conditioner is used to uniformly cool the living and non-living rooms to a comfortable temperature by blowing the air conditioner air through a plurality of blowers 18 through a plurality of ducts to the air supply sections 20 provided on the ceilings of the living and non-living rooms and other places. For example, when the area of Building 1 is about 100 m 2 and the ceiling height is 2.5 m, an air conditioner A13 with a cooling capacity equivalent to 4 kW is installed. In the weak wind notch, the air volume of the air conditioner in the indoor unit 17 is 600 m 3 / h. The air volume per blower 18 that blows air into each of the living and non-living rooms is about 100 m 3 / h in the weak air volume, about 150 m 3 / h in the medium air volume, and about 200 m 3 / h in the strong air volume. When there are 11 blowers 18, the total air volume is about 1100 m 3 / h to 2200 m 3 / h, which is more than the air volume of the air conditioner in the indoor unit 17. The air volume of 27 - 55% of the total air volume is set as the air volume of the air conditioner in the indoor unit 17 (weak wind notch). Furthermore, the air conditioning airflow rate is the airflow rate passing through the indoor heat exchanger 91 of the indoor unit 17. In order to blow conditioned air at a large volume to both living and non-living rooms, and to avoid pressure loss due to passing through the indoor heat exchanger 91, if the indoor unit 17 has an airflow path that bypasses the indoor heat exchanger 91, the airflow rate of the bypass airflow path shall be excluded from the air conditioning airflow rate.

[0039] In the above configuration, in order to operate the air conditioning system 2, the remote control of the air conditioner A13 and the switches of the blowers 18 are set appropriately, and the air conditioner A13, the multiple blowers 18, and the heat exchange ventilation unit 50 are operated appropriately. After air conditioning is applied to living rooms 4, the attic 9, the crawl space 12, and other habitable and non-habitable rooms, the returned air is returned to the stair landing 11 through the return air passage by multiple fans 18. Furthermore, fresh outdoor air, purified by the filter box 79 and heat-exchanged with indoor air by the heat exchange unit 50, enters the stair landing 11 through the ventilation air inlet 80. These airs are mixed on the stair landing 11, purified by the filter 25 of the intake grille 16 of the air conditioning unit 15, and then flow into the air conditioning unit 15. The indoor unit 17 draws in a portion of the air that has been drawn in from the intake grille 16 through the intake port 82 and cleans it with the indoor unit filter 83. A portion of the air that has exchanged heat with the refrigerant in the indoor heat exchanger 91 is blown out downwards from the outlet 84. Multiple fans (not shown) of the blowers 18 expel the airflow 48 from the indoor unit 17 and the bypass airflow 47 that bypasses the intake grille 16 and flows into the indoor unit 17 are passed through the air purifier 88 for air purification. The conditioned air mixed in the mixing unit 89 is then drawn in through the intake port 55, further purified by the blower filter 56, and flowed into ducts 30, 31, 32, 33, 34, etc.

[0040] In this embodiment, the airflow of the indoor unit 17 is approximately 600 m³. 3 At a rate of / h, the temperature of the discharged air is approximately 10K relative to the temperature of the intake air during cooling and approximately 20K during heating, but the total airflow of the multiple blowers 18 is approximately 1650m³. 3 Because of / h, of the air drawn in from the intake grille 16, the remaining approximately 1050m3 As a bypass airflow 47 that bypasses the indoor unit 17 of / h, approximately 600m 3 When the discharge airflow 48 at / h is mixed with the mixing unit 89, it reaches approximately 1650m 3 Air-conditioned air, with a temperature of approximately 5K during cooling and approximately 10K during heating, is drawn into multiple fans 18, relative to the temperature of the living and non-living rooms.

[0041] Here, since building 1 is highly airtight and well-insulated, and there is almost no temperature gradient in the return air passage, the temperature of the intake air of indoor unit 17 is almost the same as the temperature of the stair landing 11, the average temperature of the return air from the living room and non-living room, and the average temperature of the living room and non-living room. Approximately 1650 m³ generated within the air conditioning unit 15 3 The conditioned air at / h is kept within approximately 5K during cooling and approximately 10K during heating relative to the temperature of living and non-living rooms, is purified by multiple filters, and includes fresh outside air. The conditioned air is blown by the fan 18 through ducts 30 and other outlets to the living room 4, bedrooms 5, attic 9, underfloor space 12, bathroom 6 and other areas, and is supplied from supply air outlets 20, 21, 23, 24 and bathroom supply air outlet 22 and other outlets, resulting in a very comfortable and uniform temperature and very good air quality throughout the building 1. Furthermore, during the rainy season and summer months, the conditioned air is dehumidified while maintaining the temperature by operating the reheat dehumidification mode of the A13 air conditioner, thus maintaining an appropriate relative humidity level.

[0042] During normal operation, except when bathing or after bathing, the air supply unit (not shown) that blows air into the bathroom air supply unit 22 of the bathroom 6 is stopped, and the bathroom 6 is not air-conditioned. Non-living rooms other than the attic 9, underfloor 12, storage room (not shown), and walk-in closet (not shown) are not air-conditioned. Non-living rooms such as the washroom 7 and toilet 8 are designated as dirty zones where odors and humidity are generated, and ventilation exhaust units 61 and others are provided. A separate ventilation fan 60 is also provided in the bathroom 6. The conditioned air blown into the clean zone living rooms and non-living rooms, etc., and the indoor air merge and are air-conditioned, changing temperature and humidity. In living rooms where people are present, the return air with a slightly higher CO2 concentration is drawn in from the ventilation supply unit 86 and others in the dirty zone, and the odor- and humidity-containing air from the washroom 7 and toilet 8 is discharged outside from the ventilation exhaust unit 61 and others. Bathroom 6 is operated by running the ventilation fan 60 after bathing, when drying clothes, etc., to exhaust the air containing odors and a large amount of moisture to the outside. In this way, the air containing odors and moisture does not flow out into the clean zone, such as the living room and non-living rooms, and even in the dirty zone, the return air with a comfortable temperature and humidity and relatively good air quality flows in as an exchange. This is desirable because it is energy-efficient and helps maintain a comfortable and very good air quality throughout the entire building 1. Furthermore, regarding exhaust, even though heat is recovered by the heat exchange ventilation unit 50, the total heat exchange rate is about 70%, and it is undesirable to actively air condition the dirty zone by exhausting about 30% of the heat.

[0043] However, within building 1, bathroom 6 is usually small and has even better insulation, so the air conditioning load is low, and in reality, even with air conditioning, the power consumption hardly changes. If you want to keep bathroom 6 comfortable at all times, or if you want to actively air condition bathroom 6 for purposes such as bathroom drying or clothes drying, you can reduce the airflow from the fan and blow conditioned air into bathroom 6. In that case, it is desirable to close the bathroom ventilation unit 85 and operate the exhaust fan 60, or open the window 26, to vent some of the conditioned air blown into bathroom 6, along with the odor and moisture-laden air inside bathroom 6, to the outside so that it does not flow back into the washroom 7 from the bathroom ventilation unit 85. Even if it does flow into the washroom 7, it will be exhausted from the washroom 7's ventilation exhaust unit 61, so unless you are bathing or have just finished bathing, the absolute humidity of the air in bathroom 6 is not high, so there is no problem. The reason for air conditioning all non-habitable areas except for the dirty zones such as the attic 9 and crawl space 12 is to ensure uniform air quality with no temperature differences between habitable and non-habitable areas within Building 1, even if Building 1 is a highly insulated house. In particular, the roof and crawl space 12, which occupy a large proportion of the building envelope area, transfer heat and receive solar heat, resulting in a higher air conditioning load than other habitable and non-habitable areas. Without air conditioning, the heat from the ceiling and floor below the attic 9 would prevent uniform temperature and humidity within Building 1. Furthermore, by eliminating temperature differences, heat transfer within Building 1 is reduced, allowing the effects of a highly airtight and highly insulated house to be more fully realized, and the air conditioning load required to maintain a comfortable temperature is actually reduced, resulting in energy savings.

[0044] Furthermore, the heat exchange ventilation unit 50 has a 24-hour ventilation airflow of 125 m³. 3 It is set to / h. In the above operating conditions, after air conditioning the living and non-living rooms, a portion of the return air, which has a comfortable temperature and humidity and good air quality, flows into the entrance 10, the stair landing 11, the corridor (not shown), etc., and flows into the washroom 7 from the ventilation supply unit 86 of the washroom 7 via the heat exchange ventilation unit 50, and flows into the toilet 8 from the ventilation supply unit 87 of the toilet 8. The air from toilet 8 and the incoming return air merge, and after about 50m 3 Air at / h enters the heat exchange ventilation unit 50 from the ventilation exhaust section 62. Therefore, the humid and odor-laden air generated in toilet 8, along with the CO2 in the return air, is mainly exhausted outside, and in its place, return air with a comfortable temperature and humidity and good air quality flows into toilet 8. The air D from bathroom 7 and the incoming return air merge, and the mixture reaches approximately 75m. 3 Air at / h enters the heat exchange ventilation unit 50 from the ventilation exhaust section 61. Therefore, the moisture leaked from the bathroom 6 to the washroom 7, as well as the moisture and odor-containing air D generated in the washroom 7, and the CO2 in the return air are mainly exhausted to the outside, and in exchange, return air with a comfortable temperature and humidity and good air quality flows into the washroom 7. In other words, the heat exchange ventilation unit 50 removes moisture, odors, and CO2 from the bathroom 7 and other areas, up to 125 m³. 3 / h exhausts air, 125m 3The system exchanges the total heat with fresh outdoor air at a rate of / h and introduces it into Building 1, recovering approximately 70% of the total heat from the exhaust air while maintaining very good air quality inside Building 1.

