Air conditioner

Abstract

The present invention relates to an air conditioner. The air conditioner, according to an embodiment of the present invention, may comprise: a first outdoor unit including a first compressor and a first outdoor heat exchanger; a first heat recovery device fluidically connected to the first outdoor unit and having a first internal heat exchanger; a second outdoor unit including a second compressor and a second outdoor heat exchanger; a second heat recovery device fluidically connected to the second outdoor unit and having a second internal heat exchanger; and an air treatment device having a plurality of heat exchangers fluidically connected to the first and second heat recovery devices.

Description

air conditioner

[0001] The present invention relates to an air conditioning device.

[0002] An air conditioner is a device that maintains the air in a given space at the most suitable condition for its intended use or purpose. Typically, the air conditioner includes a compressor, a condenser, an expansion device, and an evaporator, and operates a refrigeration cycle that compresses, condenses, expands, and evaporates a refrigerant, thereby cooling or heating the space.

[0003] The above-mentioned designated space may be proposed in various ways depending on the location where the air conditioner is used. For example, if the air conditioner is placed in a home or office, the above-mentioned designated space may be an indoor space of the home or building.

[0004] When an air conditioner performs cooling operation, the outdoor heat exchanger provided in the outdoor unit functions as a condenser, and the indoor heat exchanger provided in the indoor unit functions as an evaporator. On the other hand, when the air conditioner performs heating operation, the indoor heat exchanger functions as a condenser, and the outdoor heat exchanger functions as an evaporator.

[0005] In general, in the case of a constant temperature and humidity system using an air conditioning unit, a technology can be applied to recover the heat energy radiated to the outside air and recycle it as reheat energy.

[0006] For example, a heat exchanger (sensible heat exchanger) is applied that can use some of the heat dissipation energy generated in the cooling cycle as reheat energy that can raise the temperature of the supercooled air, or recover heat by utilizing the temperature difference (sensible heat) between the air introduced from the outside and the exhausted air.

[0007] In particular, when a portion of the condensation heat is used as reheat energy to raise the temperature of supercooled air, it is used more in the summer when the outside temperature and humidity are high, and relatively less in the inter-seasons such as spring and fall when the load is low. Furthermore, in the winter when the outside temperature and humidity are low, it is necessary to switch to a heating cycle to cope with the large heating load caused by the introduction of outside air.

[0008] Meanwhile, when the above sensible heat exchanger is applied, the heat energy recovered may be limited due to heat exchange centered on sensible heat, and in the inter-season when the temperature difference between the introduced outside air and the exhaust air is small, the heat recovery effect may decrease or the sensible heat (heating and cooling) load may increase.

[0009] The purpose of the present invention is to provide an air conditioning device having a plurality of cycle sections capable of supplying dehumidified air to an indoor space.

[0010] The present invention aims to provide an air conditioning device that can recycle the heat dissipation generated during cooling operation to increase the temperature of supercooled air, and can prevent a decrease in cooling and dehumidifying capacity and improve cycle efficiency by dissipating heat to the exhaust air side, which has a relatively low temperature, even in situations where it is difficult to dissipate heat to the outside due to the high temperature of the outside air, such as in hot summer.

[0011] In addition, the present invention aims to provide an air conditioning device that can prevent a decrease in heating capacity and improve cycle efficiency by absorbing heat from the exhaust air side, which has a relatively high temperature, even in situations where it is difficult to absorb heat from the outside due to low outside temperature, such as in the cold winter season.

[0012] The purpose of the present invention is to provide an air conditioning device that improves heating capacity by securing additional evaporation heat by using the heat source of exhaust air having a higher temperature than the outside temperature during heating operation in winter, and delays frosting speed and reduces the number of defrosting operations according to the increase in evaporation temperature.

[0013] In addition, the present invention aims to provide an air conditioning device that prevents the exhaust temperature of air supplied indoors from dropping by continuously performing heating operation during defrosting operation.

[0014] The present invention aims to provide an air conditioning device comprising a plurality of outdoor units for driving the plurality of cycle units, a plurality of heat recovery devices connected to the plurality of outdoor units, and an air treatment device fluidly connected to the plurality of heat recovery devices to treat air flowing within a flow path.

[0015] The purpose of the present invention is to provide an air conditioning device having a heat recovery coil as a heat exchanger capable of recovering waste heat generated while operating a plurality of cycle units.

[0016] The purpose of the present invention is to provide an air conditioning device capable of improving dehumidification performance or reheating performance by arranging a coil as a heat exchanger for cooling, dehumidification, or reheating (hereinafter, heat exchange coil) in a supply side flow path.

[0017] The purpose of the present invention is to provide an air conditioning device that arranges a plurality of the above-described coils and can selectively operate some or all of the heat exchange coils among the plurality of heat exchange coils depending on the operation mode.

[0018] The present invention aims to provide an air conditioning device having a first flow path (supply air flow path) in which a plurality of heat exchange coils can be arranged to introduce outside air and dehumidify or reheat the introduced outside air.

[0019] The purpose of the present invention is to provide an air conditioning device having a second flow path (heat recovery flow path) that introduces indoor air and forms a flow path through which heat is dissipated using the introduced indoor air.

[0020] The purpose of the present invention is to provide an air conditioning device capable of recovering air heat or lowering the humidity of supplied air by installing a bypass flow path between the first flow path and the second flow path and allowing air to bypass between the flow paths through the bypass flow path.

[0021] An air conditioning device according to an embodiment of the present invention may include a plurality of cycle sections through which a refrigerant circulates to dehumidify air.

[0022] At least one of the above-described plurality of cycle units may include an air treatment device having an outdoor unit equipped with a compressor and an outdoor heat exchanger, a heat recovery device connected to the outdoor unit, and a heat exchanger fluidly connected to the heat recovery device to recover heat or perform dehumidification or reheating.

[0023] The above outdoor unit includes a plurality of outdoor units, and the plurality of outdoor units can be selectively operated in cooling mode or heating mode.

[0024] The above heat recovery device can improve condensation efficiency by including an internal heat exchanger capable of further condensing the refrigerant that has passed through the outdoor heat exchanger.

[0025] The air treatment device includes a flow path forming an air path, and the heat exchanger can be installed on the path of the flow path.

[0026] The above heat exchanger may include a heat recovery coil that is fluidly connected to the outdoor unit and can condense high-pressure gaseous refrigerant to lower the operating high pressure of the cycle.

[0027] The above heat recovery coil can be installed in the second passage that introduces and exhausts indoor air.

[0028] The above heat exchanger may include a first heat exchange coil that is fluidly connected to the heat recovery device and can cool and dehumidify air flowing through the flow path through heat absorption or heat the air through heat dissipation.

[0029] The above first heat exchange coil can be installed in the first flow path that introduces outside air and supplies it to the room.

[0030] The above air handling device may include a first flow path in which a plurality of heat exchange coils may be arranged to introduce outside air and dehumidify or reheat the introduced outside air.

[0031] The above air treatment device may include a second flow path that introduces indoor air and forms a flow path through which heat is dissipated or absorbed using the introduced indoor air.

[0032] The air treatment device may include a bypass duct that connects the first flow path and the second flow path so that air flowing through one of the first and second flow paths can be bypassed to the other flow path to recover heat or reduce humidity.

[0033] In one aspect of the present invention, an air conditioning device may include a first outdoor unit including a first compressor and a first outdoor heat exchanger; a first heat recovery device fluidly connected to the first outdoor unit and having a first internal heat exchanger; a second outdoor unit including a second compressor and a second outdoor heat exchanger; a second heat recovery device fluidly connected to the second outdoor unit and having a second internal heat exchanger; and an air treatment device having a plurality of heat exchangers fluidly connected to the first and second heat recovery devices.

[0034] The above air treatment device may include a first flow path for introducing air from the outside and supplying it to the room, in which a heat exchange coil among the plurality of heat exchangers is arranged, and a second flow path for forming a flow path for exhausting air in the indoor space to the outside, in which a heat recovery coil among the plurality of heat exchangers is arranged.

[0035] The first heat recovery device includes a first valve device connected to the first internal heat exchanger, and the first valve device can operate to guide the high-pressure refrigerant compressed in the first compressor to the heat recovery coil of the second flow path portion or the heat exchange coil of the first flow path portion.

[0036] The first outdoor unit may include a high-pressure engine that guides high-pressure refrigerant compressed in the first compressor to the first valve device, and the first heat recovery device may include a first engine branch pipe that branches to the inlet side of the first valve device and bypasses it to the first outdoor unit side.

[0037] A first control valve for opening or closing the first tracheal branch pipe is installed in the first tracheal branch pipe, and the first control valve may be configured as an electronic expansion valve (EEV) whose opening can be adjusted to reduce the pressure of the refrigerant.

[0038] The inlet pipe of the heat recovery coil of the second euro section is connected to the first valve device, and in the first mode of operation when the temperature of the outside air is higher than the set temperature, the inlet pipe of the heat recovery coil can form a high-pressure organ through which the high-pressure refrigerant compressed in the first compressor flows.

[0039] The outlet pipe of the heat recovery coil of the second flow section is connected to the first valve device, and in the second mode of operation when the temperature of the outside air is lower than the set temperature, the outlet pipe of the heat recovery coil can form a flow path through which the low-pressure refrigerant evaporated in the heat recovery coil flows.

[0040] The heat exchange coil arranged in the first flow path includes a first heat exchange coil that is fluidly connected to the first heat recovery device and introduces refrigerant that has passed through the heat recovery coil of the second flow path, and the first heat exchange coil may be an evaporator for cooling and dehumidifying air in the first flow path by evaporating refrigerant decompressed by a first coil expansion valve arranged on the inlet side of the first heat exchange coil.

[0041] The heat exchange coil arranged in the first flow section includes a first heat exchange coil that introduces high-pressure refrigerant compressed in the first compressor, and the first heat exchange coil may be a condenser for heating air in the first flow section.

[0042] The air handling device may include a bypass duct connecting the first flow section and the second flow section; and a bypass fan operable to supply room temperature air passing through the air of the second flow section to the first flow section.

[0043] The heat exchange coil disposed in the first flow section may include a plurality of heat exchange coils fluidly connected to the second heat recovery coil, and the plurality of heat exchange coils may include a second heat exchange coil and a third heat exchange coil disposed on the outlet side of the second heat exchange coil based on the air flow.

