JP7031650B2 - Air conditioner - Google Patents

Description

The present invention relates to an indoor unit of an air conditioner.

In the air conditioner, the outdoor unit installed outdoors and the indoor unit installed in the air conditioning room are connected by a refrigerant pipe, and the air conditioner is a ceiling-embedded type installed behind the ceiling as an indoor unit (hereinafter,). There is a ceiling-embedded air conditioner), but in recent years, it has been desired to increase the heat exchange capacity as a ceiling-embedded air conditioner.

As a ceiling-embedded air conditioner for increasing the heat exchange capacity, Patent Document 1 shown in FIG. 4 has an air outlet 14b arranged on the front side and an air suction port 14a arranged on the back side. Inside the housing 10, a first heat exchanger 20A as an indoor heat exchanger arranged closer to the front side and a second heat exchanger 20B as an indoor heat exchanger arranged closer to the back side. A sirocco fan 30 arranged between the first heat exchanger 20A and the second heat exchanger 20B, and a first heat exchanger arranged below the first heat exchanger 20A and the second heat exchanger 20B. The drain pan 40 that collects the dew condensation water adhering to the 20A and the second heat exchanger 20B, and the outlet air passage 33b and the air outlet 14b so as to guide the air blown out from the outlet air passage 33b of the sirocco fan 30 to the air outlet 14b. A first space S1 in which an air suction port 14a opens between the second heat exchanger 20B and the back plate 12, and a first heat exchanger 20A and a front plate 11 are provided with a blowout guide 50 for connecting the two. A ceiling-embedded air exchanger in which a third space S3 and a second space S2 connected to the first space S1 and the third space S3 are formed between the drain pan 40 and the bottom plate 14. A 100A indoor unit is disclosed.
In addition, when the air conditioner is cooled, the area around the indoor heat exchanger becomes highly humid, and germs (including mold) grow and generate a foul odor. The inside of the indoor unit is purified by using a known purification means such as.

Japanese Unexamined Patent Publication No. 2019-203629

In the case of an indoor unit having a structure in which a plurality of indoor heat exchangers are arranged, such as the ceiling-embedded air conditioner disclosed in Patent Document 1, each of the plurality of indoor units may be used even if an ion generator or the like as a purification means is used. There is a problem that the indoor heat exchanger cannot be sufficiently sterilized.
In view of the above problems, the present invention comprises an outdoor unit provided with a compressor and a four-way valve, an indoor unit including a plurality of indoor heat exchangers and an indoor unit fan, and connected to the outdoor unit, and at least a compressor and an indoor unit fan. An air conditioner that controls multiple indoor heat exchangers to function as an evaporator in the case of cooling and as a condenser in the case of heating to control the temperature of the room in which the indoor unit is installed. In the present invention, an air conditioner capable of disinfecting a plurality of indoor heat exchangers is provided.

One aspect of the present invention includes a compressor, a four-way valve, a plurality of indoor heat exchangers, a refrigeration circuit in which an expansion valve is connected to circulate a refrigerant, an outdoor unit having a compressor and a four-way valve, and a plurality of indoor heats. It is equipped with an indoor unit that includes an exchanger and an indoor unit fan and is connected to the outdoor unit, and at least controls the compressor, the indoor unit fan, and the four-way valve to function as an evaporator in the case of cooling multiple indoor heat exchangers. In the air exchanger that controls the temperature in the room where the indoor unit is installed by functioning as a condenser in the case of heating, the indoor unit has an air suction port and an air outlet, and these air suction ports. From the housing having a plurality of ventilation passages branching from the air suction port between the air outlet and at least one indoor heat exchanger arranged in each of the plurality of ventilation passages, and from the air suction port. Equipped with an indoor unit fan that guides the sucked air to the air outlet via each of multiple ventilation passages, the ventilation resistance of one ventilation passage is greater than the ventilation resistance of the other ventilation passages, and the ventilation resistance The amount of refrigerant flowing through one indoor heat exchanger arranged in one ventilation path according to the size of is set to be smaller than the amount of refrigerant flowing through other indoor heat exchangers arranged in another ventilation path. , When multiple indoor heat exchangers function as evaporators, the dew condensation water adhering to the indoor heat exchangers is heated to a predetermined temperature by making the multiple indoor heat exchangers function as condensers, and multiple indoor heat exchanges are performed. It is an air conditioner that heats and disinfects the vessel.

