JP5191817B2 - Heat exchanger unit and air conditioner equipped with the same - Google Patents

Description

  The present invention relates to a heat exchanger unit used in an air conditioner or the like.

There are various types of heat exchangers used in air conditioners, such as fin and tube type, parallel flow type, and serpentine type. The fin-and-tube type has a shape in which one or a plurality of tubes meander through a large number of parallel fins while meandering, and is commonly used. In the parallel flow type, a plurality of flat tubes are arranged between two header pipes so that a refrigerant passage inside the flat tubes communicates with the inside of the header pipe, and fins such as corrugated fins are arranged between the flat tubes. It is. The serpentine type is the same as the parallel flow type until the flat tube is placed between the two header pipes. However, the number of flat tubes is one, and this single flat tube meanders, meandering. Fins such as corrugated fins are arranged between the flat tubes. An example of the fin and tube type can be found in Patent Document 1, and an example of a parallel flow type and a serpentine type can be found in Patent Document 2.

In the heat exchanger unit, in order to increase the amount of heat exchange, a plurality of heat exchangers are often arranged back and forth in the ventilation path. Patent Document 1 describes a configuration in which a plurality of rows of fin-and-tube heat exchangers are arranged before and after. Patent Document 2 describes a configuration in which two or more parallel flow type or serpentine type heat exchangers are arranged in parallel.
JP-A-7-198166 JP 2005-55108 A

  The heat exchanger described above can be used both as a condenser and as an evaporator. In the heat pump type air conditioner, the heat exchanger of the outdoor unit is used as a condenser during cooling, and is used as an evaporator during heating. When the heat exchanger is used as an evaporator and the outside air temperature is low, a refrigerant having a temperature lower than the outside air flows in the tube, and the surface temperature of the tube and the fin is lowered to 0 ° C. or less. Thereby, the phenomenon (frosting phenomenon) that the water | moisture content in air adheres as a frost on the surface of a tube or a fin occurs. When frost formation occurs, the transfer of cold heat from the tubes and fins to the air deteriorates, and the gap between the fins is narrowed due to clogging due to frost formation, making it difficult for the air to flow, so the heat exchange efficiency decreases. For this reason, the defrost operation which reverses the role of an evaporator and a condenser is performed from time to time, and frost is melted.

  If the water in which the frost is melted, that is, the defrosted water remains attached to the tubes and the fins, it freezes when returning from the defrosting operation to the normal operation, thereby reducing the heat exchange efficiency. Therefore, it is necessary to drain defrost water promptly.

  Further, in an indoor unit of an air conditioner, condensation occurs in the heat exchanger due to heat exchange with room air during cooling operation. In an outdoor unit of an air conditioner, condensation occurs in the heat exchanger due to heat exchange with outdoor air during heating operation. Condensed water also reduces the heat exchange performance by narrowing the cross-sectional area of the air flow passage, so it must be drained quickly.

  Parallel flow type and serpentine type heat exchangers have high heat exchange efficiency, but have problems in terms of drainage of defrost water and condensed water. That is, in these heat exchangers, a so-called bridge phenomenon in which a water film is stretched between corrugated fins by the surface tension of water is likely to occur. That is, even if water hangs down to the end of the corrugated fin, only a film is stretched on the corrugated fin, and dripping does not occur. If the peak-to-valley pitch of the corrugated fins is increased so that the bridging phenomenon does not occur, the heat dissipation area of the corrugated fins is reduced and the heat exchange performance is lowered.

  The present invention has been made in view of the above points, and prevents the heat exchange performance of parallel flow type or serpentine type heat exchangers from being deteriorated due to condensation, frost formation, or defrosting action. It aims at making high heat exchange efficiency which is the feature of an exchanger fully exhibited.

  In order to achieve the above object, the present invention includes a fin-and-tube type first heat exchanger and a parallel flow type or serpentine type second heat exchanger, and the air flow generated by a blower includes the first heat exchanger. The heat exchanger unit is arranged such that one heat exchanger is on the leeward side and the second heat exchanger is on the leeward side.