[0045] Furthermore, the exhaust duct C76, which is connected to the exhaust side of the heat exchange unit 50, is connected to the upper cover 107 of the snow protection cover 74 by the through duct 72 and the connecting duct 73. As a result, the exhaust air from the exhaust duct C76, which contains the total heat that was not recovered by the heat exchange unit 50, merges with the outdoor air at the intake port 101 of the outdoor unit 19 through the side cover 106 and the rear cover 105, and is drawn into the outdoor heat exchanger 99, where it exchanges heat with the refrigerant. This improves the COP (Coefficient of Performance), which is the energy consumption efficiency of the air conditioner A13, resulting in greater energy savings. For example, in summer, even if the cooled indoor air (exhaust air) and the outdoor air (outside air) exchange heat in the heat exchange unit 50, only about 50% to 70% of the total heat is usually exchanged. Therefore, exhaust air with less total heat (lower temperature and humidity) than the outdoor air is discharged from the snow cover 74, and this air merges with the outdoor air to become air with less total heat than the outdoor air, which then passes through the outdoor heat exchanger 99, which is a condenser, and the refrigerant exchanges all of the heat. Similarly, in winter, even if the heated indoor air (exhaust air) and the outdoor air (outside air) exchange heat in the heat exchange unit 50, only about 60% to 80% of the total heat is usually exchanged. Therefore, exhaust air with more total heat (higher temperature and humidity) than the outdoor air is discharged from the snow cover 74, and this air merges with the outdoor air to become air with more total heat than the outdoor air, which then passes through the outdoor heat exchanger 99, which is an evaporator, and the refrigerant exchanges all of the heat.

[0046] Furthermore, as mentioned above, the snow cover 74 is used to prevent a decrease in heating capacity and energy efficiency when snow directly adheres to the outdoor heat exchanger 99 during snowfall in cold regions, freezes, grows, and prevents air from passing through the outdoor heat exchanger 99. In this embodiment of the present invention, the airflow rate of the blower 18 is greater than the airflow rate of the indoor unit 17 of the air conditioner A13, and conditioned air is produced with a temperature difference smaller than the temperature difference between the temperature of the air blown out by the indoor unit 17 and the temperatures of the living room and non-living room. This air is then supplied to multiple living rooms and non-living rooms within a highly airtight and highly insulated house. As a result, the entire building 1 maintains a stable and uniform comfortable temperature and humidity, and since the returned air is heat-exchanged with the outside air, the returned air exhausted by the heat exchange unit 50 has more total heat and is more stable than the outside air. During heating mode operation, return air with a higher total heat content (higher temperature and humidity) than the outdoor air is blown out by the heat exchange unit 50 and discharged from the snow cover 74. This return air then merges with the outdoor air, creating air with a higher total heat content than the outdoor air. As it passes through the outdoor heat exchanger 99, which acts as an evaporator, the evaporation temperature rises, reducing frost and ice formation on the outdoor heat exchanger 99. This decreases the frequency and duration of reverse cycle defrosting operation, improving heating capacity and energy efficiency, resulting in more energy-efficient and comfortable air conditioning. Furthermore, in extremely cold weather with heavy snowfall and other harsh outdoor conditions, set the heat exchange ventilation unit 50 to the highest setting for 250m 3 By operating at / h, the exhaust airflow after heat exchange is increased, and the ratio to the outside air is raised, resulting in air with a higher total heat content. This reduces frost and ice formation, making it easier to achieve better performance. In the embodiment of the present invention, the airflow of the outdoor fan 100 of the outdoor unit 19 is approximately 600 m³ during heating. 3 Because of the / h, the outdoor fan 100 provides approximately 0°C at 350m 3 The outdoor air at 0°C ( / h) and the indoor air at approximately 20°C exchange heat with the outdoor air at approximately 0°C with a heat exchange efficiency of 70%, resulting in a temperature of approximately 6°C over 250m². 3 The exhaust from / h merges, and at approximately 2°C, 600m 3 As the mixed air at / h passes through the outdoor heat exchanger 99, the evaporation temperature rises by approximately 2K, and the amount of frost formation decreases. A snow cover 74 is provided on the outdoor unit 19 of the air conditioner A13, and the exhaust from the heat exchange ventilation unit 50 is blown out to the intake side of the snow cover. This makes it easy to install the unit so that the exhaust is blown out to the back and side of the intake of the outdoor unit 19. The exhaust from the heat exchange ventilation unit 50 is reliably drawn into the outdoor heat exchanger 99 of the outdoor unit 19, preventing snow and ice from accumulating on the outdoor heat exchanger 99 during severe winter conditions, and preventing the outdoor heat exchanger 99 from freezing during heating mode operation.

[0047] Figure 7 is a timing chart 1 of the air conditioning system 2 during reverse cycle defrosting operation in Embodiment 1 of the present invention. Based on this figure, the operation, function, and effect of the heating mode operation and reverse cycle defrosting operation in the above configuration will be explained. When air conditioner A13 is operated in heating mode and the heating cycle continues, if the outdoor temperature is low, frost and ice may form on the outdoor heat exchanger 99, blocking it. As a result, even if the outdoor fan 100 is running, outdoor air cannot pass through, the evaporation temperature drops drastically, and heating capacity and energy efficiency decrease. To prevent this, reverse cycle defrosting operation is started. In reverse cycle defrosting operation, the refrigerant is circulated in the cooling cycle, the four-way valve 98 is controlled, and the compressor 97 is driven to discharge high-pressure, high-temperature gaseous refrigerant, which enters the outdoor heat exchanger 99, the outdoor fan 100 is stopped, the condensation temperature is further increased, and the total heat generated when the refrigerant becomes high-pressure, low-temperature liquid refrigerant melts the frost and ice that has accumulated on the outdoor heat exchanger 99. The refrigerant is then depressurized by the expansion valve 103, becoming low-pressure, low-temperature two-phase refrigerant, which enters the indoor heat exchanger 91, where the indoor fan 90 is usually stopped, and the refrigerant becomes low-pressure, low-temperature gaseous refrigerant due to the indoor air surrounding the indoor heat exchanger 91, and this process is repeated back to the compressor 97 through the four-way valve 98. The conditions for starting reverse cycle defrosting are as follows: the electrical unit (not shown) of the outdoor unit 19 detects the elapsed time of the heating cycle and the temperature of the outdoor heat exchanger 99. For example, if the temperature of the outdoor heat exchanger 99 reaches -5°C after 40 minutes of operation, it considers this to be a frosted state and turns on the defrosting signal to control the components of the outdoor unit 19, such as the compressor 97. The same signal is also sent to the indoor unit 17, which is connected to the outdoor unit 19 by electrical wiring, and the electrical unit (not shown) of the indoor unit 17 controls its components. First, simultaneously with the defrost signal being turned ON, the compressor 97 is temporarily stopped, and after the high and low pressures are equalized, the four-way valve 98 is switched from the heating cycle to the cooling cycle, and the compressor 97 is driven in the cooling cycle (direction of the solid line in Figure 6). Simultaneously with the defrost signal being turned ON, the outdoor fan 100 is turned OFF. Then, the outdoor temperature sensor 110 detects the outdoor temperature, and if the outdoor temperature is t2℃ or less, for example 1℃ or less, during the reverse cycle defrost operation, an operation signal for the indoor fan 90 is sent through the electrical section of the indoor unit 17, and the indoor fan 90 is set to the low-wind notch of 300m. 3 The program operates for a set period of time, for example, 8 minutes, using the / h setting. This is because, when the outdoor temperature is low, frost and ice formation on the outdoor heat exchanger 99 is poor, and unless the indoor fan 90 is operated to raise the evaporation temperature and condensation temperature, the reverse cycle defrosting operation will be incomplete, resulting in a deterioration of heating capacity and energy consumption efficiency after the heating cycle operation resumes. As a result, when the outdoor temperature is t2°C or below, for example 1°C or below, the indoor fan 90 is operated, causing the evaporation temperature of the indoor heat exchanger 91 to rise due to heat exchange with warm indoor air of about 20°C, the condensation temperature of the outdoor heat exchanger 99 to rise, the condensation capacity increases, and defrosting can be performed quickly and completely. In the embodiment of the present invention, when the indoor fan 90 is stopped during reverse cycle defrosting operation, the evaporation temperature of the indoor heat exchanger 91 becomes about 0°C or below, and even if the indoor air temperature is about 20°C, the evaporation temperature will drop further from about 0°C or below because the air does not pass through the indoor heat exchanger 91. However, when the indoor fan 90 is turned on at the 300m low wind notch... 3 Even when operating at / h, indoor air at approximately 20°C passes through the indoor heat exchanger 91 and exchanges heat with the refrigerant, causing the evaporation temperature to rise from approximately 0°C. Depending on the reverse cycle defrosting operation time, it will reach approximately 5°C or higher at the end of the reverse cycle defrosting operation. Accordingly, the condensation temperature of the outdoor heat exchanger 99 also rises, increasing the condensation capacity and enabling quick and complete defrosting.