According to the present invention, when a plurality of indoor heat exchangers function as evaporators, the dew condensation water adhering to the indoor heat exchangers is heated to a predetermined temperature by making the plurality of indoor heat exchangers function as condensers. Since heat sterilization of a plurality of indoor heat exchangers is performed, it is possible to provide an air conditioner capable of sterilizing a plurality of indoor heat exchangers.
According to the present invention, the ventilation resistance of one of the ventilation passages is larger than the ventilation resistance of the other ventilation passages, and the one of the above is arranged in the one ventilation passage according to the magnitude of the ventilation resistance. Since the amount of refrigerant flowing through the indoor heat exchanger is set to be smaller than the amount of refrigerant flowing through the other indoor heat exchangers arranged in the other ventilation passages, it is set to the temperature of one of the indoor heat exchangers. Since the temperature of the other indoor heat exchangers can be heated without any difference, it is possible to provide an air conditioner capable of suppressing imbalance in the sterilization of each indoor heat exchanger.

It is a refrigerating circuit diagram of an indoor harmonizer. It is an enlarged view of the indoor heat exchanger in the refrigeration circuit diagram. It is sectional drawing of an indoor unit. It is sectional drawing of the indoor unit of the conventional ceiling-embedded type air conditioner.

Hereinafter, embodiments of the present invention will be described in detail with reference to the accompanying drawings. As an embodiment, an air conditioner capable of performing cooling operation and heating operation by connecting an indoor unit to an outdoor unit and arranging two indoor heat exchangers in the indoor unit will be described as an example. The present invention is not limited to the following embodiments, and various modifications can be made without departing from the gist of the present invention.

FIG. 1 schematically shows a configuration of a refrigerating circuit of an air conditioner 11 according to an embodiment of the present invention. The air conditioner 11 includes an indoor unit 12 and an outdoor unit 13. The indoor unit 12 is installed, for example, in an indoor space inside a building. In addition, the indoor unit 12 may be installed in a space corresponding to the indoor space. The indoor unit 12 incorporates an indoor heat exchanger 14 as a heat exchanger. The outdoor unit 13 incorporates a compressor 15, an outdoor heat exchanger 16, an expansion valve 17, and a four-way valve 18. The indoor heat exchanger 14, the compressor 15, the outdoor heat exchanger 16, the expansion valve 17, and the four-way valve 18 form a refrigerating circuit 19. The outdoor unit 13 may be installed outdoors where heat exchange with the outdoor air is possible.

The refrigeration circuit 19 includes a first circulation path 21. The first circulation path 21 connects the first port 18a and the second port 18b of the four-way valve 18 to each other. A compressor 15 is provided in the first circulation path 21. The suction pipe 15a of the compressor 15 is connected to the first port 18a of the four-way valve 18 via a refrigerant pipe. The gas refrigerant is supplied from the first port 18a to the suction pipe 15a of the compressor 15. The compressor 15 compresses the low pressure gas refrigerant to a predetermined pressure. The discharge pipe 15b of the compressor 15 is connected to the second port 18b of the four-way valve 18 via a refrigerant pipe. The gas refrigerant is supplied from the discharge pipe 15b of the compressor 15 to the second port 18b of the four-way valve 18. The refrigerant pipe may be, for example, a copper pipe.
Although the four-way valve 18 is used as a flow path switching valve, a plurality of solenoid valves may be combined instead of the four-way valve 18.

