JP2011012844A - Refrigerating cycle device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a refrigerating cycle device free from radiation of heat in an internal heat exchanger during a defrosting operation without increasing manufacturing cost.SOLUTION: This refrigerating cycle device has a refrigerant circuit formed by successively connecting a compressor 21, a radiator 22, a pressure reducing means 23 and an evaporator 24, an air distributing means 27 for distributing the air to the evaporator 24, and an auxiliary heat exchanger 31 for heating at least a part of the air distributed by the air distributing means 27 by a refrigerant flowing out of the radiator 22. The refrigerant is successively circulated in the compressor 21, the radiator 22, the pressure reducing means 23 and the evaporator 24, the motion of the defrosting operation reduced in rotational frequency of the air distributing means 27, is performed, and the refrigerant at an outlet section of the evaporator 24 is heated by the air heated by the auxiliary heat exchanger 31.

Description

  The present invention relates to a refrigeration cycle apparatus used in a heat pump type hot water heater, a heat pump type hot water heater, and the like that generates a high temperature fluid by heating a low temperature fluid, and in particular, a refrigeration cycle that can efficiently perform defrosting of an evaporator. Relates to the device.

  An internal heat exchanger is provided in a refrigeration cycle apparatus used for a heat pump type hot water heater, a heat pump type hot water heater, and the like. By this internal heat exchanger, a refrigerant supplied from a radiator to an expansion valve and an evaporator to a compressor Heat exchange with the refrigerant supplied to the compressor, and the refrigerant temperature sucked into the compressor is increased to increase the discharge temperature of the compressor. As a result, the fluid to be heated (for example, hot water or The thing which raises the temperature of an antifreeze liquid is proposed (for example, refer patent document 1).

  FIG. 5 shows a schematic diagram of a refrigeration cycle apparatus using an internal heat exchanger. In FIG. 5, the refrigeration cycle apparatus 10 has a refrigeration cycle in which a compressor 11, a radiator 12, an expansion valve 13, and an evaporator 14 are connected by piping. The internal heat exchanger 15 is between the low-pressure side refrigerant flowing through the low-pressure side flow path 15A from the evaporator 14 to the compressor 11 and the high-pressure refrigerant flowing through the high-pressure side flow path 15B from the radiator 12 to the expansion valve 13. It is configured to perform heat exchange.

  In such a refrigeration cycle apparatus, if the heating operation for heating the low-temperature fluid to be heated is continued, frosting may occur in the evaporator 14 when the outside air temperature is low, and the heating capacity may be reduced.

  Conventionally, as a method for defrosting the frost on the evaporator 14, a method has been proposed in which the transport pump 18 that transports fluid to the radiator 12 is stopped and the opening of the expansion valve 13 is made larger than that during normal operation ( For example, see Patent Document 2).

  According to this, since the amount of heat energy that the high-temperature refrigerant discharged from the compressor 11 dissipates in the radiator 12 can be reduced and the temperature drop due to the decompression at the expansion valve 13 can be reduced, the refrigerant discharged from the compressor 11 is discharged. It is said that defrosting can be performed by the high-temperature refrigerant that has reached the evaporator 14 without greatly decreasing the temperature.

  As another conventional defrosting method, a bypass circuit is configured so that high-pressure refrigerant flows from the refrigerant outlet of the compressor 11 to the evaporator 14 without passing through the radiator 12, and the flow rate of an electromagnetic valve or the like is further provided in the bypass circuit. There has also been proposed a defrosting method in which a regulating valve is arranged and the flow rate regulating valve is opened during a defrosting operation to introduce a high-temperature refrigerant into the evaporator 14 (see, for example, Patent Document 3).

Japanese Patent Laid-Open No. 11-193958 JP 2001-82802 A JP 2001-108256 A

In recent years, from the viewpoint of energy saving, it has been required to efficiently perform a defrosting operation in a short time. In a refrigeration cycle apparatus having an internal heat exchanger, if the defrosting operation is performed by the technique described in Patent Document 2, the high-temperature refrigerant discharged from the compressor during the defrosting operation is caused to pass through the evaporator in the internal heat exchanger. Since the low-temperature refrigerant that has come out is deprived of heat, there is a problem that the amount of heat given to the evaporator decreases and the defrosting operation time becomes longer.