[0048] If the outdoor temperature is higher than t2℃, the indoor fan 90 will be stopped. This is because the frost formation on the outdoor heat exchanger 99 is normal, the condensation temperature will rise sufficiently even without operating the indoor fan 90, the reverse cycle defrosting operation can be performed completely, and the opportunities to operate the indoor fan 90 are limited as much as possible. When the outdoor temperature is higher than a certain temperature, the condensation temperature of the outdoor heat exchanger 99 during reverse cycle defrosting operation is high, making it highly likely that defrosting can be completed completely without needing to operate the indoor fan 90 of the air conditioner A13 or raise the evaporation temperature of the indoor heat exchanger 91. The indoor fan 90 is only operated when the outdoor temperature is low and there is a possibility that defrosting will be incomplete, so throughout the year there will be little to no feeling of cold air or temperature drop, improving comfort. In this embodiment of the present invention, the operation of the indoor fan 90 during reverse cycle defrosting is controlled by the electrical unit based on the outdoor temperature detected by the outdoor temperature sensor 110. However, for air conditioners designed for cold climates, the fan may always operate for a fixed period of time during reverse cycle defrosting. If, due to the installation conditions of the outdoor unit, there is a lot of frost or ice formation and the reverse cycle defrosting operation becomes incomplete, the system may be able to switch on-site between stopping the indoor fan during reverse cycle defrosting and operating the indoor fan for a fixed period of time using a switch on the electrical unit of the outdoor or indoor unit. Normally, the indoor fan is stopped during reverse cycle defrosting, and the system may be able to switch to operating the indoor fan for a fixed period of time during reverse cycle defrosting according to the user's preference by double-pressing a button on the remote control. This ensures that the indoor fan is operated only when there is a lot of frost or ice formation and the reverse cycle defrosting operation becomes incomplete due to the installation conditions of the outdoor unit. This allows for easy operation of the indoor fan on-site during installation or when such conditions arise, enabling complete defrosting. Multiple fans 18 continue to operate at the same airflow rate as during the heating cycle operation. If the fans 18 are stopped during the reverse cycle defrosting operation, it is good that conditioned air will not flow into living rooms or non-living rooms, but the air inside the air conditioning unit 15 will stagnate, the air blown out from the indoor unit 17 will cool the inside of the air conditioning unit, the temperature of the air drawn in by the indoor unit 17 will also decrease, the evaporation temperature of the indoor heat exchanger 91 will gradually decrease, and the condensation temperature of the outdoor heat exchanger 99 will also decrease, increasing the likelihood that the reverse cycle defrosting operation will be incomplete. However, if the volume of the air conditioning unit 15 is sufficient, it is permissible to reduce the airflow rate of the fans 18 in advance during the heating cycle operation before the reverse cycle defrosting operation, as this will raise the evaporation temperature to some extent and further reduce the feeling of cold air. For example, when operating in heating mode during severe winter conditions, the airflow of the fan 18 is pre-set to a low airflow of 100 m³. 3 By reducing the rate to approximately / h, slightly increasing the discharge temperature at the air supply unit 20, etc., and operating continuously for 24 hours, heat will be stored throughout the entire building 1 during that time. During the reverse cycle defrosting operation, the discharge velocity from the air supply unit 20, etc. will slow down. Therefore, if the air supply unit 20, etc. is installed on the ceiling, the possibility of it directly hitting people will decrease, and they will feel less cold. The airflow rate of the blower 18 is set to a low airflow rate of 100 m³. 3 Even at / h, the total airflow is 1100m³ 3 Because there is a / h setting, the airflow of indoor unit 17 is set to low wind notch 600m 3 / h, light wind, notch 300m 3 Even at / h, the airflow from the indoor unit 17 is approximately 55% to 27% of the airflow from the blower 18, so there is no problem. The conditions for stopping the reverse cycle defrosting operation are determined by detecting the reverse cycle defrosting operation time and the temperature of the outdoor heat exchanger 99. For example, if the reverse cycle defrosting operation time is 7 minutes and the temperature of the outdoor heat exchanger 99 reaches 5°C, defrosting is considered complete, the defrosting signal is turned OFF, the compressor 97 is temporarily stopped, the pressure is equalized, the four-way valve 98 is returned to the heating cycle, the compressor 97 is driven to flow the refrigerant in the heating cycle (in the direction of the dotted line in Figure 6), and at the same time the outdoor fan 100 is turned ON. Simultaneously with turning off the defrosting signal, the indoor fan 90 is temporarily stopped, and thereafter, the indoor fan 90 is controlled and operated under normal heating cycle operation conditions. The maximum operating time for the reverse cycle defrosting operation is predetermined, for example, 10 minutes.

[0049] During reverse cycle defrosting operation, operating the indoor fan 90 causes cold air to be blown into the air conditioning unit 15, lowering the temperature of the mixed air, which is the conditioned air. However, multiple blowers 18 distribute this air to almost all habitable and non-habitable rooms in the building 1. Since these habitable and non-habitable rooms have a volume several times larger than a single habitable room that a typical wall-mounted air conditioner targets, the temperature drop in multiple habitable and non-habitable rooms during reverse cycle defrosting operation is reduced. Furthermore, the airflow velocity of the air supplied from the air supply units 20 and other outlets in the habitable and non-habitable rooms is lower than that of the air outlets in a typical wall-mounted air conditioner, thus mitigating the feeling of cold air that people experience. In this embodiment of the present invention, there are 11 blowers 18, 11 air supply units 20, and others, and there are also 11 living rooms and non-living rooms. Therefore, compared to a typical wall-mounted air conditioner that air-conditions one living room, this embodiment air-conditions approximately 10 times the volume. If the indoor unit 17 draws in 20°C air and blows out 10°C air, a simple calculation shows that the temperature difference between the living room and non-living room is approximately 1K, which is very small. Regarding the discharge air velocity, while a typical wall-mounted air conditioner has a discharge air velocity of approximately 2m / s to 4m / s, the discharge air velocity of the air supply units 20 and others is approximately 1m / s. Furthermore, while the air conditioner is mounted on the wall, the air supply units 20 and others are basically mounted on the ceiling, so the air is less likely to blow directly on people, and even if it does, the feeling of coldness is less. Furthermore, since the airflow from the multiple blowers 18 is greater than the airflow from the indoor unit 17 of the air conditioner A13, conditioned air is produced with a temperature difference smaller than the temperature difference between the temperature of the air blown out by the indoor unit 17 and the temperatures of the living room and non-living room, and this air is blown into the living room and non-living room. As a result, during reverse cycle defrosting operation, the conditioned air becomes significantly hotter than the air blown out by the indoor unit 17, further reducing the temperature drop between the living room and non-living room, and further mitigating the feeling of cold air that people experience. In this embodiment of the present invention, the airflow rate of the multiple blowers 18 is 1650 m³ 3 For / h, the air conditioning airflow of indoor unit 17 is set to the low-wind notch setting of 300m 3 The temperature is / h, and during reverse cycle defrosting operation, the air intake grille 16 of the air conditioning unit 15 is approximately 20°C and 1650m 3 / h draws in return air, approximately 10°C, 300m from indoor unit 17 3 Outlet airflow of 48 / h at 20°C, 1350m 3 The bypass airflow 47 at / h is mixed in the mixing section 89, resulting in a temperature of approximately 18°C ​​and a flow rate of 1650m. 3 The air is conditioned at a temperature of / h and blown into living and non-living spaces, so the temperature drop between living and non-living spaces is less than the aforementioned temperature drop of approximately 1K, and the feeling of cold air that people perceive is further mitigated. Furthermore, when the outside temperature is t2℃ or lower, the indoor fan 90 is set to the maximum airflow setting of 900m (strong wind notch). 3 It is also acceptable to operate at / h. In this case, when the outdoor temperature is t2°C or lower, for example 1°C or lower, the indoor fan 90 is operated in high-wind mode. As a result, the evaporation temperature of the indoor heat exchanger 91 rises more quickly due to heat exchange with the large amount of warm indoor air at about 20°C from the heating operation. The condensation temperature of the outdoor heat exchanger 99 rises more quickly, increasing the condensation capacity and allowing defrosting to be performed more quickly and completely. Consequently, the evaporation temperature of the indoor heat exchanger 91 increases, and the temperature of the mixed air, which is the conditioned air, also rises. Furthermore, when operating at maximum airflow, the louvers 94 of the indoor unit 17 should be angled downwards from horizontal to an angle of 80° to 90°. As a result, even when the indoor fan 90 is operated at a high-wind setting with a long reach, the discharge airflow 48 from the intake grille 16 does not flow out of the air conditioning unit 15, the temperature of the stair landing 11 does not drop, and people who are there do not feel the cold air directly hitting them. Furthermore, because the discharge airflow 48 flows directly to the mixing unit 89, the wind speed is high, turbulence is generated, and mixing with the bypass airflow 47 is promoted, resulting in a more uniform temperature of the conditioned air drawn into many blowers 18, and the temperature drop is less and more stable.

[0050] Furthermore, the heat exchange ventilation unit 50 introduces outside air into the building 1 after heat exchange with the indoor air in the washroom 7 and toilet 8, which are so-called dirty zones that do not have an air supply unit 20 or other parts that blow out conditioned air. Then, during the reverse cycle defrosting operation, even if the indoor fan 90 operates and the conditioned air generated by the air conditioning unit 15 becomes cold, that conditioned air is not blown into the washroom 7 and toilet 8, so the temperature of the washroom 7 and toilet 8 is maintained for a while at the temperature it was at before the reverse cycle defrosting operation. Since the air at that temperature exchanges heat with the outside air, the outside air after heat exchange is close to the temperature of the indoor air before the reverse cycle defrosting operation, and is higher than the temperature of the air blown out by the indoor unit 17. It is blown out from the ventilation air supply vent 80 and drawn into the air conditioning unit 15 from the intake grille 16, thus suppressing the temperature drop of the conditioned air generated by the air conditioning unit 15. In Embodiment 1 of the present invention, if the temperature of the living room and non-living room before the reverse cycle defrosting operation is approximately 20°C, the indoor air temperature of the washroom 7 and toilet 8 will remain approximately 20°C for a while during the reverse cycle defrosting operation. The outdoor air, which is approximately 0°C and has been heat-exchanged with this air, will rise to approximately 14°C, and 125m 3 / h (24-hour ventilation) or 250m 3 The air at / h (strong notch) is drawn from the intake grille 16 into the air conditioning unit 15. Meanwhile, since the temperature of the air blown out by the indoor unit 17 is approximately 10°C, the temperature drop of the conditioned air generated by the air conditioning unit 15 is slightly suppressed. Furthermore, the reverse cycle defrosting operation time is shortened, and the heating capacity and energy efficiency after the reverse cycle defrosting operation are improved. Therefore, even if the air conditioning load and power consumption increase to compensate for the temperature drop in living and non-living rooms due to the operation of the indoor fan 90 during the reverse cycle defrosting operation, overall energy savings are achieved.