The refrigeration circuit 19 further includes a second circulation path 22. The second circulation path 22 connects the third port 18c and the fourth port 18d of the four-way valve 18 to each other. The outdoor heat exchanger 16, the expansion valve 17, and the indoor heat exchanger 14 are incorporated in the second circulation path 22 in order from the third port 18c side. The outdoor heat exchanger 16 exchanges heat energy between the passing refrigerant and the surrounding air. The indoor heat exchanger 14 exchanges heat energy between the passing refrigerant and the surrounding air.
Although the indoor heat exchanger 14 is shown as one unit in FIG. 1, as will be described later in the description of FIG. 2, the indoor heat exchanger 14 has two first heat exchangers 14A and a second heat. It is composed of an exchanger 14B.

A blower fan 23 is incorporated in the outdoor unit 13. The blower fan 23 ventilates the outdoor heat exchanger 16. The blower fan 23 generates an air flow according to the rotation of the impeller, for example. The airflow passes through the outdoor heat exchanger 16 by the action of the blower fan 23. The outdoor air passes through the outdoor heat exchanger 16 and exchanges heat with the refrigerant. The heat-exchanged cold or warm airflow is blown out from the outdoor unit 13. The flow rate of the airflow passing through is adjusted according to the rotation speed of the impeller.

The sirocco fan 24 as an indoor unit fan is incorporated in the indoor unit 12. The sirocco fan 24 ventilates the indoor heat exchanger 14. The sirocco fan 24 generates an air flow according to the rotation of the impeller. Indoor air is sucked into the indoor unit 12 by the action of the sirocco fan 24. The indoor air passes through the indoor heat exchanger 14 and exchanges heat with the refrigerant. The heat-exchanged cold or warm airflow is blown out from the indoor unit 12. The flow rate of the airflow passing through is adjusted according to the rotation speed of the impeller.

When the cooling operation is carried out in the refrigeration circuit 19, the four-way valve 18 connects the second port 18b and the third port 18c to each other, and connects the first port 18a and the fourth port 18d to each other. Therefore, the high-temperature and high-pressure refrigerant is supplied to the outdoor heat exchanger 16 from the discharge pipe 15b of the compressor 15. The refrigerant flows through the outdoor heat exchanger 16, the expansion valve 17, and the indoor heat exchanger 14 in order. The outdoor heat exchanger 16 dissipates heat from the refrigerant to the outside air. The expansion valve 17 reduces the pressure of the refrigerant to a low pressure. The decompressed refrigerant absorbs heat from the surrounding air in the indoor heat exchanger 14. Cold air is generated. The cold air is blown into the interior space by the action of the blower fan 24.

When the heating operation is carried out in the refrigeration circuit 19, the four-way valve 18 connects the second port 18b and the fourth port 18d to each other, and connects the first port 18a and the third port 18c to each other. A high-temperature and high-pressure refrigerant is supplied from the compressor 15 to the indoor heat exchanger 14. The refrigerant flows through the indoor heat exchanger 14, the expansion valve 17, and the outdoor heat exchanger 16 in order. The indoor heat exchanger 14 dissipates heat from the refrigerant to the surrounding air. Warm air is generated. Warm air is blown into the interior space by the action of the sirocco fan 24. The expansion valve 17 reduces the pressure of the refrigerant to a low pressure. The decompressed refrigerant absorbs heat from the surrounding air by the outdoor heat exchanger 16. After that, the refrigerant returns to the compressor 15. The maximum temperature of the indoor heat exchanger 14 when the heating operation is being performed is 53 ° C.

The air conditioner 11 includes a temperature sensor 26a and a humidity sensor 26b. The temperature sensor 26a is connected to the indoor heat exchanger 14. The temperature sensor 26a measures the temperature of the indoor heat exchanger 14. The temperature sensor 26a outputs a temperature signal including temperature information of the measured temperature. The humidity sensor 26b is installed in the indoor unit 12. The humidity sensor 26b measures the relative humidity in the indoor unit 12. The humidity sensor 26b outputs a humidity signal including humidity information of the measured humidity.