  On the other hand, according to the technique described in Patent Document 3, the high-temperature refrigerant discharged from the compressor is supplied to the evaporator without passing through the internal heat exchanger, so that heat is taken away in the internal heat exchanger. However, there is a problem that the manufacturing cost increases because it is necessary to install a bypass circuit, a solenoid valve, or the like.

  In view of the above circumstances, an object of the present invention is to provide a refrigeration cycle apparatus that does not dissipate heat in an internal heat exchanger during a defrosting operation without increasing manufacturing costs.

  In order to solve the above problems, a refrigeration cycle apparatus of the present invention includes a refrigerant circuit formed by connecting a compressor, a radiator, a decompression unit, and an evaporator in order, and a blowing unit that blows air to the evaporator, The refrigerant that has flowed out of the radiator includes an auxiliary heat exchanger that heats at least a part of the air blown by the blowing unit, and the refrigerant is circulated in the order of the compressor, the radiator, the pressure reducing unit, and the evaporator. And a defrosting operation operation in which the number of rotations of the blowing unit is reduced, and the air heated by the auxiliary heat exchanger is configured to heat the refrigerant at the outlet portion of the evaporator. It is characterized by being able to obtain the same effect as a conventional internal heat exchanger during heating operation, and is supplied to the auxiliary heat exchanger by reducing the rotation speed of the fan during defrosting operation. Reducing the amount of air Since the amount of heat exchange between the auxiliary heat exchanger and the evaporator outlet can be reduced, unlike the conventional internal heat exchanger, heat is not taken away by the low-temperature refrigerant at the evaporator outlet, and is discharged from the compressor. Since the heat of the refrigerant can be effectively supplied to the evaporator, an efficient defrosting operation can be performed.

  According to the present invention, since an efficient defrosting operation can be performed without increasing the manufacturing cost, a refrigeration cycle apparatus capable of efficiently heating a fluid can be provided.

1 is a schematic configuration diagram of a heat pump water heater in Embodiment 1 of the present invention. Time chart before and after the defrosting operation Schematic front view of the evaporator and auxiliary heat exchanger Schematic side view of the evaporator and auxiliary heat exchanger Schematic configuration diagram of a conventional refrigeration cycle apparatus

  A first aspect of the present invention is a refrigerant circuit formed by connecting a compressor, a radiator, a decompression unit, and an evaporator in order, a blowing unit that blows air to the evaporator, and a refrigerant that flows out of the radiator An auxiliary heat exchanger for heating at least a part of the air blown by the means, circulating the refrigerant in the order of the compressor, the radiator, the pressure reducing means, and the evaporator, and the number of rotations of the blower means In the heating operation, the defrosting operation is performed while the air heated by the auxiliary heat exchanger is configured to heat the refrigerant at the outlet of the evaporator. The same effect as a conventional internal heat exchanger can be obtained, and during the defrosting operation, the amount of air supplied to the auxiliary heat exchanger can be reduced by reducing the number of rotations of the fan, and auxiliary heat exchange The amount of heat exchange between the Because it can be reduced, the heat of the refrigerant discharged from the compressor can be effectively supplied to the evaporator without being deprived of heat by the low-temperature refrigerant at the outlet of the evaporator unlike the conventional internal heat exchanger. In addition, an efficient defrosting operation can be performed.

  The second invention is characterized in that, in the first invention, the auxiliary heat exchanger is formed integrally with the evaporator, and the auxiliary heat exchanger can be constituted by a member similar to the evaporator. Efficient defrosting operation can be performed without increasing the manufacturing cost.

  A third invention is characterized in that, in the first or second invention, the auxiliary heat exchanger is configured such that heat transfer by heat conduction with the evaporator does not occur. Since the heat of the refrigerant discharged from the compressor can be effectively supplied to the evaporator without transferring the heat from the auxiliary heat exchanger to the evaporator by heat conduction, an efficient defrosting operation can be performed.

  A fourth invention is characterized in that, in the first or second invention, the auxiliary heat exchanger is arranged on the upstream side of the air flow path of the evaporator, and the fan is completely operated during the defrosting operation. Even if it is not stopped, the air flowing through the auxiliary heat exchanger is not the air cooled by the evaporator but the outside air, so that the amount of heat taken from the refrigerant in the auxiliary heat exchanger can be reduced. Since the heat of the refrigerant discharged from the compressor can be effectively supplied to the evaporator, an efficient defrosting operation can be performed.