[0051] (Embodiment 2) Figure 8 is a timing chart of the air conditioning system 202 during reverse cycle defrosting operation in Embodiment 2 of the present invention. This second embodiment differs from the first embodiment in its control configuration and other aspects, resulting in different operation and effects. Below, only the parts that differ from the first embodiment will be described; the parts that are not described are basically the same as the first embodiment. The air conditioning system 202 of Embodiment 2 differs from Embodiment 1 in that it controls the indoor fan 90 during reverse cycle defrosting operation and has different electrical components (not shown). In other words, including during heating cycle operation, the indoor heat exchanger temperature sensor 92 detects the temperature of the indoor heat exchanger 91, and during reverse cycle defrosting operation, if the temperature of the indoor heat exchanger 91 is t1℃ or lower, for example, -5℃ or lower, an operation signal is sent to the indoor fan 90, and the indoor fan 90 is set to the low-wind notch of 300m 3 The program runs for a set period of time, for example, 5 minutes, using the / h setting. If the temperature of the indoor heat exchanger 91 is higher than a certain temperature, the evaporation temperature of the indoor heat exchanger 91 during reverse cycle defrosting is high. Therefore, even without operating the indoor fan 90 of the indoor unit 17 of the air conditioner A13 to further raise the evaporation temperature of the indoor heat exchanger 91, the condensation temperature of the outdoor heat exchanger 99 is also sufficiently high, and there is a high probability that the reverse cycle defrosting operation can be completed completely. The indoor fan 90 is only operated when the temperature of the indoor heat exchanger 91 is low and there is a possibility that the reverse cycle defrosting operation will be incomplete. As a result, the reverse cycle defrosting operation is performed quickly and completely, and throughout the season there is little to no feeling of cold air or temperature drop, improving comfort.

[0052] (Embodiment 3) Figure 9 is a timing chart of the air conditioning system 302 during reverse cycle defrosting operation in Embodiment 3 of the present invention. This third embodiment differs from the first embodiment in the configuration of the blower, etc., and as a result, its operation and effects are different. Below, only the parts that differ from the first embodiment will be described, and the parts that are not described are basically the same as the first embodiment. The air conditioning system 302 of Embodiment 3 differs from Embodiment 2 in that, instead of multiple blowers 18, it has one large blower 218 with the same total airflow capacity as the blowers, and connects to a thick duct, which is then branched into multiple thinner ducts along the way, connecting to the air supply sections of the living and non-living rooms. If the large blower 218 is of the intermediate duct fan type and concealed, it is not necessary to install multiple blowers 18 inside the air conditioning unit 15. This reduces the floor area required for installation of the air conditioning unit 15, and if it can be installed in the ceiling space, under the floor, between floors, under the stairs, etc., the usable space within the building increases. Furthermore, instead of using thick ducts, if a chamber constructed of wood, metal, etc., to prevent air leakage is used inside the space between floors, in the ceiling, under the floor, or within walls, a large blower can be connected upstream of it, and thin ducts connecting to the air supply points of living and non-living rooms can be connected downstream. This simplifies installation work and makes renovation and remodeling work easier.

[0053] (Embodiment 4) Figure 10 is a timing chart of the air conditioning system 402 during reverse cycle defrosting operation in Embodiment 4 of the present invention. This fourth embodiment differs from the first embodiment in its operating method, resulting in different operation and effects. Below, only the parts that differ from the first embodiment will be described; the parts that are not described are basically the same as the first embodiment. In the air conditioning system 402 of Embodiment 4, the operating method of the indoor unit 46 of the air conditioner B45 installed in the living room 4 and the ventilation fan 60 installed in the bathroom 6 are different from those of Embodiment 1. In other words, during the harsh winter months, when the outside temperature is low and a large amount of frost and ice formation is expected, the indoor unit 46 of air conditioner B45 is also set to operate in heating mode in advance. Furthermore, regarding the blower 18, for living room 4, the airflow rate was set to 200m in advance. 3 The airflow should be set to approximately / h, and other living spaces such as bedroom 5 and non-living spaces such as under the floor 12 should be set to a low airflow of 100m³. 3 It should be around / h. While it might seem that operating both air conditioners A13 and B45 in heating mode would increase power consumption, if the heating capacity is sufficient, both will reach the set temperature and the thermostat will turn off. If air conditioner A13's heating capacity is insufficient, B45 will compensate for it, resulting in constant comfort, and in many cases, the increase in power consumption will be minimal. When air conditioner A13 reaches the defrosting conditions and issues a defrosting signal, and the outdoor temperature is below t2℃, the indoor fan 90 is operated. Even if a temperature drop occurs in the living room or non-living room, the heating mode operation of air conditioner B45 in living room 4, with the set temperature slightly increased, will cause living room 4 to reach the set temperature, preventing a temperature drop in living room 4. The large volume of return air from living room 4 passes through the exhaust section 40, through the entrance 10 and the stair landing 11, and flows into the air conditioning unit 15, which is then drawn in by the indoor unit 17. As a result, the temperature of the air blown out by the indoor unit 17 also rises, and the temperature of the conditioned air generated by the air conditioning unit 15 also rises, further mitigating the temperature drop in other living rooms and non-living rooms. Furthermore, during reverse cycle defrosting operation, the airflow velocity from the air supply units 21, etc., in rooms other than living room 4 and non-living rooms slows down. Therefore, if the air supply units 21, etc., are located on the ceiling, the possibility of them directly hitting people decreases, making it less likely for people to feel the cold air. Furthermore, the reverse cycle defrosting time is shortened, and the heating capacity and energy efficiency after the reverse cycle defrosting operation are improved. As a result, even though the indoor fan 90 operates during the reverse cycle defrosting operation, increasing the air conditioning load and power consumption to respond to temperature drops in living and non-living rooms, and the air conditioner B45 operates in heating mode, resulting in increased power consumption, overall energy savings are achieved. Furthermore, if the bathroom 6's ventilation fan 60 is set to a low setting in advance during the coldest part of winter when the outside temperature is low and a large amount of frost and ice is expected, even if slightly cold conditioned air is blown out from the bathroom air supply unit 22 during the reverse cycle defrosting operation, the ventilation fan 60 will exhaust it outside along with the air inside the bathroom. As a result, the cold return air from the bathroom 6 will not return to the air conditioning unit 15, further reducing the temperature drop in living and non-living rooms. By blowing slightly cool air from the air-conditioned room during reverse cycle defrosting into non-living spaces such as bathroom 6, and then exhausting it outside with a ventilation fan, the temperature drop and the feeling of cold air in living spaces can be mitigated. If there is no exhaust fan 60 in bathroom 6, closing the bathroom ventilation unit 85 and slightly opening the window 26 of bathroom 6 will push the amount of air in the bathroom corresponding to the conditioned air blown out from the bathroom air supply unit 22 to the outside. In this embodiment, the bathroom 6 is equipped with a bathroom air supply unit 22, a ventilation fan 60, and a window 26. During heating mode operation, including reverse cycle defrosting, the ventilation fan 60 is operated and the window 26 is opened. However, air supply units, ventilation fans, and windows may also be installed in non-living rooms such as the washroom 7, toilet 8, kitchen (not shown), attic 9, entrance hall 10, stair landing 11, corridor (not shown), and underfloor space 12, and similar operation may be performed.

[0054] (Embodiment 5) Figure 11 is a timing chart of the air conditioning system 502 during reverse cycle defrosting operation in Embodiment 5 of the present invention. This embodiment 5 differs from embodiment 4 in the configuration of the blower, etc., and as a result, its operation and effect are different. Below, only the parts that differ from embodiment 4 will be described, and the parts that are not described are basically the same as embodiment 4. The air conditioning system 502 of Embodiment 5 differs from Embodiment 4 in that, instead of having multiple blowers 18 as in Embodiment 3, it has one large blower 218 with the same airflow as the total airflow, and connects to the air supply sections of living and non-living rooms by connecting a thick duct, which is then branched into multiple thinner ducts along the way. Therefore, its action and effect are the same as those of Embodiments 3 and 4.

[0055] (Embodiment 6) Figure 12 is a cross-sectional view of a building showing the configuration of an air conditioning system in Embodiment 6 of the present invention. This embodiment 6 differs from embodiment 1 in its configuration, including the duct and blower, and as a result, its operation and effects are different. Below, only the parts that differ from embodiment 1 will be described; the parts that are not described are basically the same as embodiment 1. As shown in the diagram, the air conditioning system 602 installed in building 601, which is a highly airtight and highly insulated house, provides air conditioning and ventilation to living rooms and non-living rooms within building 601, including the living room 4, bedroom 5, children's room (not shown), bathroom 6, washroom (not shown), toilet 8, kitchen (not shown), attic 9, entrance 10, second-floor stairwell 611, corridor (not shown), underfloor space 12, storage room (not shown), walk-in closet (not shown), and the so-called inter-floor space 607 between the ceiling (not shown) of the first floor and the floor (not shown) of the second floor.