The air conditioner 11 includes a control unit 27. The control unit 27 is formed on, for example, a control board (not shown) incorporated in the outdoor unit 13. The four-way valve 18, the expansion valve 17, and the compressor 15 in the outdoor unit 13 are electrically connected to the control unit 27 by individual signal lines. Similarly, the drive motor of the sirocco fan 24 in the indoor unit 12, the temperature sensor 26a, and the humidity sensor 26b are electrically connected to the control unit 27 by individual signal lines. The control unit 27 has a four-way valve 18 in the outdoor unit 13, an expansion valve 17 and a compressor 15, and a sirocco fan 24 in the indoor unit 12 based on the temperature signal from the temperature sensor 26a and the humidity signal from the humidity sensor 26b. Controls the behavior of. As a result of such control, as will be described later, the cooling operation, the heating operation, and the heating sterilization operation of the air conditioner 11 are realized. The control unit 27 can control the operation of the sirocco fan 24 during the cooling operation or the heating operation based on the operation signal input from the remote controller to the indoor unit 12, and can change the air volume of the cold air or the warm air.

FIG. 3 schematically shows a cross section of the indoor unit 12 according to the embodiment. The indoor unit 12 is an indoor unit of a ceiling-embedded air conditioner, and is installed behind the ceiling 100 in the room. The indoor unit 12 is entirely surrounded by a housing 30. The housing 30 includes a front plate 31, a back plate 32, a top plate 33, a bottom plate 36 having an air suction port 34 and an air outlet 35, a left side plate (not shown) provided on the back side of the paper surface of FIG. 3, and FIG. It is a box type having a right side plate (not shown) provided on the front side of the paper surface, the air suction port 34 is arranged on the side of the back plate 32, and the air outlet 35 is arranged on the front plate 31 side of the air suction port 34. ing. Since the lower surface of the bottom plate 36 is exposed indoors, the lower surface thereof is provided with a design (not shown) necessary for a decorative plate.

A flat plate-shaped first heat exchanger 14A is attached to the side of the front surface plate 11 of the lower surface 33a of the top plate 33 in a posture perpendicular to the top plate 33. Further, a flat plate-shaped second heat exchanger 14B is similarly attached to the side of the back plate 32 of the lower surface 33a of the top plate 33 in a posture perpendicular to the top plate 33. A sirocco fan 24 is arranged between the first heat exchanger 14A and the second heat exchanger 14B.
The sirocco fan 24 has a fan motor 41, an impeller 42 fixed to the rotating shaft 41a of the fan motor 41, and a suction port 44 leading to the impeller 42 on the side surface thereof, and faces the outer peripheral surface of the impeller 42 on the lower surface. It has a fan casing 43 in which a blowout air passage 45 is formed.

Under the first heat exchanger 14A and the second heat exchanger 14B, a drain pan 40 for collecting the dew condensation water generated in the first heat exchanger 14A and the second heat exchanger 14B is arranged.
Inside the housing 30, a first space S1 that functions as a ventilation path is formed between the second heat exchanger 14B and the back plate 32, and an air suction port 34 is provided in the first space S1. It is directly open. Further, a second space S2 that functions as a ventilation path is also formed between the first heat exchanger 14A and the front plate 31, and further functions as a ventilation path between the drain pan 40 and the bottom plate 36. A third space S3 connected to the first space S1 and the second space S2 is formed.

The air suction port 34 is arranged on the side of the back plate 32 of the bottom plate 36, and the air outlet 35 is arranged on the side of the front plate 31 with respect to the air suction port 34 of the bottom plate 36. Therefore, the distance of the ventilation path from the air suction port 34 to the first heat exchanger 14A via the third space S3 and the second space S2 is from the air suction port 34 via the first space S1. It is longer than the distance of the ventilation path to the second heat exchanger 14B by the amount of the third space S3.
The distance of the ventilation path from the air suction port 34 where the first heat exchanger 14A is arranged to the air outlet 35 is from the air suction port 34 where the second heat exchanger 14B is arranged to the air outlet 35. Since it is longer than the distance of the ventilation passage, the ventilation resistance of the ventilation passage in which the first heat exchanger 14A is arranged is larger than the ventilation resistance of the ventilation passage in which the second heat exchanger 14B is arranged. It has become.