  According to a fifth invention, in the first or second invention, the auxiliary heat exchanger is disposed below the evaporator, and the condensed water of the evaporator is prevented from adhering to the auxiliary heat exchanger. For preventing the heat of the refrigerant in the auxiliary heat exchanger from being taken away by the drain water, and effectively supplying the heat of the refrigerant discharged from the compressor to the evaporator. Therefore, efficient defrosting operation can be performed.

  Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings. Note that the present invention is not limited to the embodiments.

(Embodiment 1)
FIG. 1 is a schematic configuration diagram of a refrigeration cycle apparatus according to the present embodiment. The refrigeration cycle apparatus 20 includes a compressor 21 that compresses a refrigerant to a high temperature and a high pressure, a radiator 22 that heats low-temperature water using the refrigerant compressed by the compressor 21, and a refrigerant that is cooled by the radiator 22 by outside air. Furthermore, an auxiliary heat exchanger 31 for cooling, an expansion valve 23 for reducing the pressure of the refrigerant flowing out of the auxiliary heat exchanger 31, and an evaporator 24 for evaporating the refrigerant reduced by the expansion valve 23 are provided.

  The compressor 21, the radiator 22, the auxiliary heat exchanger 31, the expansion valve 23, and the evaporator 24 are connected to each other by a refrigerant pipe 26 so that the refrigerant circulates in this order to constitute a refrigeration cycle circuit. The refrigeration cycle circuit is filled with carbon dioxide (R744) as a refrigerant. A fan 27 is provided in the vicinity of the evaporator 24. The fan 27 supplies air to be exchanged with the refrigerant in the evaporator 24 to the evaporator 24. Further, the transport pump 28 supplies a heated fluid (for example, water) to be heat-exchanged with the refrigerant by the radiator 22 to the radiator 22 via the heated fluid pipe 29.

  The auxiliary heat exchanger 31 is an air heat exchanger represented by a fin tube type heat exchanger, like the evaporator 24. The auxiliary heat exchanger 31 and the evaporator 24 are installed in a blower circuit 32 that is blown by a fan 27, and air heated when passing through the auxiliary heat exchanger 31 is used as a refrigerant outlet of the evaporator 24. The refrigerant flowing through the portion 24a is heated.

  The compressor 21 may employ a positive displacement fluid mechanism such as a scroll type, a reciprocating type, or a rotary type. A heat exchanger such as a double tube type or a plate type can be adopted as the radiator 22. An electric expansion valve can be adopted as the expansion valve 23.

Next, the operation of the refrigeration cycle apparatus configured as described above will be described. First, a heating operation for heating a low-temperature fluid to be heated to a high temperature, which is an operation state of the normal refrigeration cycle apparatus 20, will be described.

  The refrigerant compressed by the compressor 21 is in a high-temperature and high-pressure state, and when flowing through the refrigerant flow path 22a of the radiator 22, it dissipates heat to the water flowing through the heated fluid flow path 22b of the radiator 22 and is cooled. The refrigerant that has flowed out of the radiator 22 is supplied to the auxiliary heat exchanger 31. In the auxiliary heat exchanger 31, the refrigerant is further cooled by the air sent by the fan 27.

  On the other hand, the air sent by the fan 27 is heated by the refrigerant flowing through the auxiliary heat exchanger 31 and supplied to the evaporator refrigerant outlet 24a. Thereafter, the refrigerant is depressurized by the expansion valve 23 to be in a low-temperature and low-pressure gas-liquid two-phase state and supplied to the evaporator 24. In the evaporator 24, the refrigerant is heated by the air sent by the fan 27, and enters a gas-liquid two-phase or gas state. Further, at the evaporator refrigerant outlet portion 24a, the refrigerant is further heated by the air heated when passing through the auxiliary heat exchanger 31. Thereafter, the refrigerant that has flowed out of the evaporator 24 is again sucked into the compressor 21.

  On the other hand, the water to be heated is sent to the heated fluid flow path 22b of the radiator 22 by the transfer pump 28, and is heated by the refrigerant flowing through the refrigerant flow path 22a of the radiator 22 to become hot hot water. These hot water is supplied to equipment (not shown) and used for hot water supply, heating, and the like.

  Here, the effect of the auxiliary heat exchanger 31 will be described. The auxiliary heat exchanger 31 performs heat exchange between the refrigerant supplied from the radiator 22 to the expansion valve 23 and the refrigerant supplied from the evaporator 24 to the compressor 21 through the supplied air. It has the same effect as a conventional internal heat exchanger.