  Condensation or frosting due to moisture in the air occurs more frequently in the first heat exchanger on the windward side than on the second heat exchanger on the leeward side. That is, the first heat exchanger accepts most of condensation and frost formation, and the condensation and frost formation of the second heat exchanger are reduced accordingly. For this reason, the second heat exchanger of the parallel flow type or the serpentine type does not need to significantly reduce the high heat exchange efficiency that characterizes the second heat exchanger. In addition, since the amount of water remaining in the second heat exchanger is small, the bridge phenomenon is not a big problem.

  On the other hand, since the 1st heat exchanger is a fin and tube type, time until frost begins to exert a bad influence is long compared with a parallel flow type and a serpentine type. In addition, since it has better drainage than the parallel flow type or serpentine type, it is difficult for condensed water to accumulate, and even if it forms frost, it can be easily washed away as defrosted water by defrosting operation. That is, even if dew condensation or frost formation occurs, even if the amount is large, adverse effects can be minimized.

  Also, when using the heat exchanger unit as a condenser, if the refrigerant is brought into a supercooled state below the saturation temperature, the enthalpy difference will be taken and the capacity will be improved. Compared to The fin-and-tube type has a lower temperature efficiency than the parallel flow type, and can be efficiently supercooled. That is, the condensation performance can be extracted.

  In this way, fin-and-tube type heat exchangers and parallel flow type or serpentine type heat exchangers have different characteristics, and these characteristics complement each other, so they are resistant to condensation and frost formation, and heat exchange efficiency Can also be a high heat exchanger unit.

  In the heat exchanger unit configured as described above, it is preferable that the fin material metal of the first heat exchanger and the material metal of the second heat exchanger are the same type.

  When the heat exchanger unit is configured in such a manner that the fin and tube type first heat exchanger is arranged on the leeward side and the parallel flow type or serpentine type second heat exchanger is arranged on the leeward side, Contact is likely to occur between the fins of the heat exchanger and the second heat exchanger. If materials that may cause contact are formed of the same type of metal, even if contact occurs, there will be no problem of corrosion due to contact of different metals. That is, since the first heat exchanger and the second heat exchanger can be disposed close to each other without worrying about contact, the heat exchanger unit can be easily designed to be compact.

  In the heat exchanger unit configured as described above, it is preferable that the first heat exchanger and the second heat exchanger have the same material.

  With such a configuration, no matter which part of the first heat exchanger comes into contact with the second heat exchanger, the problem of corrosion due to the contact of different metals does not occur. That is, since the first heat exchanger and the second heat exchanger can be disposed close to each other without worrying about contact, the heat exchanger unit can be easily designed to be compact.

  In the heat exchanger unit having the above configuration, when used as an evaporator, it is preferable that the refrigerant first flows into the first heat exchanger.

  With such a configuration, the amount of heat exchange by the first heat exchanger increases, so that more frost can be formed in the first heat exchanger, and frost formation in the second heat exchanger is reduced. be able to.

  Further, the present invention is characterized in that the heat exchanger unit having the above configuration is used as a heat exchanger unit of an outdoor unit of an air conditioner.

  According to this configuration, an air conditioner that is resistant to condensation and frost formation and has high heat exchange efficiency can be obtained.

  According to the present invention, heat exchange with high heat exchange efficiency is achieved, with the characteristics of fin-and-tube heat exchangers complementing the characteristics of parallel flow type or serpentine type heat exchangers, which is resistant to condensation and frost formation. Unit can be obtained. In addition, an air conditioner that is resistant to condensation and frost formation and has high heat exchange efficiency can be obtained.

  A first embodiment of the present invention will be described below with reference to FIGS. FIG. 1 is a side view of the heat exchanger unit, in which only the second heat exchanger is shown in a sectional view, and FIG. 2 is a schematic schematic configuration diagram of the heat exchanger unit. In both FIG. 1 and FIG. 2, the upper side of the drawing is the upper side of the heat exchanger unit.

