JP5385589B2 - Air conditioner outdoor unit - Google Patents

Description

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

  There is an air conditioner called a separate type. The outdoor unit includes an outdoor unit and an indoor unit. The outdoor unit includes a compressor, a four-way valve, an expansion valve, an outdoor heat exchanger, an outdoor fan, and the indoor unit includes an indoor heat exchanger, an indoor fan, and the like. . The outdoor heat exchanger functions as an evaporator during heating operation and functions as a condenser during cooling operation. The indoor heat exchanger functions as a condenser during heating operation and functions as an evaporator during cooling operation.

  FIG. 10 shows a basic configuration of a separate type air conditioner that uses a heat pump cycle as a refrigeration cycle. The heat pump cycle 1 includes a compressor 2, a four-way valve 3, an outdoor heat exchanger 4, a decompression expansion device 5, and an indoor heat exchanger 6 connected in a loop. The compressor 2, the four-way valve 3, the heat exchanger 4, and the decompression / expansion device 5 are accommodated in the casing of the outdoor unit, and the heat exchanger 6 is accommodated in the casing of the indoor unit. An outdoor blower 7 is combined with the heat exchanger 4, and an indoor blower 8 is combined with the heat exchanger 6. The blower 7 is often composed of a propeller fan, and the blower 8 is often composed of a cross flow fan.

  FIG. 10 shows a state during heating operation. At this time, the high-temperature and high-pressure refrigerant discharged from the compressor 2 enters the heat exchanger 6 on the indoor side, dissipates heat, and condenses. The refrigerant that has exited the heat exchanger 6 enters the outdoor heat exchanger 4 from the decompression / expansion device 5, expands there, takes heat from the outdoor air, and returns to the compressor 2. The air flow generated by the indoor air blower 8 promotes heat dissipation from the heat exchanger 6, and the air flow generated by the outdoor air blower 7 promotes heat absorption of the heat exchanger 4.

  FIG. 11 shows a state during cooling operation or defrosting operation. At this time, the refrigerant flow is reversed from that during the heating operation. That is, the high-temperature and high-pressure refrigerant discharged from the compressor 2 enters the outdoor heat exchanger 4 where it dissipates heat and condenses. The refrigerant that has exited the heat exchanger 4 enters the indoor heat exchanger 6 from the decompression / expansion device 5, expands there, takes heat from indoor air, and returns to the compressor 2. The air flow generated by the outdoor blower 7 promotes heat dissipation from the heat exchanger 4, and the air flow generated by the indoor blower 8 promotes heat absorption of the heat exchanger 6.

  The outdoor unit of the separate type air conditioner as described above has a rectangular parallelepiped shape as a whole, has a substantially rectangular plane shape, and has various functions in a housing in which the long side is the front and back, and the short side is the left and right sides. It is customary to house the parts. A configuration example of a conventional outdoor unit is shown in FIG.

  The outdoor unit 10 in FIG. 12 includes a sheet metal casing 10a having a substantially rectangular planar shape. The long side of the casing 10a is a front surface 10F and a back surface 10B, and the short side is a left side surface 10L and a right side surface 10R. An exhaust port 11 is formed on the front surface 10F, and a rear intake port 12 is formed on the back surface 10B. The exhaust port 11 is composed of a set of a plurality of horizontal slit-shaped openings, and the rear intake port 12 is composed of a lattice-shaped opening. A top plate and a bottom plate (not shown) are added to the four sheet metal members of the front surface 10F, the back surface 10B, the left side surface 10L, and the right side surface 10R to form a hexahedral-shaped housing 10a.

  Inside the housing 10a, the outdoor heat exchanger 4 is arranged just inside the rear intake port 12. In order to forcibly perform heat exchange between the heat exchanger 4 and the outdoor air, an outdoor blower 7 is disposed between the heat exchanger 4 and the exhaust port 11. The blower 7 is a combination of an electric motor 7a and a propeller fan 7b. In order to improve the blowing efficiency, a bell mouth 13 surrounding the propeller fan 7b is attached to the inner surface of the front surface 10F of the housing 10a. The space inside the right side surface 10R of the housing 10a is separated from the air flow flowing from the rear intake port 12 to the exhaust port 11 by the partition wall 14, and the compressor 2 is accommodated therein.

  As the heat exchanger 4, a fin and tube type, a parallel flow type, a serpentine type, or the like is used. The fin-and-tube type is a type in which a single tube passes through many parallel fins while meandering. 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 a flat tube is placed between two header pipes, but the number of flat tubes is one, and the single flat tube is meandered to meander. A fin such as a corrugated fin is disposed between the flat tubes.