  That is, by increasing the temperature of the refrigerant sucked into the compressor 21, the discharge temperature of the compressor 21 can be increased, and as a result, the temperature of hot water that is the heated fluid generated by the radiator 22 can be increased. In addition, the refrigeration cycle apparatus can be operated efficiently.

  Next, the defrosting operation will be described. When the refrigeration cycle apparatus 20 continues the heating operation, when the outside air temperature is low, frost forms in the evaporator 24, and the heating capacity may decrease. The defrosting operation is an operation for melting the frost of the evaporator 24 in such a case.

  The electronic control means (not shown) determines that the evaporator 24 needs to be defrosted based on signals from an outside temperature detecting means (not shown) for detecting the outside air temperature and an evaporator temperature detecting means (not shown). In this case, the heating operation is switched to the defrosting operation, and a control signal is sent to the fan 27, the transfer pump 28, the expansion valve 23, and the like.

  Operations of the fan 27, the transport pump 28, and the expansion valve 23 will be described with reference to FIG. When switching to the defrosting operation, the rotation speed (Frpm2) of the fan 27 is made smaller than the average rotation speed (Frpm1) during the heating operation, and the rotation speed (Prpm2) of the transport pump 28 is changed during the heating operation. It is made smaller than the average rotation speed (Prpm1). Moreover, the opening degree of the expansion valve 23 is changed to a predetermined opening degree (pls2) larger than the average opening degree (pls1) during the heating operation.

  As a result, during the defrosting operation, the high-temperature refrigerant that has exited the compressor 21 flows through the radiator 22, the auxiliary heat exchanger 31, and the expansion valve 23 and is supplied to the evaporator 24. In the evaporator 24, frost is melted by the heat of the high-temperature refrigerant. Then, the refrigerant that has flowed out of the evaporator 24 is again sucked into the compressor 21.

In the present embodiment, the amount of air supplied to the auxiliary heat exchanger 31 is reduced by reducing the rotational speed of the fan 27. For this reason, the high-temperature refrigerant discharged from the compressor 21 is supplied to the evaporator 24 without the heat being taken away by the auxiliary heat exchanger 31. Therefore, a high-temperature refrigerant can be supplied to the evaporator 24, and the defrosting operation can be performed in a short time.

  In addition, by reducing the rotation speed of the conveyance pump 28 during the defrosting operation, the amount of water supplied to the heated fluid flow path 22b is reduced, and the high-temperature refrigerant discharged from the compressor 21 becomes a radiator. 22 is not deprived of heat, and the opening degree of the expansion valve 23 is increased, so that the high-temperature refrigerant discharged from the compressor 21 is prevented from lowering the temperature due to the decompression of the expansion valve 23. Further, it is possible to reduce heat exchange between the refrigerant and the air in the evaporator 24 by reducing the number of rotations of the fan 27, and to efficiently transfer the heat of the refrigerant to the frost attached to the evaporator 24. Is the same as the conventional technique.

  As described above, in this embodiment, the internal heat exchanger that performs heat exchange between the refrigerant supplied from the radiator 22 to the expansion valve 23 and the refrigerant supplied from the evaporator 24 to the compressor 21 is eliminated. Since the air heated by the auxiliary heat exchanger 31 is configured to heat the refrigerant at the evaporator outlet portion 24a, an effect equivalent to that of the conventional internal heat exchanger can be obtained during the heating operation. At the time of the defrosting operation, the number of heat exchange between the auxiliary heat exchanger 31 and the evaporator outlet portion 24a is reduced by reducing the rotation speed of the fan 27 and reducing the amount of air supplied to the auxiliary heat exchanger 31. Therefore, the problem that the defrosting operation takes a long time due to heat being taken away by the low-temperature refrigerant at the outlet of the evaporator 24 as in the conventional internal heat exchanger can be solved. Furthermore, since it is not necessary to install a bypass circuit or a solenoid valve, the manufacturing cost can be reduced.

  Next, the auxiliary heat exchanger 31 that is a feature of the present embodiment will be described in more detail. FIG. 3 is a schematic front view of the auxiliary heat exchanger 31 formed integrally with the evaporator 24, and FIG. 4 is a schematic side view thereof. 3 and 4, the white arrow indicates the air flow direction in the evaporator 24 and the auxiliary heat exchanger 31, the solid line arrow indicates the refrigerant flow direction in the evaporator 24, and the broken arrow indicates the auxiliary heat exchanger. The flow direction of the refrigerant | coolant in 31 is each shown.