[0044] The capacity or heat transfer area of ​​the second heat exchange coil may be formed to be larger than the capacity or heat transfer area of ​​the third heat exchange coil.

[0045] The second heat exchange coil may constitute an evaporator for cooling and dehumidifying the air in the first flow path, and the third heat exchange coil may constitute a condenser for heating the air in the first flow path.

[0046] The second heat exchange coil and the third heat exchange coil may be disposed on the outlet side of the first heat exchange coil, which is disposed in the first flow path and fluidly connected to the first heat recovery device based on air flow.

[0047] The second heat recovery device includes a second valve device connected to the second internal heat exchanger, and the second valve device can operate to guide the high-pressure refrigerant compressed in the second compressor to the third heat exchange coil.

[0048] A second coil expansion valve is provided on the inlet side of the second heat exchange coil, and the second valve device can be operated to introduce refrigerant that has been depressurized in the second coil expansion valve and then evaporated in the second heat exchange coil.

[0049] In another aspect of the present invention, an air conditioning device may include a first outdoor unit including a first compressor and a first outdoor heat exchanger; a first heat recovery device fluidly connected to the first outdoor unit and having a first internal heat exchanger and a first valve device; a second outdoor unit including a second compressor and a second outdoor heat exchanger; a second heat recovery device fluidly connected to the second outdoor unit and having a second internal heat exchanger and a second valve device; and an air treatment device including a first flow path for introducing air from outside air and supplying it to an indoor space, and a second flow path for exhausting air in an indoor space to the outside, wherein a heat recovery coil and a first heat exchange coil are disposed fluidly connected to the first valve device.

[0050] The air conditioning device may further include a first branch pipe branched from the inlet side of the first valve device and preventing at least a portion of the refrigerant compressed in the first compressor from flowing into the heat recovery coil or the first heat exchange coil.

[0051] The air handling device may include a second heat exchange coil and a third heat exchange coil fluidly connected to the second valve device, and a second branch pipe branched from the inlet side of the second valve device and preventing at least a portion of the refrigerant compressed in the second compressor from flowing into the third heat exchange coil.

[0052] An electronic expansion valve (EEV) with adjustable opening may be installed in the first or second tracheal branch pipe to reduce the pressure of the refrigerant.

[0053] The first heat exchange coil, the second heat exchange coil, and the third heat exchange coil may be installed in the first flow path, and the heat recovery coil may be installed in the second flow path.

[0054] According to an embodiment of the present invention, an air conditioning device having a plurality of cycle sections is provided, so that air can be dehumidified and easily supplied to an indoor space.

[0055] According to an embodiment of the present invention, the heat dissipation generated during cooling operation can be recycled to increase the temperature of supercooled air, and even in situations where it is difficult to dissipate heat to the outside due to high outside temperature, such as in hot summer, heat can be dissipated to the exhaust air side where the temperature is relatively low, thereby preventing a decrease in cooling and dehumidifying capacity and improving cycle efficiency.

[0056] According to an embodiment of the present invention, even in situations where it is difficult to absorb heat from the outside due to low outside temperature, such as in the cold winter season, heat is absorbed from the exhaust air side, which has a relatively high temperature, thereby preventing a decrease in heating capacity and improving cycle efficiency.

[0057] According to an embodiment of the present invention, during heating operation in winter, heating capacity is improved by securing additional evaporation heat by using a heat source of exhaust air having a temperature higher than the outside temperature, and the frosting speed can be delayed and the number of defrosting operations can be reduced as the evaporation temperature increases.

[0058] According to an embodiment of the present invention, an object is to provide an air conditioning device that prevents the exhaust temperature of air supplied to a room from dropping by continuously performing heating operation during defrosting operation.

[0059] According to an embodiment of the present invention, a plurality of outdoor units are provided for driving the plurality of cycle units, a plurality of heat recovery devices connected to the plurality of outdoor units, and an air treatment device fluidly connected to the plurality of heat recovery devices to treat air flowing within the flow path section, so that the dehumidification performance can be improved.

[0060] According to an embodiment of the present invention, a heat recovery coil as a heat exchanger is provided to recover waste heat generated while operating a plurality of cycle units, thereby reducing the energy used for operating the device.

[0061] According to an embodiment of the present invention, an object is to provide an air conditioning device capable of improving dehumidification performance or reheating performance by arranging a coil as a heat exchanger for cooling, dehumidification, or reheating (hereinafter, heat exchange coil) in a supply side flow path section.

[0062] According to an embodiment of the present invention, since a plurality of the above coils are arranged and some or all of the heat exchange coils among the plurality of heat exchange coils can be selectively operated depending on the operation mode, optimal operation control according to external conditions can be achieved.

[0063] According to an embodiment of the present invention, a first flow path (supply air flow path) is provided in which a plurality of heat exchange coils can be arranged to introduce outside air and dehumidify or reheat the introduced outside air, so that dehumidification performance can be improved.

[0064] The present invention is provided with a second flow path (heat recovery flow path) that introduces indoor air and forms a flow path through which heat is dissipated using the introduced indoor air, so that the operating efficiency of the cycle can be improved.

[0065] The present invention can recover air heat or reduce the humidity of supplied air by installing a bypass flow path between the first flow path and the second flow path and allowing air to bypass between the flow paths through the bypass flow path.

[0066] Figure 1 is a cycle diagram showing the configuration of an air conditioning device according to an embodiment of the present invention.

[0067] Figure 2 is a cycle diagram showing the operation of the first mode of an air conditioning device according to an embodiment of the present invention.

[0068] Figure 3 is a cycle diagram showing the operation of the second mode of the air conditioning device according to an embodiment of the present invention.

[0069] Figure 4 is a cycle diagram showing the operation of the third mode of the air conditioning device according to an embodiment of the present invention.

[0070] Figure 5 is a cycle diagram showing the operation of the fourth mode of the air conditioning device according to an embodiment of the present invention.

[0071] Figure 6 is a cycle diagram showing the operation of the fifth mode of the air conditioning device according to an embodiment of the present invention.

[0072] Hereinafter, some embodiments of the present invention will be described in detail with reference to exemplary drawings. When designating components in each drawing, it should be noted that, where possible, identical components will be given the same reference numerals, even if they appear in different drawings. Furthermore, when describing embodiments of the present invention, detailed descriptions of related known structures or functions will be omitted if they are deemed to hinder understanding of the embodiments of the present invention.

[0073] Additionally, terms such as first, second, A, B, (a), (b), etc. may be used to describe components of embodiments of the present invention. These terms are only intended to distinguish the components from other components, and the nature, order, or sequence of the components are not limited by the terms. When it is described that a component is "connected," "coupled," or "connected" to another component, it should be understood that the component may be directly connected or connected to the other component, but another component may also be "connected," "coupled," or "connected" between each component.

[0074] Figure 1 is a cycle diagram showing the configuration of an air conditioning device according to an embodiment of the present invention.

[0075] Referring to FIG. 1, an air conditioning device (1) according to an embodiment of the present invention may include a plurality of cycle sections (1a, 1b) forming a cycle in which a refrigerant circulates.

[0076] The above multiple cycle parts (1a, 1b) may include a first cycle part (1a) and a second cycle part.

[0077] The above first cycle unit (1a) may include a first outdoor unit (10) and a first heat recovery device (40). The above second cycle unit (1b) may include a second outdoor unit (20) and a second heat recovery device (50).

[0078] The above air conditioning device (1) may include an air treatment device (70) for dehumidifying air supplied indoors using the heat source of the plurality of cycle units (1a, 1b). The air treatment device (70) may be called an air handling unit (AHU).

[0079] The air treatment device (70) may include a flow path (80, 90) that forms an air flow path. The flow path (80, 90) defines an air flow path formed inside the air treatment device (70), and a plurality of heat exchangers may be installed in the path of the flow path (80, 90).

[0080] The above-mentioned flow path may include a first flow path (80) that introduces outside air, dehumidifies or reheats the introduced outside air, and then supplies it to the room. The first flow path (80) may be called a “supply air flow path.”

[0081] One end of the first flow path (80) may form a first outside air introduction portion (81) into which outside air is introduced. The other end of the first flow path (80) may form an indoor supply portion (82) that removes moisture contained in the outside air or reheats it and then supplies it indoors.

[0082] A first fan (83) may be installed in the first flow path (80) to generate air flow passing through the first flow path (80). For example, the first fan (83) may be installed adjacent to and inside the indoor supply section (82).

[0083] Inside the first euro section (80), a plurality of heat exchangers constituting the first and second cycle sections (1a, 1b) can be installed.

[0084] For example, the plurality of heat exchangers may include a first heat exchange coil (261) constituting the first cycle section (1a).

[0085] The above-mentioned plurality of heat exchangers may include a second heat exchange coil (361) and a third heat exchange coil (362) constituting the second cycle section (1b).

[0086] Based on the air flow of the first flow path (80), the second heat exchange coil (361) may be placed on the outlet side of the first heat exchange coil (261), and the third heat exchange coil (362) may be placed on the outlet side of the second heat exchange coil (361).

[0087] The first to third heat exchange coils (361) may be arranged in series in sequence based on air flow. Accordingly, air passing through the first heat exchange coil (261) may pass through the second heat exchange coil (361) and then pass through the third heat exchange coil (362).

[0088] The capacity or heat transfer area of ​​the second heat exchange coil (361) may be greater than the capacity or heat transfer area of ​​the third heat exchange coil (362). Therefore, depending on whether the load of the system is high or low, either of the second heat exchange coil (361) and the third heat exchange coil (362) may be utilized.

[0089] The above-mentioned flow path may include a second flow path (90) that introduces indoor air, processes the introduced indoor air, and then exhausts the air to the outside. The second flow path (90) may be called a “heat recovery flow path.”

[0090] One end of the second flow path (90) may form an indoor air introduction portion (91) into which indoor air is introduced. The other end of the second flow path (90) may form an exhaust portion (92) that uses the introduced indoor air to radiate heat from the heat exchanger of the first cycle portion (1a) or absorb heat from the heat exchanger and then exhausts the heat to the outside.

[0091] A second fan (93) may be installed in the second flow path (90) to generate air flow passing through the second flow path (90). For example, the second fan (93) may be installed adjacent to and inside the exhaust part (92).