  In the configuration example of FIG. 12, the heat exchanger 4 exists only on the back side of the housing 10a. However, in order to increase the heat exchange area, a heat exchanger may be arranged on the side surface of the housing 10a. An example of such a configuration is shown in FIG. In the configuration example of FIG. 13, a side air inlet 12 a is formed on the left side surface 10 </ b> L, and a side surface side heat exchanger 4 a is disposed immediately inside thereof. For comparison with the “side heat exchanger”, the heat exchanger 4 is hereinafter referred to as “back heat exchanger”.

  FIG. 14 shows the rear side heat exchanger 4 and the side side heat exchanger 4a arranged side by side on the same plane. The back side heat exchanger 4 is a parallel flow down flow type. The back side heat exchanger 4 is arranged such that the upper header pipe 21 and the lower header pipe 22 are spaced horizontally from each other, that is, parallel to each other, and perpendicular to the upper header pipe 21 and the lower header pipe 22. A plurality of flat tubes 23 are arranged at a predetermined pitch, and corrugated fins 24 are arranged between adjacent flat tubes 23. The flat tube 23 is an elongated molded product obtained by extruding a metal having good heat conductivity such as aluminum, and has a refrigerant passage through which a refrigerant flows. Since the flat tube 23 is disposed so that the extrusion molding direction is vertical, the refrigerant flow direction in the refrigerant passage is also vertical. In one configuration example of the refrigerant passage, a plurality of ones having the same cross-sectional shape and cross-sectional area are arranged in the depth direction of FIG. 14, and thus the flat tube 23 has a harmonica-like cross section. Each refrigerant passage communicates with the inside of the upper header pipe 21 and the lower header pipe 22.

  The upper header pipe 21, the lower header pipe 22, and the flat tube 23, and the flat tube 23 and the corrugated fin 24 are fixed by brazing or welding, respectively. In addition to the flat tube 23, the upper header pipe 21, the lower header pipe 22, and the corrugated fin 24 are also made of a metal having good thermal conductivity such as aluminum.

  The side heat exchanger 4 a is also a parallel flow downflow type like the back heat exchanger 4, but the lateral width is narrower than that of the back heat exchanger 4. In the side heat exchanger 4a, the upper header pipe 21a and the lower header pipe 22a are arranged horizontally at intervals from each other, that is, in parallel with each other, and perpendicular to the upper header pipe 21a and the lower header pipe 22a. A plurality of flat tubes 23a are arranged at a predetermined pitch, and corrugated fins 24a are arranged between adjacent flat tubes 23a. The flat tube 23a is an elongated molded product obtained by extruding a metal having good heat conductivity such as aluminum, and a refrigerant passage through which a refrigerant flows is formed inside. Since the flat tube 23a is arranged so that the extrusion molding direction is vertical, the refrigerant flow direction in the refrigerant passage is also vertical. In one configuration example of the refrigerant passage, a plurality of tubes having the same cross-sectional shape and cross-sectional area are arranged in the depth direction of FIG. 14, and therefore the flat tube 23a has a cross section like a harmonica. Each refrigerant passage communicates with the inside of the upper header pipe 21a and the lower header pipe 22a.

  The upper header pipe 21a and the lower header pipe 22a and the flat tube 23a, and the flat tube 23a and the corrugated fin 24a are fixed by brazing or welding, respectively. In addition to the flat tube 23a, the upper header pipe 21a, the lower header pipe 22a, and the corrugated fin 24a are also made of a metal having good thermal conductivity such as aluminum.

  The number of the flat tubes 23 a of the side heat exchanger 4 a is less than the number of the flat tubes 23 of the back heat exchanger 4. Therefore, the cross-sectional area of the refrigerant flow path of the side heat exchanger 4a, which is the total refrigerant passage area of the flat tube 23a, is smaller than that of the back heat exchanger 4.

  Refrigerant pipes 25 and 26 are connected to one end on the same side of the upper header pipe 21 and the lower header pipe 22 of the back side heat exchanger 4. The other end of the upper header pipe 21 is connected to one end of the upper header pipe 21a of the side heat exchanger 4a through the refrigerant pipe 25a, and the other end of the lower header pipe 22 is connected to the lower header of the side heat exchanger 4a through the refrigerant pipe 26a. Connected to one end of the pipe 22a. The other ends of the upper header pipe 21a and the lower header pipe 22a are dead ends. The back surface side heat exchanger 4 and the side surface side heat exchanger 4a are in a parallel connection relationship.

  The refrigerant pipes 25 and 26 are configured to send refrigerant to both the back surface side heat exchanger 4 and the side surface side heat exchanger 4a and receive refrigerant from both the back surface side heat exchanger 4 and the side surface side heat exchanger 4a. . During the cooling operation, a high-temperature and high-pressure refrigerant at least partially in the form of gas flows from the refrigerant pipe 25. The refrigerant dissipates heat to the outdoor air while descending the refrigerant passages of the back-side heat exchanger 4 and the side-side heat exchanger 4a and condenses into a liquid state. During the heating operation, the refrigerant flows in from the refrigerant pipe 26, and evaporates by taking in heat from the outdoor air as it rises through the refrigerant passages of the back-side heat exchanger 4 and the side-side heat exchanger 4a.