[0056] In the second-floor hall 611 of the staircase, an air conditioning unit (return section) 615 is provided as a return section that creates conditioned air and blows it to living rooms, non-living rooms, etc. The air conditioning unit 615 is equipped with an intake grille 16 into which the conditioned air from living rooms and non-living rooms etc. flows in as return air, an air conditioner D613 having an indoor unit 617 connected to an outdoor unit 619 installed outside by refrigerant piping and electrical wiring (not shown) and having an indoor heat exchanger (not shown) and an indoor fan (not shown) inside, and a plurality of blowers 618 that blow conditioned air to living rooms and non-living rooms etc. The air conditioner D613 has a remote control (not shown) that can operate / stop, switch between cooling / heating / dehumidifying modes, set airflow, set temperature, set air outlet direction, etc.

[0057] In the living rooms (4), bedrooms (5), attics (9), underfloor spaces (12), bathrooms (6), toilets (8), and children's rooms (not shown), air supply units 620, 621, 623, 624, 628, bathroom air supply unit 622, and toilet air supply unit 627 are provided in the ceilings or floors to blow out conditioned air produced by the air conditioning unit 615. Additionally, there are four more air supply units in other rooms and non-habitable rooms, bringing the total number of units in Building 601 to 11. The air supply units 620 and others are installed in locations such as ceilings, walls, and floors, where the blown conditioned air is less likely to directly hit people and where the temperature distribution between living and non-living spaces is improved. Multiple blowers 618 and air supply units 620, 621, 623, and 624 are connected to each other on a one-to-one basis by multiple ducts 630, 631, 633, and 634. Multiple blowers 618, a bathroom air supply unit 622, and a toilet air supply unit 627 are connected by a duct 632 and a chamber (air passage) 637 located within the inter-floor space 607. Multiple blowers 618, an air supply unit 628, and four other air supply units (not shown) are connected by ducts 636 and other components, as well as a chamber (air supply passage) 638. Chambers (air passages) 637 and 638 are covered above and below by air-conditioned rooms or spaces, and on the front, back, left, and right by exterior walls with insulating materials. Airtight sealing is also applied, mainly to the contact surfaces, resulting in high airtightness and insulation. Therefore, not only within the space between floors 607, but also in the attic 9, under the floor 12, inside walls, rooms, and spaces, as well as under the ceiling and under the stairs, chambers (air passages) 637 and 638 made of wood, metal, etc., may be installed to prevent air leakage and maintain airtightness. In this case as well, the surrounding rooms or spaces must be air-conditioned, covered with insulation, etc., and also have thermal insulation properties. There are 11 blowers 618, the same as the air supply unit 620 and others, each with its own switch (not shown), which allows for temperature control by adjusting the airflow and starting / stopping the blowers 618. The amount of air supplied to each air supply unit 620, etc., is basically determined by the volume of the living room and non-living room where each air supply unit 620, etc. is installed. However, for the attic 9, underfloor space 12, and between floors 607, the amount of air supplied per unit volume is greater than that supplied to living rooms and non-living rooms. This is to improve temperature distribution and comfort by taking into account radiant heat from the roof due to solar radiation and geothermal heat from the ground, and by heating or cooling from above or below the room or space being air-conditioned, such as the attic 9, between floors 607, and underfloor space 12. Specifically, for living rooms and non-living rooms, 2.5m 3 At least 8 meters 3 For areas above / h, including attic 9, underfloor 12, and between floors 607, at least 12m 3 It must be at least / h. As a result, the conditioned air generated in the air conditioning unit 615 is blown by the blower unit 618 through the duct 630 and other chambers (air passages) 637 and other chambers, and is then blown out from the supply air units 620, 628 and other chambers, and the bathroom supply air unit 622 and other chambers into the living room 4, bedroom 5, attic 9, under the floor 12, between floors 607, bathroom 606, children's room, and other areas, forming an air conditioning air passage (not shown).

[0058] In the living room 4, bedroom 5, attic 9, underfloor 12, and other areas which have air supply units 620 and others, exhaust units 40, 41, 643, 644, and others are provided, such as undercuts in doors and vents. The conditioned air blown out from the air supply units 620 and others becomes return air after conditioned the living and non-living rooms, and flows into the corridor (not shown) from the exhaust units 40 and others, and returns to the air conditioning unit (return section) 615 through the entrance 10 and the second-floor hall 611 of the staircase, passing through the intake grille 16. As a result, a return air passage (not shown) is formed, which is an airflow path that returns to the air conditioning unit (return section) 615 from the corridor (not shown), entrance hall 10, stairwell 2nd floor hall 611, etc., via the exhaust sections 40 and other parts of the living and non-living rooms. Then, the air conditioning duct and the return duct are connected to form a circulation path (not shown).

[0059] A heat exchange ventilation unit 650 is installed in the inter-floor space 607 to introduce outside air into the room and to recover all the heat from the indoor air into the outside air when the indoor air is discharged outside, thereby ventilating the entire building 601. The amount of outdoor air introduced and the amount of indoor air discharged, or so-called ventilation airflow, by the heat exchange ventilation unit 650 are, for example, for a floor area of ​​approximately 100m². 2 For a ceiling height of 2.5m and a ventilation rate of 0.5 times / hour, the 24-hour ventilation airflow is 125m³. 3 It becomes / h. In this embodiment, the heat exchange ventilation unit 650 has a 24-hour ventilation airflow of 125 m³. 3 / h, strong notch ventilation airflow 250m 3 At a rate of / h, the total heat exchange rate is approximately 70%. In the ceilings of the toilet 608 and washroom (not shown) within building 601, ventilation and exhaust units 661 and others, such as exhaust grilles, are provided to exhaust air from each non-habitable room, and these are connected to exhaust ducts A666 and others, respectively. Exhaust ducts A666 and others are connected to a heat exchange ventilation unit 650. A ventilation fan 60 is installed in the ceiling of the bathroom 606, and an outdoor exhaust hood 675 is installed in a penetration hole in the exterior wall of the building 601, connected by a duct 665. In this embodiment, a bathroom air supply unit 622 is provided in the bathroom 606. However, if clothes drying or bathroom drying is not performed in the bathroom 606, the bathroom air supply unit 622 does not need to be provided. Furthermore, the ventilation fan 60 is provided along with the bathroom air supply unit 622 to prevent the conditioned air blown into the bathroom 606 from flowing out through the ventilation air supply unit 687 or gaps in the bathroom door into the washroom (not shown), etc., along with the odor and moisture contained in the bathroom, and causing adverse effects on surrounding living and non-living rooms such as condensation and mold growth.

[0060] An exhaust duct B671 is connected to the exhaust side of the heat exchange ventilation unit 650, and is connected to an outdoor exhaust hood 676 installed in a penetration hole in the exterior wall of the building 601. As a result, indoor air is drawn from the ventilation exhaust unit 661 and other components, through the exhaust duct A666 and other components, where all the heat is recovered in the heat exchange unit 650, and then exhausted outdoors through the exhaust duct B671 and the outdoor exhaust hood 676, forming an indoor air exhaust path.

[0061] An outdoor air supply hood 677 is installed in a penetration hole in the exterior wall of building 601 and is connected to a heat exchange ventilation unit 650 by an air supply duct (not shown). In the second-floor hall 611 of the staircase, a ventilation air inlet 680 is provided in front of the intake grille 16 of the air conditioning unit 615, which blows outside air into the building 601, and is connected to a heat exchange ventilation unit 650 by an air supply duct (not shown). As a result, an outdoor air intake path is formed in which outdoor air is introduced from the outdoor air supply hood 677, passes through an air supply duct (not shown), recovers total heat in the heat exchange unit 650, and is introduced into the room through the ventilation air inlet 680 via another air supply duct (not shown). In the toilet 608, washroom (not shown), and bathroom 606, ventilation supply sections 686, 687, etc., such as door undercuts, are provided, which draw some of the return air into each non-living room via a heat exchange ventilation unit 650 and a ventilation fan 60. These are connected to return air passages (not shown), which are air passages that return air to the air conditioning unit (return section) 615 from the washroom (not shown), corridor (not shown), entrance 10, and the second-floor hall 611 of the staircase.

[0062] Regarding toilet 608, the 24-hour ventilation operation of the heat exchange ventilation unit 650 provides some degree of air conditioning, as the return air of the conditioned air used to conditioned each room and space flows into toilet 608 from the ventilation supply unit 686. However, during extreme heat in summer or extreme cold in winter, operating the blower 618 connected to the toilet air supply unit 627 in toilet 608 can reduce the temperature difference between rooms and improve comfort. A portion of the conditioned air blown out from the toilet air supply unit 627 of toilet 608 is exhausted outside by the heat exchange unit 650 through the ventilation exhaust unit 661, and the remainder flows into the entrance 10 etc. through the ventilation supply unit 686. Therefore, after using toilet 608, the exhaust airflow of the heat exchange unit 650 is set to be greater than the airflow of the conditioned air, so that odors etc. after using toilet 608 do not leak into the entrance 10 etc., and are all exhausted outside. In addition, for bathroom 606, a blower 618 connected to the bathroom air supply unit 622 is operated to dry the bathroom after bathing and to dry clothes that have been hung to dry inside bathroom 606. The conditioned air blown out from the bathroom air supply unit 622 of the bathroom 606 may flow into the washroom (not shown) etc. through the ventilation air supply unit 687. Therefore, to prevent high-humidity air from the bathroom 606 from flowing in when drying the bathroom after bathing and when drying clothes, the ventilation fan 60 is operated with an exhaust airflow greater than the airflow of the conditioned air.