The blowout air passage 45 of the sirocco fan 24 is connected to the upper end opening 51 of the blowout guide 50 inserted into the air outlet 35 of the bottom plate 36. The blowout guide 50 is formed in a shape in which the air passage S4 between the upper end opening 51 and the lower end opening 52 is curved toward the front in the downward direction, and the opening surface 52a of the lower end opening 52 faces the front of the lower surface of the front plate 11. It is arranged like this. Further, the outlet guide 50 penetrates the outlet 53 of the drain pan 40 and the air outlet 35 of the bottom plate 36, and the lower end opening 52 of the outlet guide 50 becomes a substantial air outlet. The air suction port 34 of the bottom plate 36 is provided between the air outlet opening 35 and the back plate 12.

When the fan motor 41 of the sirocco fan 24 rotates, the indoor unit 12 enters the second heat exchanger 14B from the air suction port 34 via the first space S1 between the second heat exchanger 14B and the back plate 12. In addition to sucking air, air is sent to the first heat exchanger 14A via the third space S3 between the bottom plate 36 and the drain pan 40 and the second space S2 between the front plate 31 and the first heat exchanger 14A. Inhale. Then, the air sucked into the sirocco fan 24 after being heat-exchanged with the refrigerant in the first heat exchanger 14A and the second heat exchanger 14B passes through the outlet passage S4 of the outlet guide 50 from the outlet ventilation passage 45 of the fan casing 43. It is blown out downward and forward of the front plate 31 via.

The air sucked into the housing 30 from the air suction port 34 by the operation of the sirocco fan 24 flows separately to the first heat exchanger 14A side and the second heat exchanger 14B side. Since the distance of the ventilation path to the 1 heat exchanger 14A is longer than the distance of the ventilation path from the air suction port 34 to the 2nd heat exchanger 14B, the first heat exchanger is affected by the influence of the ventilation resistance. The amount of air sucked into the 14A is less than the amount of air sucked into the second heat exchanger 14B.

Next, with reference to FIG. 2, the structure of the indoor heat exchanger 14 of the present embodiment is schematically shown.
In the refrigeration circuit 19, the indoor heat exchanger 14 is connected between the four-way valve 18 and the expansion valve 17 so that the first heat exchanger 14A and the second heat exchanger 14B are connected in parallel, and expands. The refrigerant pipe from the valve 17 is connected via the distributor 60, and the refrigerant pipe from the four-way valve 18 is connected via the header 61. The distributor 60 has a function of dividing the refrigerant flowing from the expansion valve 17 into the first heat exchanger 14A and the second heat exchanger 14B, or flows from the first heat exchanger 14A and the second heat exchanger 14B. It has a function of merging the incoming refrigerant and flowing it to the expansion valve 17. The header 61 has a function of merging the refrigerants flowing from the first heat exchanger 14A and the second heat exchanger 14B and flowing them to the four-way valve 18, or the first heat exchanger using the refrigerant flowing from the four-way valve 18. It has a function of dividing the flow into 14A and the second heat exchanger 14B.

Each of the first heat exchanger 14A and the second heat exchanger 14B has paths as pipes through which a plurality of refrigerants flow, and in the present embodiment, the first heat exchanger 14A has three paths 14A1. The second heat exchanger 14B has five paths 14B1.
Therefore, the amount of the refrigerant flowing through the first heat exchanger 14A and the amount of the refrigerant flowing through the second heat exchanger 14B are different, and the amount of the refrigerant flowing through the second heat exchanger 14B is larger than the amount of the refrigerant flowing through the first heat exchanger 14A. There will be more.

The number of paths 14A1 possessed by the first heat exchanger 14A and the number of paths 14B1 possessed by the second heat exchanger 14B are the amount of air sucked into the first heat exchanger 14A by the sirocco fan 24 and the second heat exchange. It is determined according to the difference in the amount of air sucked into the container 14B, and in the present embodiment, the amount of air sucked into the first heat exchanger 14A is smaller than the amount of air sucked into the second heat exchanger 14B. Therefore, the number of paths 14A1 of the first heat exchanger 14A is smaller than the number of paths 14B1 of the second heat exchanger 14B.