  The evaporator 24 is a fin tube type heat exchanger composed of a heat transfer tube 41 and a plurality of fins 42 (some fins are not shown in the figure). This is a two-row air heat exchanger composed of a certain first row 241 and a second row 242 which is a leeward row.

  As with the evaporator 24, the auxiliary heat exchanger 31 is an air heat exchange of a finned tube heat exchanger composed of a heat transfer tube 51 and a plurality of fins 52 (some fins are not shown). It is a vessel. The auxiliary heat exchanger 31 is substantially in parallel with the first row 241 of the evaporator 24 and is below the first row 241 and in the vicinity of the refrigerant outlet pipe 51b provided in the second row 242 of the evaporator 24, that is, The evaporator refrigerant outlet 24a is installed at a position where the air flowing out from the auxiliary heat exchanger 31 can be heated.

Furthermore, a slit 60 is provided between the plurality of fins 52 of the auxiliary heat exchanger 31 and the plurality of fins 42 of the evaporator 24, and the auxiliary heat exchanger 31 and the evaporator 24 are It is configured so that heat transfer due to heat conduction does not occur. In addition, a drain water guide plate 61 is provided above the plurality of fins 52 of the auxiliary heat exchanger 31. The drain water guide plate 61 has a slope that decreases toward the second row 242 side of the evaporator 24, and prevents the drain water of the evaporator 24 from reaching the auxiliary heat exchanger 31. Operations of the evaporator 24 and the auxiliary heat exchanger 31 will be described. First, the case of heating operation will be described.

The refrigerant compressed by the compressor 21 is in a high-temperature and high-pressure state, and when flowing through the refrigerant flow path 22a of the radiator 22, it dissipates heat to the water flowing through the heated fluid flow path 22b of the radiator 22 and is cooled. The refrigerant that has flowed out of the radiator 22 is supplied to the auxiliary heat exchanger 31. In the auxiliary heat exchanger 31,
The refrigerant flows in from the refrigerant inlet pipe 51a, and when flowing through the heat transfer pipe 51, the refrigerant is cooled by the air flowing between the plurality of fins 52 and then flows out from the refrigerant outlet pipe 51b. On the other hand, the air flowing between the plurality of fins 52 is heated by the refrigerant flowing through the heat transfer tubes 51.

  Thereafter, the refrigerant is depressurized by the expansion valve 23 to be in a low-temperature and low-pressure gas-liquid two-phase state and supplied to the evaporator 24. In the evaporator 24, the refrigerant flows in from the refrigerant inlet pipe 41 a provided in the first row 241 and is heated by the air flowing between the plurality of fins 42 when flowing through the heat transfer pipe 41. In addition, at the evaporator refrigerant outlet 24a, the refrigerant is further heated by the air heated between the plurality of fins 52 and heated. Thereafter, the refrigerant that has flowed out of the evaporator 24 is again sucked into the compressor 21.

  That is, the auxiliary heat exchanger 31 exchanges heat between the refrigerant supplied from the radiator 22 to the expansion valve 23 and the refrigerant supplied from the evaporator 24 to the compressor 21 via the supplied air. Yes, it has the same effect as a conventional internal heat exchanger. That is, by increasing the temperature of the refrigerant sucked into the compressor 21, the discharge temperature of the compressor 21 can be increased, and as a result, the temperature of hot water that is the heated fluid generated by the radiator 22 can be increased. In addition, the refrigeration cycle apparatus can be operated efficiently.

  Next, the case of defrosting operation will be described. The electronic control means (not shown) determines that the evaporator 24 needs to be defrosted based on signals from an outside temperature detecting means (not shown) for detecting the outside air temperature and an evaporator temperature detecting means (not shown). In this case, the heating operation is switched to the defrosting operation, and a control signal is sent to the fan 27, the transfer pump 28, the expansion valve 23, and the like. When switching to the defrosting operation, the rotational speed of the fan 27 is made smaller than the average rotational speed during the heating operation, and the rotational speed of the transport pump 28 is made smaller than the average rotational speed during the heating operation.