[0092] A heat exchanger constituting the first cycle section (1a) may be installed inside the second flow section (90). For example, the heat exchanger may include a heat recovery coil (251) constituting the first cycle section (1a).

[0093] The detailed configuration of the first and second cycle sections (1a, 1b) is described.

[0094] The above first cycle section (1a) may include a first outdoor unit (10) through which refrigerant circulates and a first heat recovery device (40) fluidly connected to the first outdoor unit (10) and having a first internal heat exchanger (42).

[0095] The first outdoor unit (10) may include a first compressor (210) for compressing refrigerant to high pressure. A first accumulator (205) may be installed on the suction side of the first compressor (210) to separate gaseous refrigerant from the low-pressure refrigerant and guide it to the first compressor (210).

[0096] The above first outdoor unit (10) is installed on the outlet side of the first compressor (210) and may include a flow control valve (220, 222) that controls the flow direction of the high-temperature, high-pressure refrigerant discharged from the first compressor (210) and flows therein.

[0097] The above flow control valve (220, 222) may include a first valve (220) and a second valve (222). For example, the first and second valves (220, 222) may include a four-way valve.

[0098] The above first and second valves (220, 222) can be configured so that three of the four ports are open and connected to the refrigerant pipe, and the remaining one port is closed.

[0099] A discharge pipe (212) is connected to the outlet of the first compressor (210), and the discharge pipe (212) can be connected to a valve connection pipe (224) that connects the first valve (220) and the second valve (222).

[0100] In detail, the valve connection pipe (224) includes a joint portion (224a), and the discharge pipe (212) can be connected to the joint portion (224a). The refrigerant of the discharge pipe (212) flows into the valve connection pipe (224) through the joint portion (224a), and can be branched into the first and second valves (220, 222) and flowed into the second valve (222).

[0101] For example, when the first outdoor unit (10) is operated in cooling mode, some of the refrigerant flowing into the valve connection pipe (224) may flow into the first outdoor heat exchanger (230) through the first valve (220). The remaining refrigerant may flow into the first heat recovery device (40) through the second valve (222).

[0102] A first outdoor fan that blows air into the first outdoor heat exchanger (230) may be provided on one side of the first outdoor heat exchanger (230).

[0103] The above first outdoor unit (10) may include a heat exchanger connecting pipe (226) extending from the first valve (220) to the first outdoor heat exchanger (230).

[0104] The first outdoor unit (10) may include a high-pressure pipe (227) extending from the second valve (222) to the first heat recovery device (40). A high-pressure gaseous refrigerant flows through the high-pressure pipe (227), and may extend to the outside of the first outdoor unit (10) and be connected to the first heat recovery device (40).

[0105] The high pressure engine (227) is connected to the third valve (240) of the first heat recovery device (40), and can be extended from the third valve (240) and connected to the heat recovery coil (251). That is, the high pressure engine (227) can form an inlet pipe of the heat recovery coil (251).

[0106] The third valve (240) may include, for example, a four-way valve. The third valve (240) may fluidly connect the outdoor unit (10) and the heat exchanger (251, 261) of the air treatment device (70) to the refrigerant.

[0107] The first outdoor unit (10) may include a first outdoor heat exchanger (230). In the cooling mode of the first outdoor unit (10), the refrigerant compressed in the first compressor (210) may be condensed in the first outdoor heat exchanger (230). That is, the first outdoor heat exchanger (230) may function as a condenser.

[0108] On the other hand, in the heating mode of the first outdoor unit (10), the refrigerant flowing into the first outdoor unit (10) from the first heat recovery device (40) is depressurized in the outdoor expansion valve (234) and then flows into the first outdoor heat exchanger (230), and can be evaporated while passing through the first outdoor heat exchanger (230). That is, the first outdoor heat exchanger (230) can function as an evaporator.

[0109] Based on the cooling mode of the first outdoor unit (10), a liquid pipe (235) may be connected to the outlet side of the first outdoor heat exchanger (230). A liquid refrigerant flows through the liquid pipe (235), and may extend to the outside of the first outdoor unit (10) and be connected to the first heat recovery device (40).

[0110] An outdoor expansion valve (234) may be installed in the above liquid pipe (235). The outdoor expansion valve (234) may be configured as, for example, an electronic expansion valve (EEV) whose opening can be adjusted to reduce the pressure of the refrigerant.

[0111] The first outdoor unit (10) may include a low-pressure pipe (264) extending from the inlet side of the first accumulator (205) to the first heat recovery device (40). A low-pressure gaseous refrigerant flows through the low-pressure pipe (264), and may extend to the outside of the first outdoor unit (10) and be connected to the first heat recovery device (40).

[0112] The first outdoor unit (10) and the first heat recovery device (40) can be connected by three pipes. In detail, the first outdoor unit (10) and the first heat recovery device (40) are connected by the high pressure engine (227), the liquid pipe (235), and the low pressure engine (264), so that refrigerant can circulate between the first outdoor unit (10) and the first heat recovery device (40).

[0113] The first heat recovery device (40) may include a third valve (240) connected to the high pressure engine (227) and the low pressure engine (264). For example, the third valve (240) may include a four-way valve.

[0114] The third valve (240) can, in the first mode, transfer the refrigerant of the high-pressure engine (227) to the heat recovery coil (251) to condense it. That is, the heat recovery coil (251) can function as a condenser. The heat recovery coil (251) is installed in the second flow path (90), and the air of the second flow path (90) can be heated while passing through the heat recovery coil (251).

[0115] Ultimately, when exhausting indoor air through the second duct (90), the waste heat can be used to condense the heat recovery coil (251), thereby improving the operating performance of the cycle.

[0116] The third valve (240) can receive the refrigerant evaporated from the heat recovery coil (251) in any one of the second to fourth modes. That is, the heat recovery coil (251) can function as an evaporator. Consequently, when exhausting indoor air through the second flow path (90), waste heat can be used to evaporate the heat recovery coil (251), thereby improving the operating performance of the cycle.

[0117] The first heat recovery device (40) may include a first internal heat exchanger (42). The first internal heat exchanger (42) may be configured as a heat exchanger in which heat exchange occurs between refrigerants.

[0118] The first internal heat exchanger (42) may be configured to allow heat exchange between a medium-temperature, high-pressure two-phase refrigerant flowing through the liquid pipe (235) and a low-temperature refrigerant flowing through the low-pressure engine (264). In this process, the refrigerant in the liquid pipe (235) may be further condensed.

[0119] When the first cycle section (1a) is operating, at least a portion of the high-pressure refrigerant compressed in the first compressor (210) is branched to the heat recovery coil (251) through the high-pressure engine (227), so the high pressure of the first cycle section (1a) is lowered, and thus heat dissipation in the first outdoor heat exchanger (230) may not be smooth.

[0120] In order to solve this problem, the first internal heat exchanger (42) is provided in the first heat recovery device (40) to further condense the refrigerant in the liquid pipe (235), thereby improving the condensation performance of the cycle.

[0121] The high pressure engine (227) may be connected to the heat recovery coil (251) via the third valve (240). The high pressure engine (227) may include a second branch (227a) to which the first engine branch pipe (280) is connected.

[0122] The second branch portion (227a) is located on the inlet side of the third valve (240), and the first branch pipe (280) can extend from the second branch portion (227a) and be connected to a low pressure engine (264).

[0123] A first control valve (285) for controlling the flow of refrigerant may be installed in the first branch pipe (280). For example, the first control valve (285) may be configured as an electronic expansion valve (EEV) whose opening can be adjusted to reduce the pressure of the refrigerant.

[0124] When the above air conditioning device (1) operates in the third mode, the first control valve (285) is opened to a set opening degree, and at least a portion of the refrigerant flowing through the high-pressure engine (227) is not introduced into the third valve (240) but is bypassed to the first engine branch pipe (280) and returned to the first outdoor unit (10).

[0125] The refrigerant in the first engine branch pipe (280) can be depressurized in the first control valve (285) and introduced into the low pressure engine (264).

[0126] The above low pressure engine (264) may include a third branch (264a) to which the first engine branch pipe (280) is connected. The third branch (264a) may be formed at a point on the outlet side of the third valve (240) of the low pressure engine (264).

[0127] In the third branch section (264a), the refrigerant of the low pressure engine (264) and the refrigerant of the first engine branch pipe (280) are combined, and the combined refrigerant can be introduced into the first internal heat exchanger (42).

[0128] The first cycle section (1a) may include a first heat exchange coil (261) connected to the liquid pipe (235). In the first mode of operation of the air conditioning device (1), the liquid pipe (235) may be extended from the first internal heat exchanger (42) to the first heat exchange coil (261) after being radiated from the first internal heat exchanger (42).

[0129] The above first heat exchange coil (261) is installed in the first flow path (80) and can cool the outside air introduced from the first outside air introduction part (81) to remove moisture.

[0130] A heat recovery coil outlet pipe (253) may be connected to the outlet side of the heat recovery coil (251). Medium-temperature, high-pressure liquid refrigerant condensed in the heat recovery coil (251) may flow through the heat recovery coil outlet pipe (253).

[0131] A control valve (254) may be installed in the heat recovery coil outlet pipe (253). For example, the control valve (254) may be configured as an electronic expansion valve (EEV) whose opening can be adjusted. The opening of the control valve (254) may control the amount of refrigerant to be introduced into the heat recovery coil (251). During operation in the first mode, the amount of refrigerant introduced into the first outdoor heat exchanger (230) may also be controlled according to the opening of the control valve (254).

[0132] The above heat recovery coil outlet pipe (253) can be connected to the liquid pipe (235). In detail, the liquid pipe (235) forms a first branch portion (235a), and the heat recovery coil outlet pipe (253) can be connected to the liquid pipe (235) through the first branch portion (235a).

[0133] In the first mode of the air conditioning device (1), the refrigerant of the heat recovery coil outlet pipe (253) flows into the liquid pipe (235) through the first branch portion (235a), and can be combined with the refrigerant of the liquid pipe (235) and flow into the first heat exchange coil (261). A first coil expansion valve (236) for reducing the pressure of the refrigerant to be flowed into the first heat exchange coil (261) can be installed on the inlet side of the first heat exchange coil (261).