[0063] Figure 13 is a longitudinal cross-sectional view of the air conditioning unit 615 in Embodiment 6 of the present invention. The air conditioning unit 615, which is enclosed by walls (including a sealed door) and insulation, is installed in the second-floor hall 611 of the staircase. Above the sealed door (not shown) that is adjacent to the second-floor hall 611 of the staircase, there is an intake grille 16 into which air-conditioned air from living rooms and non-living rooms flows in as return air, and it is equipped with a filter 25. The indoor unit 617 of the air conditioner D613 is located in front of the intake grille 16, at a distance from the back, and the multiple blowers 618 are located in the lower part of the air conditioning unit 615, with their main bodies embedded in the vertical shaft 35 on the back side of the air conditioning unit 615. The indoor unit 617 draws in a portion of the air (a mixture of return air from living and non-living rooms and introduced outside air in the second-floor hall 611 of the staircase) from the intake grille 16 by the blower 618, and uses an indoor fan (not shown) to draw in air from the intake ports 682 on the top and front, cleans it with the indoor unit filter 683, and blows out the air that has exchanged heat with the refrigerant in the indoor heat exchanger (not shown) downwards from the outlet 684. Below the air purifier (not shown), in front of the blower 618, is the mixing section 689, where the air drawn in from the intake grille 16 (air mixed in the second-floor hall 611 of the staircase with return air from living and non-living rooms and introduced outside air) is mixed with the bypass airflow 647 that bypasses the indoor unit 617 and flows in, and the discharge airflow 648 blown out from the indoor unit 617 of the air conditioner D613. The fan (not shown) of the blower 618 blows out the discharge airflow 648 from the indoor unit 617, and the bypass airflow 647 that bypasses the intake grille 16 and flows into the indoor unit 617 without being drawn in, are passed through an air purifier (not shown) for air purification. The conditioned air mixed in the mixing unit 689 is then drawn in through the intake port (not shown), further purified by a blower filter (not shown), and flows into ducts 630, 631, 632, 633, 634, 636, etc. Here, the total airflow rate of the blower 618 is set to be greater than the air conditioning airflow rate of the indoor unit 617. As a result, fresh outdoor air from the heat exchange ventilation unit 650 and the return air of conditioned air are converted into fresh, clean conditioned air with a temperature difference smaller than the temperature difference between the air blown out by the indoor unit 617 and the temperatures of the living room, non-living room, etc., by the air conditioner D613 and blower 618 in the return section, air conditioning unit 615, and sent to the living room and non-living room for air conditioning.

[0064] Figure 14 is a longitudinal cross-sectional view of the indoor unit 617 of the air conditioner D613 in Embodiment 6 of the present invention. In the indoor unit 617, the indoor heat exchanger 91 is divided into two parts, indoor heat exchanger A691 and indoor heat exchanger B695, with an expansion valve B (not shown) between them that can be fully opened by reducing the pressure of the refrigerant. Additionally, the louver 694, which allows for changing the direction of the blown air, consists of two louver plates. The D613 air conditioner has three operating modes: cooling, heating, and reheat dehumidification. Indoor heat exchangers A691 and B695 have the same characteristics and roles for the refrigerant flowing through them, except when operating in reheat dehumidification mode. When operating in reheat dehumidification mode, indoor heat exchanger A691 functions as an evaporator through which low-temperature refrigerant flows, and indoor heat exchanger B695 functions as a reheater through which medium-temperature, medium-pressure refrigerant flows.

[0065] Figure 15 is a refrigeration cycle diagram of the air conditioner D613 in Embodiment 6 of the present invention. In the air conditioner D613, the indoor heat exchanger 91 is divided into two parts, indoor heat exchanger A691 and indoor heat exchanger B695, compared to the heat pump type refrigeration cycle of the air conditioner D13. Between them is an expansion valve B699 that can be fully opened by reducing the refrigerant pressure, and the expansion valve 103 is an expansion valve A698 of the same specifications. During cooling cycle operation in cooling mode and heating cycle operation in heating mode, the expansion valve B699 is fully open, and the characteristics of the refrigerant flowing through indoor heat exchanger A691 and indoor heat exchanger B695 are the same, with the valve functioning as a condenser during cooling cycle operation and as an evaporator during heating cycle operation. During reheat dehumidification cycle operation in reheat dehumidification mode, the refrigerant is circulated in the cooling cycle, expansion valve A698 is fully open, and expansion valve B699 is appropriately throttled. In this manner, indoor heat exchanger B695 functions as a reheater and indoor heat exchanger A691 functions as an evaporator. In other words, the four-way valve 98 is controlled so that the refrigerant follows the solid arrow, and the compressor 97 is driven to discharge high-pressure, high-temperature gaseous refrigerant, which enters the outdoor heat exchanger 99. Next, the outdoor fan 100 is operated to convert the refrigerant into high-pressure, medium-temperature two-phase refrigerant, which then passes straight through the fully open expansion valve A698. This refrigerant then exchanges heat with the indoor air in the indoor heat exchanger B695 via the indoor fan 90, becoming a high-pressure, low-temperature liquid refrigerant. It is then depressurized in the expansion valve B699, becoming a low-pressure, low-temperature two-phase refrigerant, which enters the indoor heat exchanger A691. This refrigerant then exchanges heat with the indoor air via the indoor fan 90, becoming a low-pressure, low-temperature gaseous refrigerant, and the process of returning to the compressor 97 via the four-way valve 98 is repeated. As a result, the air dehumidified and cooled by indoor heat exchanger A691 mixes with the air heated by indoor heat exchanger B695, dehumidifying the indoor air, and the resulting discharge airflow 648, with almost no change in temperature, is blown out from the outlet 684 of indoor unit 617. Furthermore, if the outdoor temperature is low during winter and the heating mode is activated, causing frost or ice to form on the entire outdoor heat exchanger 99, a reverse cycle defrosting operation will be performed. The reverse cycle defrosting operation is the same as in Embodiment 1, in which the refrigerant is circulated in the cooling cycle, but depending on the frosting state of the outdoor heat exchanger 99, the functions of the indoor heat exchanger B695 and other components are controlled in two ways, as will be described later. During heating operation in severe winter conditions, if there is significant frost or ice formation, the expansion valve B699 is fully opened to allow low-pressure, low-temperature two-phase refrigerant to flow into indoor heat exchangers B695 and A691, causing indoor heat exchangers B695 and A691 to function as evaporators. The indoor fan 90 is operated at maximum airflow to exchange heat between the indoor air and the refrigerant in indoor heat exchangers A691 and B695, rapidly raising the evaporation temperature and returning the refrigerant to the compressor 97. This raises the condensation temperature, allowing the frost and ice on the outdoor heat exchanger 99 to melt quickly and completely.

[0066] Figure 16 is a timing chart for reverse cycle defrosting operation of an air conditioning system in Embodiment 6 of the present invention. During normal winter heating operation, if there is not much frost formation, the expansion valve A698 is fully opened, and high-pressure, medium-temperature two-phase refrigerant flows into the indoor heat exchanger B695. Then, the indoor fan 90 is operated at its maximum airflow to exchange heat with the warm indoor air, becoming a high-pressure, low-temperature liquid refrigerant. This is then reduced in pressure by the expansion valve B699, which is set to an appropriate opening, becoming a low-pressure, low-temperature two-phase refrigerant. This refrigerant enters the indoor heat exchanger A691, and again, the indoor fan 90 is operated at its maximum airflow to exchange heat with the warm indoor air, becoming a low-pressure, low-temperature gaseous refrigerant, which is then returned to the compressor 97 through the four-way valve 98. By doing so, the evaporation temperature in the indoor heat exchanger A691 is raised, the condensation temperature in the indoor heat exchanger B698 is raised, and the condensation temperature in the outdoor heat exchanger 99 is raised, allowing the frost and ice on the outdoor heat exchanger 99 to melt quickly and completely.

[0067] In this embodiment, the building area 601 is approximately 100 m² 2 The ceiling height is 2.5m, and an air conditioner D613 with a cooling capacity equivalent to 4kW is installed. The airflow of the indoor unit 617 is 900m in the strong wind setting. 3 / h, 600m with light wind notch 3 / h, light wind notch at 300m 3 The airflow per fan 618, which supplies air to both the living room and the non-living room, is 100 m³ at low speed. 3 / h, 150m at medium airflow 3 / h, strong winds at 200m 3 A system with a volume of 11 fans (618 total) is installed, and the total airflow is 1100 m³. 3 / h~2200m 3 This becomes / h, which is greater than the airflow of indoor unit 617, and when indoor unit 17 is set to the low airflow notch, the airflow will be 27-55% of the total airflow. In the above configuration, in order to operate the air conditioning system 602, the remote control of the air conditioner D613 and the switches of the blowers 618 are set appropriately, and the air conditioner D613, the multiple blowers 618, and the heat exchange ventilation unit 650 are operated appropriately. Here, the airflow of indoor unit 617 is 600 m / s at the low wind setting.3 Assuming a value of / h, the average airflow per fan 618 for the living room (4), bedrooms (5), bathrooms (6), toilets (8), children's room (not shown), and 4 other habitable rooms, as well as non-habitable rooms, is 150m³. 3 Assuming a value of / h, the average airflow rate per blower 618 for the attic 9 and underfloor 12 is 200m³. 3 It is set to / h. Therefore, the temperature of the air blown out by the indoor unit 617 is approximately 10K relative to the intake air temperature during cooling and approximately 20K during heating, while the total airflow of the multiple blowers 618 is approximately 1750 m³. 3 It is / h. Therefore, of the air drawn in from the intake grille 16, approximately 1150m 3 The air bypassing the indoor unit 617 at / h is called the bypass airflow 647 and flows approximately 600m 3 When the discharge airflow 648 at / h is mixed with the mixing section 689, it reaches approximately 1750m 3 For the temperature of the living and non-living rooms at / h, air-conditioned air at approximately 5K during cooling and approximately 10K during heating is drawn into multiple blowers 618, and air-conditions each living room, non-living room, attic 9, underfloor 12, and between floors 607.