  The heat exchanger unit 1 includes a first heat exchanger 10 and a second heat exchanger 20. The first heat exchanger 10 is arranged on the windward side in an airflow generated by a blower (not shown) (the arrow in FIG. 1 represents the airflow), and the second heat exchanger 20 is connected to the first heat exchanger 10. It is arranged on the leeward side in a back-and-forth manner. The first heat exchanger 10 and the second heat exchanger 20 are parallel to each other.

  The first heat exchanger 10 is a fin-and-tube type, in which a large number of rectangular fins 11 are arranged in parallel so that the longitudinal directions thereof are aligned in the vertical direction, and the large number of fins penetrates in the horizontal direction. Thus, the meandering tube 12 is arranged. When used as an evaporator, the port 13 provided at the upper end of the tube 12 serves as a refrigerant inflow port, and the port 14 provided at the lower end serves as a refrigerant outflow port. When used as a condenser, the refrigerant flows in the opposite direction, so the lower port 14 of the tube 12 serves as a refrigerant inlet and the upper port 13 serves as a refrigerant outlet. However, when used as an evaporator, even if the lower port 14 of the tube 12 is a refrigerant inlet and the upper port 13 is a refrigerant outlet, Even if the other port 13 is the refrigerant inlet and the lower port 14 is the refrigerant outlet, there is no particular problem.

  The fin 11 and the tube 12 are crimped by performing a tube expansion process for expanding the tube 12 from the inside after passing the tube 12 through the hole of the fin 11. Both the fin 11 and the tube 12 are made of a metal having good heat conductivity, such as aluminum. The tube 12 may be made of copper and the fin 11 may be made of aluminum.

The second heat exchanger 20 is a parallel flow type. In the second heat exchanger 20, two horizontal header pipes 21 and 22 are arranged in parallel with an interval in the vertical direction, and a plurality of vertical flat tubes 23 are arranged between the header pipes 21 and 22 at a predetermined pitch. It is a thing. The flat tube 23 is an elongated molded product obtained by extruding a metal having good heat conductivity such as aluminum, and a refrigerant passage 24 through which a refrigerant flows is formed inside. Since the flat tube 23 is disposed so that the extrusion molding direction is vertical, the refrigerant flow direction in the refrigerant passage 24 is also vertical. A plurality of refrigerant passages 24 having the same cross-sectional shape and cross-sectional area are arranged in the depth direction of FIG. 2, and therefore the flat tube 23 has a harmonica-like cross section. Each refrigerant passage 24 communicates with the inside of the header pipes 21 and 22.

Corrugated fins 25 are disposed between the flat tubes 23. The header pipes 21, 22 and the flat tube 23, and the flat tube 23 and the corrugated fin 25 are fixed by brazing or welding, respectively. In addition to the flat tube 23, the header pipes 21 and 22 and the corrugated fins 25 are also made of a metal having good thermal conductivity such as aluminum.

  A port 26 used as a refrigerant inlet or a refrigerant outlet is provided at one end of the upper header pipe 21. At one end of the lower header pipe 22, a port 27 used as a refrigerant outlet or a refrigerant inlet is provided at a position diagonal to the port 26.

Since many flat tubes 23 are provided between the header pipes 21 and 22 and corrugated fins 25 are provided between the flat tubes 23, the heat dissipation (heat absorption) area of the second heat exchanger 20 is large and efficient. Heat exchange can be performed. In the first heat exchanger 10, a gap remains between the expanded tube 12 and the fin 11, and this gap may become a resistance and the heat exchange efficiency may not be improved, but the second heat exchanger 20. Then, since the flat tube 23 and the corrugated fin 25 are fixed by brazing or welding, there is no gap between them. This is also a factor that improves the heat exchange efficiency as compared with the first heat exchanger 10.

  When the second heat exchanger 20 is used as an evaporator, the port 27 of the lower header pipe 22 serves as a refrigerant inlet, and the port 26 of the upper header pipe 21 serves as a refrigerant outlet. When used as a condenser, the flow of the refrigerant is reversed, so that the port 26 of the upper header pipe 21 serves as a refrigerant inlet, and the port 27 of the lower header pipe 22 serves as a refrigerant outlet. However, when used as an evaporator, the port 26 of the upper header pipe 21 serves as a refrigerant inlet, and the port 27 of the lower header pipe 22 serves as a refrigerant outlet, and is also used as a condenser. In such a case, even if the port 27 of the lower header pipe 22 serves as the refrigerant inlet and the port 26 of the upper header pipe 21 serves as the refrigerant outlet, there is no serious problem.