  Moreover, the opening degree of the expansion valve 23 is changed to a predetermined opening degree that is larger than the average opening degree during the heating operation. As a result, during the defrosting operation, the high-temperature refrigerant that has exited the compressor 21 flows through the radiator 22, the auxiliary heat exchanger 31, and the expansion valve 23 and is supplied to the evaporator 24. In the evaporator 24, frost is melted by the heat of the high-temperature refrigerant. Then, the refrigerant that has flowed out of the evaporator 24 is again sucked into the compressor 21.

  On the other hand, in the evaporator 24, drain water, which is water formed by melting frost, drops between the fins 42, is collected on the drain water guide plate 61, and the evaporator has a gradient provided in the drain water guide 61. 24 is discharged to the second row 242 side.

  In the present embodiment, the amount of air flowing between the plurality of fins 52 of the auxiliary heat exchanger 31 is reduced by reducing the rotational speed of the fan 27. For this reason, the high-temperature refrigerant discharged from the compressor 21 is supplied to the evaporator 14 without the heat being taken away by the auxiliary heat exchanger 31. Therefore, a high-temperature refrigerant can be supplied to the evaporator 24, and the defrosting operation can be performed in a short time.

That is, the internal heat exchanger that performs heat exchange between the refrigerant supplied from the radiator 22 to the expansion valve 23 and the refrigerant supplied from the evaporator 24 to the compressor 21 is abolished, and is heated by the auxiliary heat exchanger 31. The air is configured to heat the refrigerant at the evaporator outlet 24 a, and the slit 60 is provided between the auxiliary heat exchanger 31 and the evaporator 24. By providing the drain water guide 61 that is provided on the upper side and prevents the drain water of the evaporator 24 from reaching the auxiliary heat exchanger 31, an effect equivalent to that of the conventional internal heat exchanger is obtained during the heating operation. In addition, during the defrosting operation, the heat of the auxiliary heat exchanger 31 does not move to the evaporator 24 due to heat conduction, and even if the fan 27 is not completely stopped, auxiliary heat exchange is possible. The air flowing through the vessel 31 is steamed Rather than cooled air in vessel 24, to be the outside air,
The amount of heat deprived of the refrigerant in the auxiliary heat exchanger 31 is reduced, and the heat of the refrigerant in the auxiliary heat exchanger 31 is effectively taken away by the drain water, and the heat of the refrigerant discharged from the compressor 21 is effectively reduced. It can be supplied to the generator 24.

  Furthermore, since it is not necessary to install a bypass circuit, a solenoid valve, or the like, and it can be formed integrally with the evaporator 24 by a member similar to the evaporator 24, the manufacturing cost can be reduced. For this reason, the subject that the defrosting operation takes a long time can be solved without significantly increasing the manufacturing cost.

  The refrigeration cycle apparatus of the present invention can be applied to a wide range of uses, such as heat pump hot water heaters and heat pump hot water heaters that heat a low-temperature fluid to generate a high-temperature fluid, regardless of whether it is for home use or business use.

21 Compressor 22 Radiator 23 Pressure reducing means (expansion valve)
24 Evaporator 27 Blower (fan)
31 Auxiliary heat exchanger

Claims (5)

A refrigerant circuit formed by sequentially connecting a compressor, a radiator, a decompression unit, and an evaporator, a blowing unit that blows air to the evaporator, and an air that is blown by the blowing unit after the refrigerant has flowed out of the radiator And an auxiliary heat exchanger that heats at least a part of the refrigerant, the refrigerant is circulated in the order of the compressor, the heat radiator, the pressure reducing means, and the evaporator, and the number of revolutions of the air blowing means is reduced. A refrigeration cycle apparatus configured to perform an operation and to be configured such that air heated by the auxiliary heat exchanger heats a refrigerant at an outlet of the evaporator. The refrigeration cycle apparatus according to claim 1, wherein the auxiliary heat exchanger is formed integrally with the evaporator. The refrigeration cycle apparatus according to claim 1 or 2, wherein the auxiliary heat exchanger is configured not to generate heat transfer by heat conduction with the evaporator. The refrigeration cycle apparatus according to claim 1 or 2, wherein the auxiliary heat exchanger is disposed on the upstream side of the air flow path of the evaporator. The auxiliary heat exchanger is disposed below the evaporator, and a prevention member for preventing the condensed water of the evaporator from adhering to the auxiliary heat exchanger is provided. Or the refrigeration cycle apparatus of 2.