[0134] The above first coil expansion valve (236) may be configured as an electronic expansion valve (EEV) whose opening can be adjusted, for example, to reduce the pressure of the refrigerant. The refrigerant reduced in pressure by the first coil expansion valve (236) may flow into the first heat exchange coil (261) and evaporate.

[0135] The first heat exchange coil (261) may be connected to a low-pressure engine (264). Accordingly, the refrigerant evaporated in the first heat exchange coil (261, 262) may flow through the low-pressure engine (264) and flow into the first outdoor unit (10) through the third valve (240) and the first internal heat exchanger (42).

[0136] In detail, a low pressure engine (264) is connected to the outlet of the first heat exchange coil (261), and the low pressure engine (264) can extend through the third valve (240) and the first internal heat exchanger (42).

[0137] The low pressure organ (264) may extend into the interior of the first outdoor unit (10) and be connected to the inlet side of the first accumulator (205). Among the low pressure refrigerants introduced into the first accumulator (205) from the low pressure organ (264), gaseous refrigerant may be sucked into the first compressor (210).

[0138] In this way, in the first cycle section (1a), refrigerant circulation can be performed to drive the first heat exchange coil (261) to exchange heat with air inside the first flow section (80).

[0139] In addition, by placing a heat recovery coil (251) inside the second flow path (90) and exchanging heat between the indoor air flowing through the second flow path (90) and the heat recovery coil (251), the operating pressure of the cycle can be stabilized and the performance can be improved.

[0140] The above air treatment device (70) may include a bypass duct (85) connecting the first flow section (80) and the second flow section (90). A bypass fan (85a) may be installed in the bypass duct (85).

[0141] When the bypass fan (85a) is driven in a specific mode of the air conditioning device, at least a portion of the low-humidity air at room temperature flowing through the second flow path (90) is bypassed to the first flow path (80), thereby helping to cool, dehumidify, or heat the air in the first flow path (80).

[0142] The second cycle unit (1b) according to an embodiment of the present invention may include a second outdoor unit (20) through which refrigerant circulates, and a second heat recovery device (50) fluidly connected to the second outdoor unit (20) and having a second internal heat exchanger (52).

[0143] The second outdoor unit (20) may include a second compressor (310) for compressing refrigerant to high pressure. A second accumulator (305) may be installed on the suction side of the second compressor (310) to separate gaseous refrigerant from the low-pressure refrigerant and guide it to the second compressor (210).

[0144] The second outdoor unit (20) is installed on the outlet side of the second compressor (210) and may include a flow control valve (320, 322) that controls the flow direction of the high-temperature, high-pressure refrigerant discharged from the second compressor (210) and flows therein.

[0145] The above flow control valve (320, 322) may include a first valve (320) and a second valve (322). For example, the first and second valves (320, 322) may include a four-way valve.

[0146] The above first and second valves (320, 322) can be configured so that three of the four ports are open and connected to the refrigerant pipe, and the remaining one port is closed.

[0147] A discharge pipe (312) is connected to the outlet of the second compressor (310), and the discharge pipe (312) can be connected to a valve connection pipe (324) that connects the first valve (320) and the second valve (322).

[0148] In detail, the valve connection pipe (324) includes a joint portion (324a), and the discharge pipe (312) can be connected to the joint portion (324a). The refrigerant of the discharge pipe (312) flows into the valve connection pipe (324) through the joint portion (324a), and can be branched into the first and second valves (320, 322) and flowed into the second valve (322).

[0149] For example, when the first outdoor unit (10) is operated in cooling mode, some of the refrigerant flowing into the valve connection pipe (324) may flow into the second outdoor heat exchanger (330) through the first valve (320). The remaining refrigerant may flow into the second heat recovery device (50) through the second valve (322).

[0150] A second outdoor fan that blows air to the second outdoor heat exchanger (330) may be provided on one side of the second outdoor heat exchanger (330).

[0151] The second outdoor unit (20) may include a heat exchanger connecting pipe (326) extending from the first valve (320) to the second outdoor heat exchanger (330).

[0152] The second outdoor unit (20) may include a high-pressure pipe (327) extending from the second valve (322) to the second heat recovery device (50). High-pressure gaseous refrigerant flows through the high-pressure pipe (327), and may extend to the outside of the second outdoor unit (20) and be connected to the second heat recovery device (50).

[0153] The high pressure engine (327) is connected to the third valve (340) of the second heat recovery device (50), and can be extended from the third valve (340) and connected to the third heat exchange coil (362).

[0154] The third valve (340) may include, for example, a four-way valve. The third valve (340) may fluidly connect the outdoor unit (10) and the heat exchanger (361, 362) of the air treatment device (70) to the refrigerant.

[0155] The second outdoor unit (20) may include a second outdoor heat exchanger (330). In the cooling mode of the second outdoor unit (20), the refrigerant compressed in the second compressor (310) may be condensed in the second outdoor heat exchanger (330). That is, the second outdoor heat exchanger (330) may function as a condenser.

[0156] On the other hand, in the heating mode of the second outdoor unit (20), the refrigerant flowing into the second outdoor unit (20) from the second heat recovery device (50) is depressurized in the outdoor expansion valve (334) and then flows into the second outdoor heat exchanger (330), and can be evaporated while passing through the second outdoor heat exchanger (330). That is, the second outdoor heat exchanger (330) can function as an evaporator.

[0157] Based on the cooling mode of the second outdoor unit (20), a liquid pipe (335) may be connected to the outlet side of the second outdoor heat exchanger (330). A liquid refrigerant flows through the liquid pipe (335), and may be extended to the outside of the second outdoor unit (20) and connected to the second heat recovery device (50).

[0158] An outdoor expansion valve (334) may be installed in the above liquid pipe (335). The outdoor expansion valve (334) may be configured as, for example, an electronic expansion valve (EEV) whose opening can be adjusted to reduce the pressure of the refrigerant.

[0159] The second outdoor unit (20) may include a low-pressure pipe (364) extending from the inlet side of the second accumulator (305) to the second heat recovery device (50). A low-pressure gaseous refrigerant flows through the low-pressure pipe (364), and may extend to the outside of the second outdoor unit (20) and be connected to the second heat recovery device (50).

[0160] The second outdoor unit (20) and the second heat recovery device (50) can be connected by three pipes. In detail, the second outdoor unit (20) and the second heat recovery device (50) are connected by the high pressure engine (327), the liquid pipe (335), and the low pressure engine (364), so that refrigerant can circulate between the second outdoor unit (20) and the second heat recovery device (50).

[0161] The second heat recovery device (50) may include a third valve (340) connected to the high pressure engine (327). For example, the third valve (340) may include a four-way valve. For convenience of explanation, in order to distinguish the third valve (240) of the first heat recovery device (40) from the third valve (340) of the second heat recovery device (50), the third valve (240) may be referred to as a “first valve device” and the third valve (340) may be referred to as a “second valve device.”

[0162] The third valve (340) can transfer the refrigerant of the high pressure engine (327) to the third heat exchange coil (362) in the first mode to condense it. That is, the third heat exchange coil (362) can function as a condenser. The third heat exchange coil (362) is installed in the first flow path (80), and the air of the first flow path (90) can be heated while passing through the third heat exchange coil (362).

[0163] Ultimately, when supplying air to the indoor space through the first duct (80), the air can be reheated as it passes through the third heat exchange coil (362).

[0164] The third valve (240) can receive refrigerant evaporated from the second heat exchange coil (361) in the first mode. That is, the second heat exchange coil (361) can function as an evaporator.

[0165] Ultimately, when air is supplied to the indoor space through the first duct (80), the air is cooled and dehumidified as it passes through the second heat exchange coil (361), and the dehumidified air can be supplied to the indoor space.

[0166] The second heat recovery device (50) may include a second internal heat exchanger (52). The second internal heat exchanger (52) may be configured as a heat exchanger in which heat exchange occurs between refrigerants.

[0167] The second internal heat exchanger (52) may be configured to allow heat exchange between the medium-temperature, high-pressure two-phase refrigerant flowing through the liquid pipe (335) and the low-temperature refrigerant flowing through the low-pressure engine (364). In this process, the refrigerant in the liquid pipe (335) may be further condensed.

[0168] When the second cycle unit (1b) is operating, at least a portion of the high-pressure refrigerant compressed in the second compressor (310) is branched to the third heat exchange coil (362) through the high-pressure engine (327), so the high pressure of the second cycle unit (1b) is lowered, and thus heat dissipation in the second outdoor heat exchanger (330) may not be smooth.

[0169] To solve this problem, the second internal heat exchanger (52) is provided in the second heat recovery device (50) to further condense the refrigerant in the liquid pipe (335), thereby improving the condensation performance of the cycle.

[0170] The high pressure engine (327) may be connected to the third heat exchange coil (362) via the third valve (340). The high pressure engine (227) may include a second branch (327a) to which a second engine branch pipe (380) is connected.

[0171] The second branch portion (327a) is located on the inlet side of the third valve (240), and the second branch pipe (380) can extend from the second branch portion (327a) and be connected to a low pressure engine (364).

[0172] A second control valve (385) for controlling the flow of refrigerant may be installed in the second branch pipe (380). For example, the second control valve (385) may be configured as an electronic expansion valve (EEV) whose opening can be adjusted to reduce the pressure of the refrigerant.

[0173] When the above air conditioning device (1) operates in the fifth mode, the second control valve (385) is opened to a set opening degree, and at least a portion of the refrigerant flowing in the high-pressure engine (327) is not introduced into the third valve (340) but is bypassed to the second engine branch pipe (380) and returned to the second outdoor unit (20).

[0174] The refrigerant in the second engine branch pipe (380) can be depressurized in the second control valve (385) and introduced into the low pressure engine (364).

[0175] The above low pressure engine (364) may include a third branch (364a) to which the second branch pipe (380) is connected. The third branch (364a) may be formed at a point on the outlet side of the third valve (240) of the low pressure engine (364).

[0176] In the third branch section (364a), the refrigerant of the low pressure engine (364) and the refrigerant of the second engine branch pipe (380) are combined, and the combined refrigerant can be introduced into the second internal heat exchanger (52).

[0177] The refrigerant in the liquid pipe (335) additionally condensed in the second internal heat exchanger (52) can be introduced into the second heat exchange coil (361). That is, the second cycle section (1b) can include a second heat exchange coil (361) connected to the liquid pipe (335).