Therefore, in order to increase the heat exchange capacity, the amount of air flowing through the first heat exchanger 14A and the amount of air flowing through the second heat exchanger 14B are different from each other with two indoor heat exchangers 14 as in the present embodiment. Even in this case, the first heat is determined by determining the number of paths 14A1 constituting the first heat exchanger 14A and the number of paths 14B1 constituting the second heat exchanger 14B according to the difference in the amount of flowing air. It is possible to improve the imbalance between the temperature of the refrigerant flowing through the exchanger 14A and the temperature of the refrigerant flowing through the second heat exchanger 14B.
Thereby, when the heat exchangers 14A and 14B are sterilized by heating, the temperature of each of the heat exchangers 14A and 14B can be set to a predetermined temperature (for example, 55 ° C.).

In this embodiment, the distance of the ventilation path from the air suction port 34 to the first heat exchanger 14A is longer than the distance of the ventilation path from the air suction port 34 to the second heat exchanger 14B. , The ventilation resistance of the ventilation path from the air suction port 34 to the first heat exchanger 14A is larger than the ventilation resistance of the ventilation path of the ventilation path from the air suction port 34 to the second heat exchanger 14B, but the ventilation resistance. Is affected not only by the length of the ventilation passage, but also by the cross-sectional area of the ventilation passage, the shape of the inside of the ventilation passage, the friction coefficient of the inner surface of the ventilation passage, and the like.

Therefore, for example, even if the distance of the ventilation path from the air suction port 34 to the first heat exchanger 14A and the distance of the ventilation path from the air suction port 34 to the second heat exchanger 14B are the same, air suction is performed. If the cross-sectional area of the ventilation path from the port 34 to the first heat exchanger 14A is smaller than the cross-sectional area of the ventilation path from the suction port 34 to the second heat exchanger 14B, the first heat exchange from the air suction port 34 Since the ventilation resistance of the ventilation passage to the vessel 14A is larger than the ventilation resistance of the ventilation passage of the ventilation passage from the air suction port 34 to the second heat exchanger 14B, the number of paths 14A1 of the first heat exchanger 14A Is less than the number of paths 14B1 of the second heat exchanger 14B, so that the temperature of the refrigerant flowing through the first heat exchanger 14A and the temperature of the refrigerant flowing through the second heat exchanger 14B can be imbalanced. ..

That is, the first heat exchanger corresponds to the ventilation resistance of the ventilation path from the air suction port 34 to the first heat exchanger 14A and the ventilation resistance of the ventilation path from the air suction port 34 to the second heat exchanger 14B. The number of paths 14A1 constituting 14A and the number of paths 14B1 constituting the second heat exchanger 14B may be determined.
When determining the number of paths 14A1 constituting the first heat exchanger 14A and the number of paths 14B1 constituting the second heat exchanger 14B, ventilation from each of the indoor heat exchangers 14A and 14B to the air outlet 35 is determined. Since the ventilation resistance of the passage also affects the amount of air sucked into each of the indoor heat exchangers 14A and 14B, the air suction port including the ventilation passage from each of the indoor heat exchangers 14A and 14B to the air outlet 35. It is necessary to consider the ventilation resistance of the ventilation path from 34 to the air outlet 35.

The indoor heat exchanger 14 is composed of two units, a first heat exchanger 14A and a second heat exchanger 14B, and the temperature sensor 26a for measuring the temperature of the indoor heat exchanger 14 and the indoor heat exchanger 14 The humidity sensor 26b for measuring humidity does not need to be attached to each of the first heat exchanger 14A and the second heat exchanger 14B, but is attached to either the first heat exchanger 14A or the second heat exchanger 14B. It suffices if it is done. In the present embodiment, the distance of the ventilation path from the air suction port 34 to the first heat exchanger 14A and the distance of the ventilation path from the air suction port 34 to the second heat exchanger 14B are different. Since the number of paths 14A1 constituting the first heat exchanger 14A and the number of paths 14B1 constituting the second heat exchanger 14B are determined, the temperature of the refrigerant flowing through the first heat exchanger 14A and the second heat exchanger 14B are determined. This is because it is not necessary to attach the temperature sensor 26a to each of the first heat exchanger 14A and the second heat exchanger 14B because imbalance with the temperature of the refrigerant flowing through the heat exchanger is unlikely to occur.