  The port 14 (refrigerant outlet) of the first heat exchanger 10 is connected to the port 27 (refrigerant inlet) of the second heat exchanger 20. Thereby, one continuous refrigerant flow path starting from the port 13 (refrigerant inlet) of the first heat exchanger 10 and continuing to the port 26 (refrigerant outlet) of the second heat exchanger is formed. It will be.

  When the heat exchanger unit 1 is used as an evaporator and a low-temperature refrigerant is allowed to flow from the port 13 (refrigerant inlet) to the port 26 (refrigerant outlet), moisture in the air condenses on the surface and frost is generated. Since the dew condensation phenomenon and the frost formation phenomenon occur more frequently in the first heat exchanger 10 on the leeward side than the second heat exchanger 20 on the leeward side, the first heat exchanger 10 has much condensation and frost formation. The dew condensation and frost formation of the second heat exchanger 20 are reduced by that amount. For this reason, the second heat exchanger 20 of the parallel flow type does not need to reduce the characteristic heat exchange efficiency so much. In addition, since the amount of water remaining in the second heat exchanger 20 is small, the bridge phenomenon is not a big problem.

  In the fin-and-tube type first heat exchanger 10, the time until frosting starts to exert an adverse effect is longer than that of the second heat exchanger 20. Moreover, since the drainage is better than the second heat exchanger 20, the condensed water is difficult to accumulate, and even if it forms frost, it can be easily washed away as defrosted water by defrosting operation. That is, even if dew condensation or frost formation occurs, even if the amount is large, adverse effects can be minimized.

  Further, when the heat exchanger unit 1 is used as a condenser, the refrigerant flows from the port 26 (refrigerant inlet) to the port 13 (refrigerant outlet). When the refrigerant is cooled to a supercooled state below the saturation temperature, the enthalpy difference is taken and the capacity is increased. By bringing the first heat exchanger 10 into a supercooled state, the condensation performance can be extracted.

  Thus, in the heat exchanger unit 1 of the first embodiment, the characteristics of the fin-and-tube type first heat exchanger 10 and the parallel flow type second heat exchanger 20 complement each other, and condensation and It is possible to obtain the heat exchanger unit 1 that is resistant to frost formation and has high heat exchange efficiency.

  If the material metal of the 1st heat exchanger 10 and the 2nd heat exchanger 20 is made into the same kind, for example, if both material metals are made into aluminum, the 1st heat exchanger 10 and the 2nd heat exchanger will be carried out. Even if 20 contacts, since the problem of corrosion due to contact of different metals does not occur, the first heat exchanger 10 and the second heat exchanger 20 can be arranged close to each other without worrying about the contact, The compact design of the heat exchanger unit 1 is facilitated.

  In addition, since it is highly likely that the fins 11 are particularly in contact with the second heat exchanger 20 in the first heat exchanger 10, at least the fins 11 are made of the same material metal as the second heat exchanger 20. It is good to form. Of course, if the entire first heat exchanger 10 is made of the same type of material metal as the second heat exchanger 20, which portion of the first heat exchanger 10 is the second heat exchanger 20. You don't have to worry about touching.

  In the first embodiment, the number of the tubes 12 of the fin-and-tube type first heat exchanger 10 is one, but a plurality of tubes 12 meandering in parallel are provided, and each tube 12 has a shunt. It is good also as using the structure which flows the refrigerant | coolant shunted in (3), and makes a refrigerant | coolant merge at the exit of each tube 12, and to make it flow out.

  Although the 1st heat exchanger 10 and the 2nd heat exchanger 20 are connected in series so that one continuous refrigerant | coolant flow path may be formed, the structure set as a parallel connection is also possible. The configuration is shown in FIG. 3 as a second embodiment.