[0178] The above second heat exchange coil (361) is installed in the first flow path (80) and can cool the outside air introduced from the first outside air introduction part (81) to remove moisture when the air conditioning device (1) is operated in the first mode.

[0179] The above liquid pipe (335) is heat-radiated from the second internal heat exchanger (52) and can extend from the second internal heat exchanger (52) to the second heat exchange coil (361).

[0180] A heat exchange coil outlet pipe (353) may be connected to the outlet side of the third heat exchange coil (362). A medium-temperature, high-pressure liquid refrigerant condensed in the heat exchange coil (362) may flow through the heat exchange coil outlet pipe (353).

[0181] A third coil expansion valve (337) may be installed in the above heat exchange coil outlet pipe (353). For example, the third coil expansion valve (337) may be configured as an electronic expansion valve (EEV) whose opening can be adjusted.

[0182] Depending on the opening degree of the above control valve (254), the amount of refrigerant to be introduced into the third heat exchange coil (362) or the degree of pressure reduction of the refrigerant can be controlled.

[0183] The above heat exchange coil outlet pipe (353) can be connected to the liquid pipe (335). In detail, the liquid pipe (335) forms a first branch portion (335a), and the heat exchange coil outlet pipe (353) can be connected to the liquid pipe (235) through the first branch portion (335a).

[0184] The refrigerant of the above liquid pipe (335) and the refrigerant of the heat exchange coil outlet pipe (353) can be combined in the first branch portion (335a) and introduced into the second heat exchange coil (361).

[0185] A second coil expansion valve (336) may be installed on the inlet side of the second heat exchange coil (361) to reduce the pressure of the refrigerant to be introduced into the second heat exchange coil (361). The second coil expansion valve (336) may be configured as, for example, an electronic expansion valve (EEV) whose opening can be adjusted to reduce the pressure of the refrigerant.

[0186] The refrigerant depressurized in the second coil expansion valve (336) can be introduced into the second heat exchange coil (361) and evaporated.

[0187] The second heat exchange coil (361) may be connected to a low-pressure engine (364). Therefore, when the air conditioning device (1) is operated in the first mode, the refrigerant evaporated in the second heat exchange coil (361) may flow through the low-pressure engine (364) and flow into the second outdoor unit (20) through the second internal heat exchanger (52).

[0188] In detail, a low pressure engine (364) is connected to the outlet of the second heat exchange coil (361), and the low pressure engine (364) can extend through the second internal heat exchanger (52).

[0189] The low pressure organ (364) may extend into the interior of the second outdoor unit (20) and be connected to the inlet side of the second accumulator (305). Among the low pressure refrigerants introduced into the second accumulator (305) from the low pressure organ (364), the gaseous refrigerant may be sucked into the second compressor (310).

[0190] In this way, in the first cycle section (1b), circulation of refrigerant can be achieved to drive the second heat exchange coil (361) and the third heat exchange coil (362) in order to exchange heat with the air flowing through the first flow section (80).

[0191] Figure 2 is a cycle diagram showing the operation of the first mode of an air conditioning device according to an embodiment of the present invention.

[0192] Referring to FIG. 2, the air conditioning device (1) according to an embodiment of the present invention can be operated in a first mode. The first mode can be understood as a mode in which the device operates under conditions in which the temperature and humidity of the outside air are relatively high. For example, the first mode can be operated in the summer when the outside air temperature is approximately 30°C or higher, and the first mode can be referred to as a "summer mode."

[0193] In the above first mode, both the first outdoor unit (10) of the first cycle unit (1a) and the second outdoor unit (20) of the second cycle unit (1b) can be operated in cooling mode.

[0194] First, in the first cycle section (1a), when the first compressor (210) of the first outdoor unit (10) is driven, at least a portion of the refrigerant compressed in the first compressor (210) flows into the first outdoor heat exchanger (230) through the first valve (220), and the refrigerant condensed in the first outdoor heat exchanger (230) can flow into the first internal heat exchanger (42) through the liquid pipe (235).

[0195] The ratio of the refrigerant compressed in the first compressor (210) and flowing into the first outdoor heat exchanger (230) through the first valve (220) may be 50% or less. For example, the ratio of the refrigerant flowing into the first outdoor heat exchanger (230) may be formed within the range of 15 to 25%.

[0196] The outdoor fan provided on one side of the first outdoor heat exchanger (230) can be operated at a minimum RPM.

[0197] And, the ratio of the remaining refrigerant among the refrigerant compressed in the first compressor (210), that is, the refrigerant flowing into the heat recovery coil (251) through the second valve (222), can be formed within the range of 75 to 85%.

[0198] By distributing the refrigerant in this manner, a relatively large amount of the high-pressure refrigerant compressed in the first compressor (210) flows to the heat recovery coil (251), thereby increasing the heat recovery efficiency.

[0199] The refrigerant in the above liquid pipe (235) can be further condensed by exchanging heat with the refrigerant of the low pressure engine (264) in the first internal heat exchanger (42). At least a portion of the additionally condensed refrigerant can be depressurized in the first coil expansion valve (236) and then introduced into the first heat exchange coil (261) to evaporate.

[0200] The refrigerant evaporated in the first heat exchange coil (261) flows through the low pressure engine (264) and can exchange heat (additionally evaporate) with the refrigerant in the liquid pipe (235) in the first internal heat exchanger (42).

[0201] The refrigerant that has undergone heat exchange in the first internal heat exchanger (42) is introduced into the first outdoor unit (10), and after passing through the first accumulator (205), can be sucked into the first compressor (210).

[0202] Meanwhile, another portion of the refrigerant compressed in the first compressor (210) may be introduced into the first heat recovery device (40) through the second valve (222) and into the heat recovery coil (251) through the third valve (240). The refrigerant is condensed in the heat recovery coil (251), and the condensed refrigerant may be combined with the liquid pipe (235) through the first branch portion (235a).

[0203] The refrigerant combined in the above liquid pipe (235) can be evaporated in the first heat exchange coil (261) after being depressurized in the first coil expansion valve (236) as described above. The heat recovery coil (251) can easily condense and recover heat by the air flowing in the second flow path (90), i.e., the exhausted indoor air.

[0204] Meanwhile, when the bypass fan (85a) is driven, at least a portion of the low-humidity air flowing through the second flow path (90) can flow into the first flow path (80) through the bypass duct (85) and into the first heat exchange coil (261).

[0205] Next, in the second cycle section (1b), when the second compressor (310) of the second outdoor unit (20) is driven, at least a portion of the refrigerant compressed in the second compressor (310) flows into the second outdoor heat exchanger (330) through the first valve (320), and the refrigerant condensed in the second outdoor heat exchanger (330) can flow into the second internal heat exchanger (52) through the liquid pipe (335).

[0206] The ratio of the refrigerant compressed in the second compressor (310) and flowing into the second outdoor heat exchanger (330) through the first valve (320) may be 50% or less. For example, the ratio of the refrigerant flowing into the second outdoor heat exchanger (330) may be formed within the range of 15 to 25%.

[0207] The outdoor fan provided on one side of the second outdoor heat exchanger (330) can be operated at a minimum RPM.

[0208] And, the ratio of the remaining refrigerant among the refrigerant compressed in the second compressor (310), that is, the refrigerant flowing into the third heat exchange coil (362) through the second valve (322), can be formed within the range of 75 to 85%.

[0209] By distributing the refrigerant in this manner, a relatively large amount of the high-pressure refrigerant compressed in the second compressor (310) flows to the third heat exchange coil (362), thereby increasing the reheating efficiency.

[0210] The refrigerant in the above liquid pipe (235) can be further condensed by exchanging heat with the refrigerant of the low-pressure engine (364) in the second internal heat exchanger (52). The additionally condensed refrigerant can be depressurized in the second coil expansion valve (336) and then introduced into the second heat exchange coil (361) to evaporate. During the evaporation process of the second heat exchange coil (361), the air can be cooled and dehumidified, thereby increasing the dehumidification performance.

[0211] The refrigerant evaporated in the second heat exchange coil (361) flows through the low pressure engine (364) and can exchange heat (additionally evaporate) with the refrigerant in the liquid pipe (335) in the second internal heat exchanger (52).

[0212] The refrigerant evaporated in the second internal heat exchanger (52) is introduced into the second outdoor unit (20), and after passing through the second accumulator (305), can be sucked into the second compressor (310).

[0213] Meanwhile, another portion of the refrigerant compressed in the second compressor (310) may be introduced into the second heat recovery device (50) through the second valve (322) and into the third heat exchange coil (362) through the third valve (340). The refrigerant is condensed in the third heat exchange coil (362), and the condensed refrigerant may be combined with the liquid pipe (335) through the first branch portion (335a).

[0214] The refrigerant combined in the above liquid pipe (335) can be depressurized in the second coil expansion valve (336) as described above and then evaporated in the second heat exchange coil (361).

[0215] Meanwhile, the first control valve (285) installed in the first tracheal branch pipe (280) of the first cycle section (1a) and the second control valve (385) installed in the second tracheal branch pipe (380) of the second cycle section (1b) are each turned off (closed), so that the flow of refrigerant through the first and second tracheal branch pipes (280, 380) may not occur.

[0216] Describes air flow.

[0217] The outside air introduced from the first outside air introduction section (81) of the first flow path (80) may be cooled and dehumidified as it passes through the first and second heat exchange coils (261, 361), and may be heated as it passes through the third heat exchange coil (362). Then, the air may be supplied to the indoor space through the first fan (83).

[0218] The air introduced through the indoor air introduction portion (91) of the second duct (90) can be heated in the heat recovery coil (251) and discharged to the outside through the first exhaust portion (92) via the second fan (93).

[0219] In this way, in the first mode operation of the air conditioning device (1), the operating pressure can be reduced and the input power of the first compressor (210) can be reduced by dissipating heat to the air side having a lower temperature than the outside air through the heat recovery coil (251). In addition, the cooling capacity can be improved by realizing a reduction in enthalpy on the evaporation inlet side in the first heat exchange coil (261).

[0220] In addition, as the supercooled air passes through the first and second heat exchange coils (261, 361) and the third heat exchange coil (362), reheat energy can be supplied to raise the temperature to the target temperature, so the power consumption of the device can be reduced.