In the present embodiment, as shown in FIG. 3, the temperature sensor 26a and the humidity sensor 26b are the surfaces of the second heat exchanger 14B on the first space S1 side and are arranged on the lower side. Since the first space S1 opens directly to the air suction port 34, if the temperature sensor 26a is arranged on the lower side of the surface of the second heat exchanger 14B on the first space S1 side, the temperature sensor 26a This is because when the humidity sensor 26b is maintained and inspected, it can be easily inspected from the air suction port 34.

The air conditioner 11 of the present embodiment has the first heat exchanger 14A and the second heat exchanger 14B by making the first heat exchanger 14A and the second heat exchanger 14B function as evaporators by the cooling operation. The first heat exchanger 14A and the second heat exchanger 14A and the second heat are heated by controlling the rotation speed of the sirocco fan 24 while making the first heat exchanger 14A and the second heat exchanger 14B function as condensers. A heat sterilization operation is performed in which the temperature of the exchanger 14B is heated in a temperature range different from that of the heating operation.

In the heating sterilization operation, the first heat exchanger 14A and the second heat are driven by driving the rotation speed of the sirocco fan 24 at a rotation speed lower than the rotation speed in the case of the heating operation without aiming at the temperature control in the room. Dew condensation formed on the surfaces of the first heat exchanger 14A and the second heat exchanger 14B by heating the temperature of the refrigerant flowing through the exchanger 14B in a temperature range different from that of the heating operation, for example, 55 to 59 ° C. It is an operation to heat bacteria and mold in the dew condensation water by heating without evaporating the water.
In the case of the heating operation, the rotation speed of the sirocco fan 24 is about 500 rpm to 1000 rpm, but in the case of the heat sterilization operation, the rotation speed of the sirocco fan 24 is, for example, about 200 rpm. By lowering the rotation speed of the sirocco fan 24 compared to the case of heating operation, the pressure of the high-pressure side refrigerant can be increased to maintain the temperatures of the first heat exchanger 14A and the second heat exchanger 14B at 55 ° C to 59 ° C. can.

In the air conditioner 11 of the present embodiment, when the first heat exchanger 14A and the second heat exchanger 14B function as evaporators, dew condensation adheres to the first heat exchanger 14A and the second heat exchanger 14B. By making the first heat exchanger 14A and the second heat exchanger 14B function as condensers and heating the water at 55 to 59 ° C., which is a temperature range different from the heating operation, the water is heated with the first heat exchanger 14A. Since the second heat exchanger 14B is heat-sterilized, the sterilization can be carried out at low cost without providing a dedicated device, and the sterilization can be performed even when the inside of the indoor unit 12 is in a high humidity state.

Further, even if the distance of the ventilation path from the air suction port 34 to the first heat exchanger 14A and the distance of the ventilation path from the air suction port 34 to the second heat exchanger 14B are different, it corresponds to the case. Since the number of paths 14A1 constituting the first heat exchanger 14A and the number of paths 14B1 constituting the second heat exchanger 14B are determined, the first heat exchanger 14A flows even in the state of heat sterilization operation. Since the imbalance between the temperature of the refrigerant and the temperature of the refrigerant flowing through the second heat exchanger 14B can be suppressed, the imbalance of sterilization of the first heat exchanger 14A and the second heat exchanger 14B can be suppressed. Can be done.
Although the above description has been made with reference to a limited number of embodiments, the scope of rights is not limited thereto, and modifications of the embodiments based on the above disclosure are obvious to those skilled in the art.