  In the first heat exchanger 10 according to the second embodiment, the lower port 14 of the tube 12 serves as a refrigerant inlet, and the upper port 13 serves as a refrigerant outlet. In the second heat exchanger 20, the port 27 of the lower header pipe 22 serves as a refrigerant inlet, and the port 26 of the upper header pipe 21 serves as a refrigerant outlet. The port 26 is not located at a position diagonal to the port 27 but is provided on the same side as the port 27. The ports 14 and 27 are connected to a common refrigerant inlet 28, and the ports 13 and 26 are connected to a common refrigerant outlet 29.

  In the heat exchanger unit 1 of the second embodiment, the refrigerant flowing in from the refrigerant inlet 28 is divided into the port 14 and the port 27 and flows through the first heat exchanger 10 and the second heat exchanger 20, respectively. Then, they merge at the refrigerant outlet 29 and flow out. Needless to say, the first heat exchanger 10 is located on the leeward side, and the second heat exchanger 20 is located on the leeward side.

  Arrangement | positioning of the refrigerant | coolant inflow port 28 and the refrigerant | coolant outflow port 29 of 2nd Embodiment is an example, and is not limited to this. For example, it is possible to provide the refrigerant inlet 28 for the upper ports 13 and 26 and provide the refrigerant outlet 29 for the lower ports 14 and 27. Further, it is also possible to have a configuration in which the port 13 and the port 27, the port 14 and the port 26 are cross-connected, the refrigerant inlet 28 is provided at one of the cross connections, and the refrigerant outlet 29 is provided at the other.

  Next, a third embodiment of the present invention will be described with reference to FIGS. 4 is a side view of the heat exchanger unit, in which only the second heat exchanger is shown in a sectional view, and FIG. 5 is a schematic schematic configuration diagram of the heat exchanger unit. In addition, the same code | symbol as used in description of 1st Embodiment is attached | subjected to the component which is common in 1st Embodiment, and description is abbreviate | omitted.

  The heat exchanger unit 1 includes a first heat exchanger 10 disposed on the windward side in an air flow generated by a blower (not shown) and a second heat exchanger 30 disposed on the leeward side. Although the 1st heat exchanger 10 is a fin and tube type similarly to 1st Embodiment, the 2nd heat exchanger 30 is a serpentine type.

In the second heat exchanger 30, two horizontal header pipes 31 and 32 are arranged in parallel in a horizontal direction, and one meandering flat tube 33 is arranged between the header pipes 31 and 32. It is a thing. The flat tube 33 is an elongated molded product obtained by extruding a metal having good heat conductivity such as aluminum, and a refrigerant passage 34 for circulating a refrigerant is formed inside. A plurality of refrigerant passages 34 having the same cross-sectional shape and cross-sectional area are arranged in the left-right direction in FIG. 4 and in the depth direction in FIG. 5, so that the flat tube 33 has a cross section like a harmonica. Each refrigerant passage 34 communicates with the inside of the header pipes 31 and 32.

Corrugated fins 35 are arranged between parallel portions of the meandering flat tube 33. The header pipes 31 and 32 and the flat tube 33 and the flat tube 33 and the corrugated fin 35 are fixed by brazing or welding. In addition to the flat tube 33, the header pipes 31, 32 and the corrugated fins 35 are also made of a metal having good heat conductivity such as aluminum.

Since the corrugated fins 35 are provided between the parallel portions of the meandering flat tube 33, the heat dissipation (heat absorption) area of the second heat exchanger 30 is large, and heat exchange can be performed efficiently. One end of one header pipe 31 is provided with a port 36 used as a refrigerant inlet or outlet, and one end of the other header pipe 32 is provided with a port 37 used as a refrigerant outlet or inlet. Yes.

  The upper port 13 of the first heat exchanger 10 is connected to the port 36 of the second heat exchanger 30. Thereby, one continuous refrigerant | coolant flow path which connects the port 14 of the 1st heat exchanger 10 and the port 37 of the 2nd heat exchanger is formed.