[0221] Figure 3 is a cycle diagram showing the operation of the second mode of the air conditioning device according to an embodiment of the present invention.

[0222] Referring to FIG. 3, the air conditioning device (10) according to an embodiment of the present invention can be operated in a second mode. The second mode can be understood as a mode in which the device operates under conditions in which the outside temperature and humidity are relatively low. For example, the second mode can be operated in winter when the outside temperature is in the range of approximately -2 to 10°C, and the second mode can be referred to as a "winter mode."

[0223] In the second mode, both the first outdoor unit (10) of the first cycle unit (1a) and the second outdoor unit (20) of the second cycle unit (1b) can be operated in heating mode.

[0224] First, in the first cycle section (1a), when the first compressor (210) of the first outdoor unit (10) is driven, the refrigerant compressed in the first compressor (210) can flow into the first heat recovery device (40) through the second valve (222) and into the first heat exchange coil (261) through the third valve (240). The refrigerant is condensed in the first heat exchange coil (261), and the condensed refrigerant can flow through the liquid pipe (235).

[0225] Some of the refrigerant in the above liquid pipe (235) is branched from the first branch (235a), and the refrigerant branched from the first branch (235a) can be introduced into the heat recovery coil (251) through the heat recovery coil outlet pipe (253).

[0226] The refrigerant in the heat recovery coil outlet pipe (253) is depressurized in the control valve (254), and the depressurized refrigerant can be evaporated in the heat recovery coil (251). At this time, the temperature of the air passing through the second flow path (90) and the temperature of the heat recovery coil (251) can form room temperature, so frosting may not occur in the heat recovery coil (251).

[0227] The refrigerant evaporated in the above heat recovery coil (251) passes through the first internal heat exchanger (42) via the third valve (240), flows into the first accumulator (205), and can be sucked into the first compressor (210).

[0228] And, the remaining refrigerant other than the refrigerant branched from the first branch section (235a) can be introduced into the first outdoor unit (10) after exchanging heat with the refrigerant evaporated in the heat recovery coil (251) while passing through the first internal heat exchanger (42).

[0229] The refrigerant introduced into the first outdoor unit (10) is depressurized in the outdoor expansion valve (234) and then evaporated in the first outdoor heat exchanger (230). The evaporated refrigerant can be sucked into the first compressor (210) through the first accumulator (205).

[0230] Meanwhile, the amount of refrigerant (approximately 20 to 30%) flowing from the first branch portion (235a) toward the first outdoor heat exchanger (230) is formed to be less than the amount of refrigerant (approximately 70 to 80%) branched to the heat recovery coil (251), and accordingly, the evaporation temperature of the first outdoor heat exchanger (230) can be maintained above room temperature. Accordingly, frost formation in the first outdoor heat exchanger (230) can be prevented.

[0231] The amount of refrigerant flowing toward the first outdoor heat exchanger (230) and the amount of refrigerant branched to the heat recovery coil (251) can be controlled by the opening degree of the control valve (254) or the opening degree of the outdoor expansion valve (234).

[0232] Meanwhile, when the bypass fan (85a) is driven, at least a portion of the air at room temperature flowing through the second flow path (90) can flow into the first flow path (80) through the bypass duct (85) and into the first heat exchange coil (261).

[0233] Next, in the second cycle section (1b), when the second compressor (310) of the second outdoor unit (20) is driven, the refrigerant compressed in the second compressor (310) can flow into the second heat recovery device (50) through the second valve (322) and into the third heat exchange coil (362) through the third valve (340). The refrigerant is condensed in the third heat exchange coil (362), and the condensed refrigerant can flow into the liquid pipe (335) through the first branch section (335a).

[0234] The refrigerant flowing through the liquid pipe (335) may flow into the second internal heat exchanger (52) and then into the second outdoor unit (20). The refrigerant flowing into the second outdoor unit (20) may be depressurized in the outdoor expansion valve (334) and evaporated in the second outdoor heat exchanger (330). The evaporated refrigerant may be sucked into the second compressor (310) through the second accumulator (305).

[0235] At this time, the opening of the outdoor expansion valve (334) or the third coil expansion valve (337) can be adjusted so that the evaporation temperature of the second outdoor heat exchanger (330) can be maintained at room temperature. Accordingly, continuous heating operation can be performed through the third heat exchange coil (362) while avoiding frost formation of the second outdoor heat exchanger (330).

[0236] Meanwhile, since the second coil expansion valve (336) is closed, the refrigerant in the liquid pipe (335) does not flow into the second heat exchange coil (361) (stoppage of the second heat exchange coil). Accordingly, the refrigerant condensed in the third heat exchange coil (362) does not flow from the liquid pipe (335) toward the second heat exchange coil (361), but can flow toward the second internal heat exchanger (52).

[0237] The first control valve (285) installed in the first tracheal branch pipe (280) of the first cycle section (1a) and the second control valve (385) installed in the second tracheal branch pipe (380) of the second cycle section (1b) are each turned off (closed), so that the flow of refrigerant through the first and second tracheal branch pipes (280, 380) may not occur.

[0238] Accordingly, the refrigerant of the high pressure engine (227, 327) can be introduced into the first heat exchange coil (261) and the third heat exchange coil (362) without being bypassed to the first and second engine branch pipes (280, 380).

[0239] Describes air flow.

[0240] The outside air introduced from the first outside air introduction section (81) of the first flow section (80) is heated while passing through the first heat exchange coil (261), and can be further heated while exchanging heat with the third heat exchange coil (362).

[0241] The air introduced through the indoor air introduction portion (91) of the second flow path (90) is cooled as it passes through the heat recovery coil (251) and can be discharged to the outside through the first exhaust portion (92) via the second fan (93). At this time, the heat recovery coil (251) maintains the room temperature while exchanging heat with the room temperature air of the indoor space, thereby preventing frost formation.

[0242] In this way, in the second mode operation of the air conditioning device (1), the operating pressure can be increased by absorbing heat from air at a higher temperature than the outside air through the heat recovery coil (251), and the input power of the first compressor (210) can be reduced.

[0243] In addition, by preventing the entry into defrosting operation in the first and second outdoor heat exchangers (330), additional power saving and a decrease in the supply air temperature due to defrosting operation can be prevented.

[0244] Another example of this embodiment is proposed.

[0245] When the outside temperature is below zero, the possibility of frost formation in the first outdoor heat exchanger (230) may increase. In this case, all of the refrigerant condensed in the first heat exchange coil (261) flows from the first branch section (235a) to the coil outlet pipe (253), and the outdoor expansion valve (234) of the first outdoor unit (10) may be turned off.

[0246] Accordingly, the flow of refrigerant condensed in the first heat exchange coil (261) and then evaporated in the first outdoor heat exchanger (230) after being depressurized in the outdoor expansion valve (234) can be restricted. By stopping the first outdoor heat exchanger (230), frost formation on the first outdoor heat exchanger (230) can be prevented.

[0247] Figure 4 is a cycle diagram showing the operation of the third mode of the air conditioning device according to an embodiment of the present invention.

[0248] Referring to FIG. 4, the air conditioning device (10) according to an embodiment of the present invention can be operated in a third mode. The second mode can be understood as a defrosting mode that operates under conditions where the outside temperature and humidity are relatively low. For example, the third mode can be operated in winter when the outside temperature is in the range of approximately -2 to 4°C, and the third mode can be called a "winter defrosting mode."

[0249] In the above second mode, the first outdoor unit (10) of the first cycle unit (1a) can be operated in the defrosting mode, and the second outdoor unit (20) of the second cycle unit (1b) can be operated in the heating mode.

[0250] First, in the first cycle section (1a), when the first compressor (210) of the first outdoor unit (10) is driven, at least a portion of the refrigerant compressed in the first compressor (210) flows into the first outdoor heat exchanger (230) through the first valve (220), and the refrigerant condensed in the first outdoor heat exchanger (230) can flow into the first internal heat exchanger (42) through the liquid pipe (235).

[0251] During the process in which the refrigerant passes through the first outdoor heat exchanger (230), the first outdoor heat exchanger (230) can be defrosted.

[0252] The ratio of the refrigerant compressed in the first compressor (210) and flowing into the first outdoor heat exchanger (230) through the first valve (220) may be 50% or more. For example, the ratio of the refrigerant flowing into the first outdoor heat exchanger (230) may be formed within the range of 75 to 85%.

[0253] The outdoor fan provided on one side of the first outdoor heat exchanger (230) can be turned off.

[0254] And, the ratio of the remaining refrigerant among the refrigerant compressed in the first compressor (210), that is, the refrigerant flowing into the first heat exchange coil (261) through the second valve (222), can be formed within the range of 15 to 25%.

[0255] The refrigerant in the above liquid pipe (235) can be further condensed by exchanging heat with the refrigerant of the low pressure engine (264) in the first internal heat exchanger (42). The additionally condensed refrigerant flows into the heat recovery coil outlet pipe (253) in the first branch section (235a), is depressurized in the control valve (254), and then flows into the heat recovery coil (251) to evaporate.

[0256] The refrigerant evaporated in the above heat recovery coil (261) flows through the low pressure engine (264) and can exchange heat (additionally evaporate) with the refrigerant in the liquid pipe (235) in the first internal heat exchanger (42).

[0257] The refrigerant that has undergone heat exchange in the first internal heat exchanger (42) is introduced into the first outdoor unit (10), and after passing through the first accumulator (205), can be sucked into the first compressor (210).

[0258] Meanwhile, another portion of the refrigerant compressed in the first compressor (210) may flow into the first heat recovery device (40) through the second valve (222) and into the first heat exchange coil (261) through the third valve (240). The refrigerant is condensed in the first heat exchange coil (261), and the condensed refrigerant may flow into the liquid pipe (235).

[0259] And, the refrigerant flows into the heat recovery coil outlet pipe (253) from the first branch section (235a), is depressurized in the control valve (254), and then flows into the heat recovery coil (251) to evaporate.

[0260] Meanwhile, the first control valve (285) installed in the first engine branch pipe (280) of the first cycle section (1a) is turned on (opened), so that some of the refrigerant of the high-pressure engine (227) does not flow into the third valve (240) but is bypassed to the first engine branch pipe (280).