[0068] When the air conditioner D613 is operated in heating mode and the heating cycle continues, frost and ice may form on the outdoor heat exchanger 99, especially when the outdoor temperature is low, reducing heating capacity and energy efficiency. To prevent this, reverse cycle defrosting operation is initiated. First, simultaneously with the defrost signal being turned ON, the compressor 97 is temporarily stopped, and after the high and low pressures are equalized, the four-way valve 98 is switched from the heating cycle to the cooling cycle, and the compressor 97 is driven in the cooling cycle. Simultaneously with the defrost signal being turned ON, the outdoor fan 100 is turned OFF, and the outdoor temperature sensor 110 detects the outdoor temperature. If the outdoor temperature is t2℃ or less, for example 1℃ or less, during the reverse cycle defrost operation, an operation signal for the indoor fan 90 is sent through the electrical section of the indoor unit 617, and the indoor fan 90 is set to the strong wind notch of 900m, which is the maximum airflow. 3 The system operates at a constant rate of / h for a set period of time, for example, 5 minutes, with the louvers 694 angled downwards from horizontal to 80° to 90°, and the expansion valve B699 kept fully open. As a result, when the outdoor temperature is t2°C or below, for example 1°C or below, the indoor fan 90 is operated in the strong wind notch, so the evaporation temperature of indoor heat exchangers A691 and B695 rises more quickly due to heat exchange with a large amount of warm indoor air at about 20°C due to heating operation, the condensation temperature of outdoor heat exchanger 99 rises more quickly, the condensation capacity increases, and defrosting can be performed more quickly and completely. If the indoor fan 90 is stopped during reverse cycle defrosting operation, the evaporation temperature of indoor heat exchangers A691 and B695 will be about 0°C or below, and even if the indoor air temperature is about 20°C, the evaporation temperature will drop even further from about 0°C or below because that air does not pass through indoor heat exchangers A691 and B695. However, in the embodiment of the present invention, the indoor fan 90 is operated in the strong wind notch at the maximum airflow of 900m 3 Because it operates at / h, indoor air at approximately 20°C passes through indoor heat exchangers A691 and B695, exchanging heat with the refrigerant. As a result, the evaporation temperature rises rapidly from approximately 0°C, and depending on the reverse cycle defrosting operation time, it reaches approximately 18°C ​​or higher at the end of the reverse cycle defrosting operation. Accordingly, the condensation temperature of the outdoor heat exchanger 99 also rises rapidly, increasing the condensation capacity quickly and enabling faster and more complete defrosting. Multiple blowers 618 continue to operate at the same airflow rate as during the heating cycle.

[0069] If the outside temperature is higher than t2℃, the expansion valve A698 is fully opened, the expansion valve B699 is set to an appropriate opening, and the indoor fan 90 is set to the strong wind notch of 900m, which is the maximum airflow. 3 Because it operates at / h, the indoor heat exchanger B695, which functions as a condenser, exchanges heat with a large amount of indoor air at approximately 20°C, causing the condensation temperature to rise rapidly. Then, the indoor heat exchanger A691, which functions as an evaporator, also operates with the indoor fan 90 at its maximum airflow setting of 900m / h. 3 Because it operates at / h, the liquid refrigerant exchanges heat with a large amount of indoor air at approximately 20°C, causing the evaporation temperature to rise quickly. This rapidly increases the condensation temperature, which is the temperature of the outdoor heat exchanger 99, increasing the condensation capacity and enabling quick and complete defrosting.

[0070] During reverse cycle defrosting operation, operating the indoor fan 90 causes a cold airflow 648 to be blown into the air conditioning unit 615, raising concerns that the temperature of the mixed air, which is the conditioned air, will decrease. However, if the outside temperature is lower than t2℃, the indoor fan 90 of the indoor unit 617 will be set to the maximum airflow notch of 900m. 3 Because it operates at / h, the evaporation temperatures of indoor heat exchangers A691 and B695 become high, and the temperature of the discharge airflow 648 is 300m of the low wind notch in Embodiment 1. 3 When operating at / h, the temperature of the discharge airflow 648 is significantly higher, the temperature of the mixed air (conditioned air) is also higher, and the condensation temperature is higher, so the reverse cycle defrosting time is significantly shortened. For example, with the low wind notch, the maximum temperature of the discharge airflow 648 is 10°C and the reverse cycle defrosting time is a maximum of 8 minutes, whereas with the high wind notch, the maximum temperature of the discharge airflow 648 is 18°C ​​and the reverse cycle defrosting time is a maximum of 5 minutes. Furthermore, since the airflow from the multiple blowers 618 is greater than the airflow from the indoor unit 617 of the air conditioner D613, conditioned air is produced with a temperature difference smaller than the temperature difference between the temperature of the air blown out by the indoor unit 617 and the temperatures of the living and non-living rooms, and this air is then blown into the living and non-living rooms. As a result, during reverse cycle defrosting operation, the conditioned air becomes significantly hotter than the air blown out by the indoor unit 617, resulting in less temperature drop between the living and non-living rooms, and further mitigating the feeling of cold air that people experience. In this embodiment of the present invention, the airflow rate of the multiple blowers 618 is 1750 m³ 3 For / h, the air conditioning airflow of indoor unit 617 is 900m with the strong wind setting. 3 The temperature is / h, and during reverse cycle defrosting operation, the air intake grille 16 of the air conditioning unit 15 is approximately 20°C and 1750m 3 / h draws in return air, approximately 18°C, 900m from indoor unit 617 3 Outlet airflow of 648 / h at 20°C, 850m 3 The bypass airflow 647 at / h is mixed in the mixing section 689, resulting in approximately 19°C and 1750m. 3 The air is conditioned at a rate of / h and blown into living and non-living spaces, resulting in less temperature drop between living and non-living spaces, and further reducing the feeling of cold air that people experience. Furthermore, regarding the airflow rate, for living rooms and non-living rooms, it is 2.5 m³.3 At least 8 meters 3 For areas above / h, including attic 9, underfloor 12, and between floors 607, at least 12m 3 Because the setting is 1 / h or more, the capacity per unit volume of conditioned air in living and non-living rooms where people are often present is about 2 / 3 of the capacity per unit volume of conditioned air in the attic (9), underfloor (12), and between floors (607), where people are rarely present. As a result, the temperature drop between living and non-living rooms is less than approximately 1K, which is very small, and the feeling of cold air is hardly noticeable. Furthermore, the conditioned air blown into the attic 9 and under the floor 12 undergoes minimal temperature changes in the returned air after heating due to heat transfer from the surrounding roof, floor, and insulation materials during heating operation. This air then flows from the exhaust units 643 and 644 into the second-floor stairwell 611 and the entrance 10, and quickly returns to the air conditioning unit 615. Therefore, even if the return air is cooler than the room temperature during startup, other rooms will not feel cold.

[0071] Furthermore, in children's rooms (not shown), bathrooms 606, toilets 608, etc., conditioned air is blown out through chambers (air passages) 637, 638, etc., which have a certain volume and are located within the inter-floor space 607. As the air passes through the chambers (air passages), the temperature drop is further reduced due to the transfer of heat stored in the chambers (air passages), which are surrounded by rooms or spaces that are air-conditioned above and below, and covered on all sides by outer walls with insulating material. Furthermore, a ventilation fan 60 is installed in the bathroom 606, and a ventilation exhaust unit 661 connected to a heat exchange ventilation unit 650 is installed in the toilet 608. When conditioned air is blown out from the bathroom air supply unit 622, the ventilation fan 60 is basically operated, and the heat exchange ventilation unit 650 basically operates continuously for 24 hours. Therefore, the conditioned air blown out from the bathroom air supply unit 622 and the toilet air supply unit 627 mixes with the air inside the bathroom 606 and toilet 608, and is quickly exhausted outside by the ventilation fan 60 and the heat exchange ventilation unit. As a result, even if the conditioned air temperature drops slightly below room temperature due to the reverse cycle defrosting operation, the temperature drop in the bathroom 606 and toilet 608 is very small, there is almost no feeling of cold air, and it does not affect other rooms or spaces. Furthermore, during reverse cycle defrosting operation, the louvers 694 of the indoor unit 617 are facing downwards. As a result, even when the indoor fan 90 of the indoor unit 617 is operated at a high-wind setting with a long reach, the discharge airflow 648 from the intake grille 16 does not flow out of the air conditioning unit 615 to the outside. This prevents a temperature drop in the second-floor hall 611 of the staircase, and if a person is present, they will not feel the cold air directly hitting them. Additionally, the discharge airflow 684 flows directly into the mixing section 689, resulting in a high wind speed and turbulence, which promotes mixing with the bypass airflow 647. This makes the temperature of the conditioned air drawn into the many blowers 618 more uniform, resulting in less temperature drop and greater stability. Even when the indoor fan 90 is set to maximum airflow and the louvers 694 are directed downwards during reverse cycle defrosting operation, the indoor unit 617 is located inside the air conditioning unit 615, so the discharged airflow 648 does not directly hit people and does not affect the room temperature in the space in front of the intake grille 16 of the air conditioning unit 615.