  When the heat exchanger unit 1 is used as an evaporator and a low-temperature refrigerant is allowed to flow from the port 14 (refrigerant inlet) to the port 37 (refrigerant outlet), moisture in the air condenses on the surface and frost is generated. Since the dew condensation phenomenon and the frost formation phenomenon occur more frequently in the first heat exchanger 10 on the leeward side than the second heat exchanger 30 on the leeward side, the first heat exchanger 10 has much condensation and frost formation. The dew condensation and frost formation of the second heat exchanger 30 are reduced accordingly. For this reason, the serpentine-type second heat exchanger 30 does not require a significant reduction in the characteristic heat exchange efficiency. In addition, since the amount of water remaining in the second heat exchanger 30 is small, the bridge phenomenon is not a big problem.

  In the fin-and-tube type first heat exchanger 10, the time until frosting starts to exert an adverse effect is longer than that of the second heat exchanger 30. Further, since the drainage is better than the second heat exchanger 30, the condensed water is difficult to accumulate, and even if it forms frost, it can be easily washed away as defrosted water by defrosting operation. That is, even if dew condensation or frost formation occurs, even if the amount is large, adverse effects can be minimized.

  Further, when the heat exchanger unit 1 is used as a condenser, the refrigerant flows from the port 37 (refrigerant inlet) to the port 14 (refrigerant outlet). When the refrigerant is cooled to a supercooled state below the saturation temperature, the enthalpy difference is taken and the capacity is increased. By bringing the first heat exchanger 10 into a supercooled state, the condensation performance can be extracted.

  In this way, in the heat exchanger unit 1 of the third embodiment, the characteristics of the fin-and-tube type first heat exchanger 10 and the serpentine type second heat exchanger 30 complement each other, and condensation and adhesion It is possible to obtain the heat exchanger unit 1 that is resistant to frost and has high heat exchange efficiency.

  If the material metal of the 1st heat exchanger 10 and the 2nd heat exchanger 30 is made into the same kind, for example, if both material metals are made into aluminum, the 1st heat exchanger 10 and the 2nd heat exchanger will be carried out. Even if 30 contacts, the problem of corrosion due to the contact of different metals does not occur, so the first heat exchanger 10 and the second heat exchanger 30 can be arranged close to each other without worrying about the contact, The compact design of the heat exchanger unit 1 is facilitated.

  In addition, since it is highly likely that the fins 11 are particularly in contact with the second heat exchanger 30 in the first heat exchanger 10, at least the fins 11 are made of the same type of material metal as the second heat exchanger 30. It is good to form. Of course, if the entire first heat exchanger 10 is made of the same type of material metal as the second heat exchanger 30, which part of the first heat exchanger 10 is the second heat exchanger 30. You don't have to worry about touching.

  In the third embodiment, the number of the tubes 12 of the fin-and-tube type first heat exchanger 10 is one, but a plurality of tubes 12 meandering in parallel are provided, and each of the tubes 12 has a current divider. It is good also as using the structure which flows the refrigerant | coolant shunted in (3), and makes a refrigerant | coolant merge at the exit of each tube 12, and to make it flow out.

  The first heat exchanger 10 and the second heat exchanger 30 are connected in series so as to form one continuous refrigerant flow path, but a configuration in which they are connected in parallel is also possible. The configuration is shown in FIG. 6 as a fourth embodiment.

  In the first heat exchanger 10 according to the fourth embodiment, the upper port 13 of the tube 12 serves as a refrigerant inlet, and the lower port 14 serves as a refrigerant outlet. The port 13 of the first heat exchanger 10 and the port 36 of the second heat exchanger 30 are connected to a common refrigerant inlet 38.

  In the heat exchanger unit 1 of the fourth embodiment, the refrigerant flowing in from the refrigerant inflow port 38 is divided into the port 13 and the port 36, and flows through the first heat exchanger 10 and the second heat exchanger 30, respectively. Then, it flows out from the port 14 (refrigerant outlet) and the port 37 (refrigerant outlet). Needless to say, the first heat exchanger 10 is located on the leeward side, and the second heat exchanger 30 is located on the leeward side.