[0261] The above-mentioned bypassed refrigerant can be depressurized in the first control valve (285) and introduced into the first outdoor unit (10) through the first internal heat exchanger (42). Then, the refrigerant can be sucked into the first compressor (210) through the first accumulator (205).

[0262] When the above bypass fan (85a) is driven, at least a portion of the relatively high temperature air flowing in the second flow path (90) can flow into the first flow path (80) through the bypass duct (85) and into the first heat exchange coil (261).

[0263] Next, in the second cycle section (1b), when the second compressor (310) of the second outdoor unit (20) is driven, the refrigerant compressed in the second compressor (310) can flow into the second heat recovery device (50) through the second valve (322) and into the second heat exchange coil (361) through the third valve (340). The refrigerant is condensed in the second heat exchange coil (361), and the condensed refrigerant can flow through the liquid pipe (335).

[0264] The refrigerant flowing through the liquid pipe (335) may flow into the second internal heat exchanger (52) and then into the second outdoor unit (20). The refrigerant flowing into the second outdoor unit (20) may be depressurized in the outdoor expansion valve (334) and evaporated in the second outdoor heat exchanger (330). The evaporated refrigerant may be sucked into the second compressor (310) through the second accumulator (305).

[0265] Meanwhile, since the third coil expansion valve (337) is closed, the refrigerant in the liquid pipe (335) does not flow into the third heat exchange coil (362) (stoppage of the third heat exchange coil). Accordingly, the refrigerant condensed in the second heat exchange coil (361) does not flow from the first branch portion (335a) toward the heat exchange coil outlet pipe (353), but can flow toward the second internal heat exchanger (52).

[0266] The second control valve (385) installed in the second branch pipe (380) of the second cycle section (1b) is turned off (closed), so that the flow of refrigerant through the second branch pipe (380) may not occur. Accordingly, the refrigerant of the high-pressure engine (327) may not be bypassed to the second branch pipe (380) and may flow into the second heat exchange coil (361).

[0267] In this way, while the first outdoor heat exchanger (230) of the first cycle section (1a) is being heated, heat is dissipated in the second heat exchange coil (361) of the second cycle section (1b), so that heating can be continuously performed.

[0268] When the defrosting of the first outdoor heat exchanger (230) is completed, the first outdoor unit (10) is operated in heating mode and the second outdoor unit (20) is operated in defrosting mode, so that the defrosting of the second outdoor heat exchanger (330) can be performed.

[0269] Describes air flow.

[0270] The outside air introduced from the first outside air introduction section (81) of the first duct (80) is heated while passing through the first heat exchange coil (261), and can be further heated while exchanging heat with the second heat exchange coil (361).

[0271] The air introduced through the indoor air introduction portion (91) of the second duct (90) is cooled as it passes through the heat recovery coil (251) and can be discharged to the outside through the first exhaust portion (92) via the second fan (93).

[0272] In this way, in the third mode operation of the air conditioning device (1), even if the first heat exchange coil (261) performs minimum heating by absorbing heat from air at a temperature higher than the outside air through the heat recovery coil (251), a cycle can be induced in which the defrosting ability is not insufficient and normal heating is possible within the shortest time when returning to heating operation after defrosting operation.

[0273] Figure 5 is a cycle diagram showing the operation of the fourth mode of the air conditioning device according to an embodiment of the present invention.

[0274] Referring to FIG. 5, the air conditioning device (10) according to an embodiment of the present invention can be operated in a fourth mode. The fourth mode can be understood as a mode that operates under conditions where the outside temperature is significantly low. For example, the third mode can be operated during the low-temperature winter season when the outside temperature is below approximately -2°C, and the fourth mode can be referred to as a "low-temperature winter mode."

[0275] In the aforementioned low-temperature winter season, the outdoor temperature is low, but the humidity is relatively mild, so the dehumidification load may not be significant. Therefore, rather than focusing on dehumidification, heating can be focused on supplying air to indoor spaces.

[0276] In the above fourth mode, both the first outdoor unit (10) and the second cycle unit (1b) of the first cycle unit (1a) can perform the heating mode.

[0277] First, in the first cycle section (1a), when the first compressor (210) of the first outdoor unit (10) is driven, the refrigerant compressed in the first compressor (210) can flow into the first heat recovery device (40) through the second valve (222) and into the first heat exchange coil (261) through the third valve (240). The refrigerant is condensed in the first heat exchange coil (261), and the condensed refrigerant can flow through the liquid pipe (235).

[0278] The refrigerant of the above liquid pipe (235) flows into the heat recovery coil outlet pipe (253) from the first branch section (235a) and can flow to the heat recovery coil (251). The refrigerant of the heat recovery coil outlet pipe (253) is depressurized in the control valve (254), and the depressurized refrigerant can be evaporated in the heat recovery coil (251).

[0279] The refrigerant evaporated in the above heat recovery coil (251) passes through the first internal heat exchanger (42) via the third valve (240), flows into the first accumulator (205), and can be sucked into the first compressor (210).

[0280] Meanwhile, the outdoor expansion valve (234) of the first outdoor unit (10) is turned off, and thus the flow flowing from the first branch (235a) through the first internal heat exchanger (42) to the first outdoor unit (10) can be restricted. Accordingly, the first outdoor heat exchanger (230) is stopped, thereby reducing the possibility of frost formation on the first outdoor heat exchanger (230).

[0281] Meanwhile, when the bypass fan (85a) is driven, at least a portion of the air at room temperature flowing through the second flow path (90) can flow into the first flow path (80) through the bypass duct (85) and into the first heat exchange coil (261). Therefore, it can help to increase the temperature of the air in the first flow path (80).

[0282] Next, in the second cycle section (1b), when the second compressor (310) of the second outdoor unit (20) is driven, the refrigerant compressed in the second compressor (310) can flow into the second heat recovery device (50) through the second valve (322) and into the second heat exchange coil (361) through the third valve (340). The refrigerant is condensed in the second heat exchange coil (361), and the condensed refrigerant can flow into the liquid pipe (335) through the first branch section (335a).

[0283] The refrigerant flowing through the liquid pipe (335) may flow into the second internal heat exchanger (52) and then into the second outdoor unit (20). The refrigerant flowing into the second outdoor unit (20) may be depressurized in the outdoor expansion valve (334) and evaporated in the second outdoor heat exchanger (330). The evaporated refrigerant may be sucked into the second compressor (310) through the second accumulator (305).

[0284] At this time, the opening of the outdoor expansion valve (334) can be adjusted so that the evaporation temperature of the second outdoor heat exchanger (330) can be maintained at room temperature. Accordingly, continuous heating operation can be performed through the third heat exchange coil (362) while avoiding frost formation of the second outdoor heat exchanger (330).

[0285] Meanwhile, since the third coil expansion valve (337) is closed, the refrigerant in the liquid pipe (335) does not flow into the third heat exchange coil (362). Accordingly, the refrigerant condensed in the second heat exchange coil (361) does not flow from the liquid pipe (335) toward the third heat exchange coil (362), but can flow toward the second internal heat exchanger (52).

[0286] That is, since the second heat exchange coil (361) having a larger heat transfer area than the heat exchange coil (362) is used as a condenser, heating capacity and system efficiency can be improved.

[0287] The first control valve (285) installed in the first tracheal branch pipe (280) of the first cycle section (1a) and the second control valve (385) installed in the second tracheal branch pipe (380) of the second cycle section (1b) are each turned off (closed), so that the flow of refrigerant through the first and second tracheal branch pipes (280, 380) may not occur.

[0288] Accordingly, the refrigerant of the high pressure engine (227, 327) can be introduced into the first heat exchange coil (261) and the second heat exchange coil (361) without being bypassed to the first and second engine branch pipes (280, 380), respectively.

[0289] Describes air flow.

[0290] The outside air introduced from the first outside air introduction section (81) of the first duct (80) is heated while passing through the first heat exchange coil (261), and can be further heated while exchanging heat with the second heat exchange coil (361).

[0291] The air introduced through the indoor air introduction portion (91) of the second flow path (90) is cooled as it passes through the heat recovery coil (251) and can be discharged to the outside through the first exhaust portion (92) via the second fan (93). At this time, the heat recovery coil (251) maintains the room temperature while exchanging heat with the room temperature air of the indoor space, thereby preventing frost formation.

[0292] In this way, in the second mode operation of the air conditioning device (1), the operating pressure can be increased by absorbing heat from air at a higher temperature than the outside air through the heat recovery coil (251), and the input power of the first compressor (210) can be reduced.

[0293] Figure 6 is a cycle diagram showing the operation of the fifth mode of the air conditioning device according to an embodiment of the present invention.

[0294] Referring to FIG. 6, the air conditioning device (10) according to an embodiment of the present invention can be operated in a fifth mode. The fifth mode can be understood as a mode in which the device is operated under ambient temperature conditions. For example, the fifth mode can be operated during the inter-season when the ambient temperature is in the range of approximately 10 to 30°C, and the first mode can be referred to as an "inter-seasonal mode."

[0295] First, in the second mode, the first cycle section (1a) can be stopped. Accordingly, the first compressor (210) is turned off, and the refrigerant does not flow through the first heat recovery device (40), the first heat exchange coil (261), and the heat recovery coil (251).

[0296] Next, the second outdoor unit (20) of the first cycle section (1b) can be operated in cooling mode.

[0297] Next, in the second cycle section (1b), when the second compressor (310) of the second outdoor unit (20) is driven, at least a portion of the refrigerant compressed in the second compressor (310) flows into the second outdoor heat exchanger (330) through the first valve (320), and the refrigerant condensed in the second outdoor heat exchanger (330) can flow into the second internal heat exchanger (52) through the liquid pipe (335).

[0298] The ratio of the refrigerant compressed in the second compressor (310) and flowing into the second outdoor heat exchanger (330) through the first valve (320) may be 50% or less. For example, the ratio of the refrigerant flowing into the second outdoor heat exchanger (330) may be formed within the range of 15 to 25%.

[0299] The outdoor fan provided on one side of the second outdoor heat exchanger (330) can be operated at a minimum RPM.

[0300] And, the ratio of the remaining refrigerant among the refrigerant compressed in the second compressor (310), that is, the refrigerant flowing into the third heat exchange coil (362) through the second valve (322), can be formed within the range of 75 to 85%.