11 ... Air conditioner, 13 ... Outdoor unit, 12 ... Indoor unit, 14 ... Indoor heat exchanger, 14A ... 1st heat exchanger, 14B ... 2nd heat exchanger, 14A1, 14B1 ... Pass, 24 ... Sirocco fan, 26a ... temperature sensor, 33 ... housing, 34 ... air inlet, 35 ... air outlet, 40 ... drain pan, S1 ... first space, S2 ... second space, S3 ... third space, S4 ... air guide, 45 ... Blowout ventilation path

Claims (6)

A compressor, a four-way valve, multiple indoor heat exchangers, a refrigeration circuit to which an expansion valve is connected and a refrigerant circulates,
The compressor, the outdoor unit equipped with the four-way valve, and
An indoor unit including a plurality of the indoor heat exchangers and an indoor unit fan and connected to the outdoor unit is provided.
At least the compressor, the indoor unit fan, and the four-way valve are controlled so that the plurality of indoor heat exchangers function as evaporators in the case of cooling and as condensers in the case of heating. In the air conditioner that controls the temperature in the installed room
The indoor unit has a housing having an air suction port and an air outlet, and having a plurality of ventilation passages between the air suction port and the air outlet and branching from the air suction port , and a plurality of the above. At least one indoor heat exchanger arranged in each of the ventilation passages, and the indoor unit fan that guides the air sucked from the air suction port to the air outlet via each of the plurality of ventilation passages. In preparation for
The ventilation resistance of one of the ventilation passages is larger than the ventilation resistance of the other ventilation passages, and the amount of refrigerant flowing through the indoor heat exchanger arranged in the one ventilation passage according to the magnitude of the ventilation resistance. Is set to be less than the amount of refrigerant flowing through the other indoor heat exchangers located in the other ventilation passages.
When the plurality of indoor heat exchangers function as evaporators, the dew condensation water adhering to the indoor heat exchangers is heated to a predetermined temperature by making the plurality of indoor heat exchangers function as condensers, and the plurality of said indoor heat exchangers. An air conditioner characterized by heating and disinfecting an indoor heat exchanger. Each of the plurality of indoor heat exchangers has a plurality of paths through which the refrigerant flows, and the number of passes of the one indoor heat exchanger is set to be smaller than the number of passes of the other indoor heat exchangers. The air conditioner according to claim 1, wherein the air conditioner is characterized by. The housing is a box type having a front plate, a back plate, a top plate, a bottom plate, a left side plate, and a right side plate.
The bottom plate has the air outlet arranged on the front plate side and the air suction port arranged on the back plate side.
The plurality of indoor heat exchangers include a first heat exchanger as the one indoor heat exchanger attached near the front plate in the housing, and the other indoor heat exchanger attached near the back plate. Including the second heat exchanger as
The indoor unit fan has an outlet ventilation passage and is arranged at a position between the first heat exchanger and the second heat exchanger.
A drain pan arranged under the first heat exchanger and the second heat exchanger to collect the dew condensation water adhering to the first heat exchanger and the second heat exchanger.
A blowout guide connecting the blowout air passage and the air outlet so as to guide the air blown from the blowout air passage of the indoor unit fan to the air outlet is provided.
A first space for opening the air suction port is formed between the second heat exchanger and the back plate, and a second space is formed between the first heat exchanger and the front plate. A third space for connecting the first space and the second space is formed between the drain pan and the bottom plate.
The plurality of ventilation passages are a ventilation passage from the air suction port to the first heat exchanger via the third space and the second space, and from the air suction port via the first space. The air conditioner according to claim 1 or 2, wherein the air conditioner has a ventilation path to the second heat exchanger. The ventilation resistance of the ventilation path from the air suction port to the first heat exchanger via the third space and the second space is the second heat from the air suction port via the first space. The air conditioner according to claim 3 , wherein the first heat exchanger and the second heat exchanger are arranged so as to be larger than the ventilation resistance of the ventilation path to the exchanger. The air conditioner according to any one of claims 1 to 4 , wherein the plurality of indoor heat exchangers are connected in parallel in the refrigeration circuit. Claims 1 to 5 characterized in that the heating sterilization of the plurality of indoor heat exchangers drives the indoor unit fan at a rotation speed lower than the minimum rotation speed of the indoor unit fan in the case of heating. The air conditioner according to any one of the above items.

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