[0072] When the outdoor temperature is higher than t2℃, only the indoor heat exchanger A691 functions as an evaporator, resulting in a smaller evaporation capacity. However, the indoor heat exchanger B695 functions as a condenser, and the indoor fan 90 is operated at the high-wind setting. As a result, the condensation capacity of the indoor heat exchanger B695 increases, and the condensation temperature, which is the temperature of the outdoor heat exchanger 99, rises faster than in Embodiment 1. This increases the condensation capacity and allows for faster and complete defrosting. Furthermore, only indoor heat exchanger A691 functions as an evaporator, resulting in a small evaporation capacity. The temperature drop of the air passing through indoor heat exchanger A691 is minimal. Indoor heat exchanger B695, which functions as a condenser, essentially acts as a reheater, and the air passing through it does not experience a temperature drop. As a result, the discharge airflow 648, which is a mixture of these airs, experiences almost no temperature drop relative to the room temperature, resulting in almost no temperature difference between living and non-living spaces, and virtually no feeling of coldness perceived by people. In other words, when the outdoor temperature is higher than t2°C, it is assumed that less frost will form on the outdoor heat exchanger 99 than when it is lower than t2°C. Therefore, priority is given to preventing a temperature drop in the discharged airflow 648 when the indoor fan 90 is operated during reverse cycle defrosting, rather than to defrosting capacity. However, the defrosting capacity is also increased compared to Embodiment 1, and the defrosting time can be shortened. [Industrial applicability]

[0073] This system enables efficient air conditioning, primarily during heating mode operation, and can be applied to air conditioning in large commercial facilities, hospitals, and other buildings with large floor areas. [Explanation of Symbols]

[0074] 1,601 building 2, 202, 302, 402, 502, 602 Air Conditioning System 4 Living Room 5 Bedrooms 6, 606 Bathroom 7. Bathroom 8,608 toilets 9 Attic 10 Entrance 11. Stair landing 12 Under the floor 13 Air conditioner A 15,615 Air conditioning unit (return section) 16. Suction grille 17, 617 Indoor unit 18,618 blowers 19, 619 Outdoor unit 20, 21, 23, 24, 620, 621, 623, 624, 628 Air supply section 22, 622 Bathroom air supply section 25 Filters 26 windows 30, 31, 32, 33, 34, 630, 631, 632, 633, 634, 636 ducts 35 Vertical shaft 40, 41, 43, 44, 643, 644 Exhaust section 45 Air conditioner B 46 Indoor unit 47, 647 Bypass airflow 48,648 Outlet airflow 50,650 Heat Exchange Ventilation Unit 51 Heat exchange element 55 Inlet 56 Blower filter 60 Ventilation fan 61, 62, 661 Ventilation and exhaust section 65, 665 duct 66, 67, 666 Exhaust duct A 70 Confluence 71, 671 Exhaust duct B 72 Through-duct 73 Connection duct 74 Snow cover 75, 675, 676 Outdoor Exhaust Hood 76 Exhaust duct C 77,677 Outdoor Air Intake Hood 78 Air supply duct A 79 Filter Box 80, 680 ventilation air intake 81 Air supply duct B 82,682 Inlet 83,683 Indoor unit filter 84, 684 Air outlet 85 Bathroom ventilation unit 86, 87, 686, 687 Ventilation supply unit 88 Air purifier 89, 689 Mixing section 90 Indoor Fan 91 Indoor heat exchanger 92 Indoor heat exchanger temperature sensor 93 Drain pan 94,694 louvers 96 Partition Plates 97 Compressor 98 Four-way valve 99 Outdoor heat exchanger 100 Outdoor Fan 101 Inlet 102 Air outlet 103 Expansion valve 105 Rear cover 106 Side cover 107 Top cover 110 Outdoor temperature sensor 218 Large blower Between the 607th floor 611 Staircase, 2nd floor hall 613 Air conditioner D 627 Toilet air supply unit 637, 638 Chambers (air passages) 691 Indoor heat exchanger A 695 Indoor heat exchanger B 698 Expansion valve A 699 Expansion valve B

Claims

1. In a highly airtight and well-insulated building, air intake and exhaust vents are provided in both the living and non-living spaces. From the aforementioned air supply unit, conditioned air is supplied to the living room and the non-living room. A return air passage is provided to return the return air from the exhaust section between the living room and the non-living room back to the air conditioning unit. An intake section and the indoor unit of air conditioner A are provided above the aforementioned air conditioning unit. A blower is installed below the aforementioned air conditioning unit. The air supply unit and the blower are connected, The return air is drawn in from the aforementioned suction section. The blower and the air conditioner A produce the conditioned air and blow it into the air supply section. The aforementioned air conditioner A connects the indoor unit and the outdoor unit with refrigerant piping and electrical wiring, and has a heat pump type refrigeration cycle. A cooling cycle in which the refrigerant passes through a compressor, a four-way valve, an outdoor heat exchanger, an expansion valve, an indoor heat exchanger, and the aforementioned four-way valve, and returns to the compressor, The four-way valve allows the refrigerant to switch between a heating cycle in which it passes through the compressor, the four-way valve, the indoor heat exchanger, the expansion valve, the outdoor heat exchanger, and the four-way valve, and returns to the compressor, and this cycle can be switched by the four-way valve. The indoor unit has the indoor heat exchanger, indoor fan and louvers, When the air conditioner A is in heating operation and in reverse cycle defrosting operation, in which the refrigerant is circulated in the cooling cycle to defrost the outdoor heat exchanger, the indoor fan is operated at maximum airflow, the louvers are directed downward, the return air is passed through the indoor heat exchanger, and blown out from the indoor unit downward into the air conditioning unit. An air conditioning system characterized in that the conditioned air produced within the air conditioning unit is blown out from the air supply section between the living room and the non-living room by the operation of the blower.

2. The air supply unit and the exhaust unit are provided in at least one of the airtight spaces with insulation, such as the attic, underfloor space, or between floors within the building. An air conditioning system in which the conditioned air produced by the air conditioning unit is blown out from the air supply section by the blower, The air conditioning system according to claim 1, characterized in that the amount of air blown out per unit volume of the conditioned air blown out from the air supply unit of at least one of the insulated and airtight spaces located in the attic, under the floor, or between floors is increased compared to the amount of air blown out per unit volume of the conditioned air blown out from the air supply unit of each of the habitable room and the non-habitable room.

3. The air conditioning system according to claim 1, wherein the blower and the air supply unit are connected by an airtight chamber, and the chamber is insulated by being covered with at least one of the following: a room to be air-conditioned, a space to be air-conditioned, or an insulating material.

4. In a highly airtight and well-insulated building, air intake and exhaust vents are provided in both the living and non-living spaces. From the aforementioned air supply unit, conditioned air is supplied to the living room and the non-living room. A return air passage is provided to return the return air from the exhaust section between the living room and the non-living room back to the air conditioning unit. An intake section and the indoor unit of the air conditioner D are provided above the aforementioned air conditioning unit. A blower is installed below the aforementioned air conditioning unit. The air supply unit and the blower are connected, The return air is drawn in from the aforementioned suction section. The blower and the air conditioner D produce the conditioned air and blow it into the air supply section. The aforementioned air conditioner D connects the indoor unit and the outdoor unit with refrigerant piping and electrical wiring, and has a heat pump type refrigeration cycle. The cooling cycle involves the refrigerant passing through the compressor, four-way valve, outdoor heat exchanger, expansion valve A, indoor heat exchanger B, expansion valve B, indoor heat exchanger A, and the four-way valve before returning to the compressor. The four-way valve allows the refrigerant to switch between a heating cycle in which it passes through the compressor, the four-way valve, the indoor heat exchanger A, the expansion valve B, the indoor heat exchanger B, the expansion valve A, the outdoor heat exchanger, and the four-way valve, and returns to the compressor, and this cycle can be switched by the four-way valve. The indoor unit comprises the indoor heat exchanger A, the expansion valve B, the indoor heat exchanger B, an indoor fan, and a louver. When the air conditioner D is in heating operation and in reverse cycle defrosting operation, in which the refrigerant is circulated in the cooling cycle to defrost the outdoor heat exchanger, the expansion valve A is fully opened, the expansion valve B is opened to an appropriate degree, the indoor fan is operated at maximum airflow, the louvers are directed downward, the return air is passed through the indoor heat exchanger A and the indoor heat exchanger B, and blown downward from the indoor unit into the air conditioning unit. An air conditioning system characterized in that the conditioned air produced within the air conditioning unit is blown out from the air supply section between the living room and the non-living room by the operation of the blower.

5. In a highly airtight and well-insulated building, air intake and exhaust vents are provided in both the living and non-living spaces. From the aforementioned air supply unit, conditioned air is supplied to the living room and the non-living room. A return air passage is provided to return the return air from the exhaust section between the living room and the non-living room back to the air conditioning unit. An intake section and the indoor unit of the air conditioner A are provided above the aforementioned air conditioning unit. A blower is installed below the aforementioned air conditioning unit. The air supply unit and the blower are connected, The return air is drawn in from the aforementioned suction section. The blower and the air conditioner A produce the conditioned air and blow it into the air supply section. The aforementioned air conditioner A connects the indoor unit and the outdoor unit with refrigerant piping and electrical wiring, and has a heat pump type refrigeration cycle. A cooling cycle in which the refrigerant passes through a compressor, a four-way valve, an outdoor heat exchanger, an expansion valve, an indoor heat exchanger, and the aforementioned four-way valve, and returns to the compressor, The four-way valve allows the refrigerant to switch between a heating cycle in which it passes through the compressor, the four-way valve, the indoor heat exchanger, the expansion valve, the outdoor heat exchanger, and the four-way valve, and returns to the compressor, and this cycle can be switched by the four-way valve. The indoor unit has the indoor heat exchanger, indoor fan and louvers, When the air conditioner A is in heating operation and in reverse cycle defrosting operation, in which the refrigerant is circulated in the cooling cycle to defrost the outdoor heat exchanger, the airflow rate of the blower is greater than the airflow rate of the indoor unit's outlet airflow. The blower draws in the return air from the intake, operates the indoor fan at maximum airflow, directs the louvers downward, passes the return air through the indoor heat exchanger, and blows the discharged airflow downward into the air conditioning unit from the indoor unit, The return air drawn in from the intake section is mixed with the bypass airflow that does not pass through the indoor heat exchanger. The conditioned air produced has a temperature difference smaller than the temperature difference between the temperature of the discharged airflow and the temperature of the return air from the indoor unit. An air conditioning system characterized by air being blown out from the air supply section between the living room and the non-living room.

Images