[0301] By distributing the refrigerant in this manner, a relatively large amount of the high-pressure refrigerant compressed in the second compressor (310) flows to the third heat exchange coil (362), thereby increasing the reheating efficiency.

[0302] The refrigerant in the above liquid pipe (235) can be further condensed by exchanging heat with the refrigerant of the low-pressure engine (364) in the second internal heat exchanger (52). The additionally condensed refrigerant can be depressurized in the second coil expansion valve (336) and then introduced into the second heat exchange coil (361) to evaporate. During the evaporation process of the second heat exchange coil (361), the air can be cooled and dehumidified, thereby increasing the dehumidification performance.

[0303] The refrigerant evaporated in the second heat exchange coil (361) flows through the low pressure engine (364) and can exchange heat (additionally evaporate) with the refrigerant in the liquid pipe (335) in the second internal heat exchanger (52).

[0304] The refrigerant evaporated in the second internal heat exchanger (52) is introduced into the second outdoor unit (20), and after passing through the second accumulator (305), can be sucked into the second compressor (310).

[0305] Meanwhile, another portion of the refrigerant compressed in the second compressor (310) may be introduced into the second heat recovery device (50) through the second valve (322) and into the third heat exchange coil (362) through the third valve (340). The refrigerant is condensed in the third heat exchange coil (362), and the condensed refrigerant may be combined with the liquid pipe (335) through the first branch portion (335a).

[0306] The refrigerant combined in the above liquid pipe (335) can be depressurized in the second coil expansion valve (336) as described above and then evaporated in the second heat exchange coil (361).

[0307] Meanwhile, since the first cycle section (1a) is stopped, the first control valve (285) installed in the first organ branch pipe (280) can be turned off (closed).

[0308] The second control valve (385) installed in the second organ branch pipe (380) of the second cycle section (1b) can be turned off (closed) or on (opened) based on the temperature of the air supplied through the first flow section (80) or the temperature of the indoor space.

[0309] For example, when the temperature of the air extracted through the indoor supply section (82) of the first duct (80) or the temperature of the indoor space is formed within the set range, the second control valve (385) can be turned off (closed).

[0310] However, if the temperature of the air being extracted or the temperature of the indoor space is formed to be above the set range, i.e., if the amount of reheating heat through the third heat exchange coil (363) is excessive, the opening degree of the third coil expansion valve (337) can be reduced to a setting degree (for example, 30%) or less to induce a reduction in the amount of reheating heat.

[0311] However, when the opening of the third coil expansion valve (337) decreases, a phenomenon of liquid refrigerant accumulation occurs within the third heat exchange coil (362), resulting in a phenomenon of refrigerant shortage in the entire cycle, and thus a problem of a decrease in cooling and dehumidifying capacity due to a lack of capacity in the second heat exchange coil (361) may occur.

[0312] Accordingly, in order to solve this problem, the second control valve (385) can be opened by a set opening amount (for example, 40%). By opening the second control valve (385), the refrigerant of the high-pressure engine (327) is bypassed to the second engine branch pipe (380), thereby preventing the accumulation of liquid refrigerant in the third heat exchange coil (362).

[0313] Thereafter, when the exhaust temperature of the air supplied to the indoor space decreases or the temperature of the indoor space decreases and forms within the set range, the opening degree of the second control valve (385) can be gradually reduced. By such control, the amount of reheat heat in the third heat exchange coil (362) can be reduced.

[0314] Describes air flow.

[0315] The outside air introduced from the first outside air introduction section (81) of the first flow path (80) may be cooled and dehumidified as it passes through the second heat exchange coil (361), and may be heated as it passes through the third heat exchange coil (362). Then, the air may be supplied to the indoor space through the first fan (83).

[0316] In the process of the air supercooled through the second heat exchange coil (361) passing through the third heat exchange coil (362), reheat energy can be supplied to raise the temperature to the target temperature, so the power consumption of the device can be reduced.

[0317] Due to the stoppage of the first cycle section (1a), air flow in the second flow section (90) may not occur.

[0318] The present invention relates to an air conditioning device, and provides an air conditioning device having a plurality of cycle sections, thereby enabling the device to dehumidify air and easily supply it to an indoor space. Therefore, the present invention has significant industrial applicability.

Claims

1. A first outdoor unit including a first compressor and a first outdoor heat exchanger; A first heat recovery device fluidly connected to the first outdoor unit and having a first internal heat exchanger; A second outdoor unit including a second compressor and a second outdoor heat exchanger; A second heat recovery device fluidly connected to the second outdoor unit and having a second internal heat exchanger; and An air treatment device comprising a plurality of heat exchangers fluidly connected to the first and second heat recovery devices, The above air treatment device, A first flow path is formed to introduce air from the outside and supply it to the room, and a heat exchange coil is arranged among the plurality of heat exchangers; and An air conditioning device that forms a path for exhausting indoor air to the outside and includes a second path section in which a heat recovery coil among the plurality of heat exchangers is arranged.

2. In paragraph 1, The first heat recovery device includes a first valve device connected to the first internal heat exchanger, An air conditioning device in which the first valve device operates to guide the refrigerant compressed in the first compressor to the heat recovery coil of the second flow path section or the heat exchange coil of the first flow path section.

3. In paragraph 2, The first outdoor unit includes a high-pressure engine that guides the refrigerant compressed in the first compressor to the first valve device, An air conditioning device including a first branch pipe branched from the inlet side of the first valve device and bypassed to the first outdoor unit side, wherein the first heat recovery device is a first heat recovery device.

4. In paragraph 3, An air conditioning device in which a first control valve for opening or closing the first tracheal branch pipe is installed in the first tracheal branch pipe, and the first control valve is configured as an electronic expansion valve (EEV) whose opening can be adjusted for reducing the pressure of the refrigerant.

5. In paragraph 2, The inlet pipe of the heat recovery coil of the second euro section is connected to the first valve device, An air conditioning device in which, in the first mode of operation when the outside temperature is higher than the set temperature, the inlet pipe of the heat recovery coil forms a high-pressure passage through which the refrigerant compressed in the first compressor flows.

6. In paragraph 2, The outlet pipe of the heat recovery coil of the second euro section is connected to the first valve device, An air conditioner in which, in the second mode of operation when the outside temperature is lower than the set temperature, the outlet pipe of the heat recovery coil forms a path through which low-pressure refrigerant evaporated in the heat recovery coil flows.

7. In paragraph 1, The heat exchange coil disposed in the first flow section includes a first heat exchange coil that is fluidly connected to the first heat recovery device and introduces refrigerant that has passed through the heat recovery coil of the second flow section. An air conditioning device in which the first heat exchange coil is an evaporator for cooling and dehumidifying air in the first flow path by evaporating refrigerant decompressed by a first coil expansion valve disposed on the inlet side of the first heat exchange coil.

8. In paragraph 1, An air conditioning device in which the heat exchange coil disposed in the first flow section includes a first heat exchange coil that introduces refrigerant compressed in the first compressor, and the first heat exchange coil is a condenser for raising the temperature of air in the first flow section.

9. In paragraph 1, The above air treatment device, A bypass duct connecting the first euro section and the second euro section; and An air conditioning device including a bypass fan operable to supply room temperature air passing through the second flow section to the first flow section.

10. In paragraph 1, The heat exchange coil disposed in the first section includes a plurality of heat exchange coils fluidly connected to the second heat recovery coil, An air conditioner comprising a plurality of heat exchange coils, wherein the plurality of heat exchange coils comprises a second heat exchange coil and a third heat exchange coil disposed on the outlet side of the second heat exchange coil based on air flow.

11. In paragraph 10, An air conditioner in which the capacity or heat transfer area of ​​the second heat exchange coil is formed to be larger than the capacity or heat transfer area of ​​the third heat exchange coil.

12. In paragraph 10, An air conditioning device in which the second heat exchange coil constitutes an evaporator for cooling and dehumidifying the air in the first flow section, and the third heat exchange coil constitutes a condenser for heating the air in the first flow section.

13. In paragraph 10, The second heat exchange coil and the third heat exchange coil are, An air conditioning device disposed on the outlet side of a first heat exchange coil that is disposed in the first euro section and fluidly connected to the first heat recovery device based on air flow.

14. In paragraph 10, An air conditioning device wherein the second heat recovery device includes a second valve device connected to the second internal heat exchanger, and the second valve device operates to guide the refrigerant compressed in the second compressor to the third heat exchange coil.

15. In paragraph 10, Including a second coil expansion valve provided on the inlet side of the second heat exchange coil, An air conditioning device in which the second valve device operates to introduce refrigerant that has been depressurized in the second coil expansion valve and then evaporated in the second heat exchange coil.

16. A first outdoor unit including a first compressor and a first outdoor heat exchanger; A first heat recovery device fluidly connected to the first outdoor unit and having a first internal heat exchanger and a first valve device; A second outdoor unit including a second compressor and a second outdoor heat exchanger; A second heat recovery device fluidly connected to the second outdoor unit and having a second internal heat exchanger and a second valve device; An air treatment device including a first flow path for introducing air from the outside and supplying it to the room, and a second flow path for exhausting air from the room to the outside, wherein a heat recovery coil and a first heat exchange coil are arranged in fluid connection with the first valve device; and An air conditioning device including a first branch pipe branched from the inlet side of the first valve device and preventing at least a portion of the refrigerant compressed in the first compressor from flowing into the heat recovery coil or the first heat exchange coil.

17. In paragraph 16, The air handling device includes a second heat exchange coil and a third heat exchange coil fluidly connected to the second valve device, An air conditioning device including a second branch pipe branched from the inlet side of the second valve device and preventing at least a portion of the refrigerant compressed in the second compressor from flowing into the third heat exchange coil.

18. In paragraph 17, An air conditioning device in which an electronic expansion valve (EEV) capable of controlling opening is installed in the first or second tracheal branch pipe to reduce the pressure of the refrigerant.

19. In paragraph 17, An air conditioner in which the first heat exchange coil, the second heat exchange coil, and the third heat exchange coil are installed in the first flow path, and the heat recovery coil is installed in the second flow path.

20. In paragraph 19, The first valve device operates to guide the refrigerant compressed in the first compressor to the heat recovery coil of the second flow path section or the first heat exchange coil of the first flow path section, An air conditioning device in which the second valve device operates to guide the refrigerant compressed in the second compressor to the third heat exchange coil of the first flow path.

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