  The heat exchanger unit 1 from 1st Embodiment to 4th Embodiment can be used as a heat exchanger unit of the outdoor unit of the heat pump type air conditioner which consists of an outdoor unit and an indoor unit. A configuration example of such an air conditioner is shown in FIG.

  The air conditioner uses a heat pump cycle 101 as a refrigeration cycle. The heat pump cycle 101 includes a compressor 102, a four-way valve 103, an outdoor unit heat exchanger unit 104, a decompression expansion device 105, and an indoor unit heat exchanger unit 106 connected in a loop.

  During the cooling operation, the high-temperature and high-pressure refrigerant discharged from the compressor 102 enters the heat exchanger unit 104 from the four-way valve 103, dissipates heat there, and condenses. The refrigerant exiting the heat exchanger unit 104 enters the heat exchanger unit 106 of the indoor unit from the decompression / expansion device 105, expands there, takes heat from indoor air, and returns to the compressor 102 via the four-way valve 103.

  During the heating operation, the flow of the refrigerant is reversed, and the high-temperature and high-pressure refrigerant discharged from the compressor 102 enters the heat exchanger unit 106 of the indoor unit from the four-way valve 103, where it dissipates heat and condenses. The refrigerant exiting the heat exchanger unit 106 enters the heat exchanger unit 104 of the outdoor unit from the decompression / expansion device 105, expands there, takes heat from the outdoor air, and then returns to the compressor 102 via the four-way valve 103.

  By using the heat exchanger unit 1 from the first embodiment to the fourth embodiment as the heat exchanger unit 104 of the outdoor unit, the characteristics of the fin-and-tube type heat exchanger and the heat exchange of the parallel flow type or the serpentine type It is possible to provide an efficient air conditioner including a heat exchanger unit that complements the characteristics of the vessel, is resistant to condensation and frost formation, and has high heat exchange efficiency.

  As mentioned above, although each embodiment of the present invention was described, the scope of the present invention is not limited to this, and various modifications can be made without departing from the spirit of the invention.

  The present invention is widely applicable to a heat exchanger unit that combines a plurality of heat exchangers.

In the side view of the heat exchanger unit according to the first embodiment, only the second heat exchanger is shown in a sectional view. Typical schematic block diagram of the heat exchanger unit of 1st Embodiment Schematic schematic block diagram of a heat exchanger unit according to the second embodiment In the side view of the heat exchanger unit according to the third embodiment, only the second heat exchanger is shown in a sectional view. Typical schematic block diagram of the heat exchanger unit of 3rd Embodiment Typical schematic block diagram of the heat exchanger unit which concerns on 4th Embodiment Refrigeration cycle diagram of an air conditioner in which the heat exchanger unit of the present invention is used

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Heat exchanger unit 10 Fin and tube type 1st heat exchanger 20 Parallel flow type 2nd heat exchanger 30 Serpentine type 2nd heat exchanger

Claims (4)

In the heat exchanger unit of an outdoor unit of an air conditioner that is used as a condenser during cooling and as an evaporator during heating,
A fin-and-tube type first heat exchanger and a parallel flow type having corrugated fins or a serpentine type second heat exchanger having corrugated fins,
The corrugated fin of the second heat exchanger is disposed between flat tubes in which a refrigerant passage through which a refrigerant flows is formed,
In the airflow generated by the blower, the first heat exchanger and the second heat exchanger are configured such that the first heat exchanger is on the windward side and the second heat exchanger is on the leeward side. In close proximity to each other ,
The plurality of fins of the first heat exchanger are arranged in parallel so that their longitudinal directions are aligned in the vertical direction,
The corrugated fins of the second heat exchanger fit within the vertical width of the fins of the first heat exchanger;
The heat exchanger unit, wherein the refrigerant first flows into the first heat exchanger during heating.   The heat exchanger unit according to claim 1, wherein the fin material metal of the first heat exchanger and the material metal of the second heat exchanger are the same type.   3. The heat exchanger unit according to claim 2, wherein the first heat exchanger and the second heat exchanger are made of the same type of material metal.   The heat exchanger unit according to any one of claims 1 to 3, wherein the material metal of the second heat exchanger is aluminum.

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