  When the blower 7 is operated, outdoor air flows from the rear intake port 12 and the side intake port 12a. The outdoor air that flowed in from the rear air inlet 12 exchanged heat with the rear heat exchanger 4, and the outdoor air that flowed in from the side air inlet 12a exchanged heat with the side heat exchanger 4a. Thereafter, the air is sucked into the blower 7 and discharged from the exhaust port 11.

  Examples of heat exchangers in which two heat exchangers are arranged at right angles can be seen in Patent Document 1 to Patent Document 3, such as a combination of the above-described back-side heat exchanger and side-side heat exchanger.

  In the heat exchanger described in Patent Document 1, a parallel flow side flow type heat exchanger is formed into a right angle by bending a flat tube to make a right angle.

  The heat exchanger described in Patent Document 2 is a parallel flow downflow type heat exchanger that is bent at a right angle by bending a header pipe.

  The heat exchanger described in Patent Document 3 includes two parallel-flow downflow type heat exchangers, one having a wide main core and the other having a narrow sub-core, arranged at right angles to each other. . The refrigerant flows in the main core and the slave core in the same manner as the refrigerant flows to the back-side heat exchanger 4 and the side-side heat exchanger 4a in FIG.

In order to increase the heat exchange area of the heat exchanger, a plurality of heat exchangers may be arranged in a plurality of rows aligned in the airflow direction. Patent Document 4 describes a configuration in which parallel flow type heat exchangers are arranged in a plurality of rows. Patent Document 5 describes a configuration in which a plurality of strip plate-like tube elements are stacked in the thickness direction.
JP 2008-45862 A Japanese Patent Laid-Open No. 2005-90806 JP-A-10-160382 JP 2002-13840 A JP 2001-108392 A

  In order to effectively utilize the space in the housing of the outdoor unit, when the heat exchanger is also arranged on the side surface of the housing, the heat exchanger is bent as in the case of Patent Document 1 or Patent Document 2, and the side surface side Forming the heat exchanger is difficult to process because there is a risk that the flat tube and header pipe will be broken if one step is wrong. Moreover, the side flow type heat exchanger has poor drainage and is difficult to use as an evaporator. In the configuration in which two independent heat exchangers are arranged at right angles like the one described in Patent Document 3, there are few problems that the ones described in Patent Document 1 and Patent Document 2 have. However, in the case of the configuration described in Patent Document 3, the flat tube of the back side heat exchanger and the flat tube of the side side heat exchanger are in a parallel relationship, and the heat exchange area is expanded compared to the case of only the back side heat exchanger. That said, the cross-sectional area of the refrigerant flow path remains large and constant, and as the refrigerant gradually liquefies from the gas and the specific volume decreases, the flow velocity of the refrigerant decreases, leading to a decrease in heat transfer coefficient. As a result, the performance of the entire heat exchanger may deteriorate. Thus, simply expanding the heat exchange area does not lead to efficient supercooling of the refrigerant, and has not led to an improvement in performance commensurate with the expansion of the heat exchange area.

  The present invention has been made in view of the above points, and can obtain a large heat exchange area relatively easily, and can effectively promote supercooling without reducing the flow rate of the liquefied refrigerant. An object of the present invention is to provide an outdoor unit for an air conditioner.

  In order to achieve the above object, the present invention accommodates a compressor, a heat exchanger, and a blower in a casing having a substantially rectangular planar shape, with the long side on the front and back and the short side on the left and right sides. In the outdoor unit of an air conditioner, the housing includes a rear intake port and a side intake port formed on the rear surface and one side surface, and an exhaust port formed on the front surface, and the exhaust port is formed inside the exhaust port. Through which a blower that discharges air in the housing is arranged, and a rear-side heat exchanger and a side-side heat exchanger, both of which are parallel flow downflow types, are arranged inside the rear inlet and the side inlet, The back-side heat exchanger and the side-side heat exchanger are connected so that the refrigerant that has passed through the flat tube of the back-side heat exchanger is sent to the side-side heat exchanger during condensation, and the back-side heat exchange At least one of the heat exchanger and the side heat exchanger A plurality of heat exchangers aligned in a direction, and a refrigerant circuit that flows from the leeward heat exchanger to the windward heat exchanger during condensation is formed between the plurality of heat exchangers. It is a feature.

  The flow path area of the side heat exchanger is inevitably smaller than the flow path area of the back heat exchanger. When these heat exchangers are used as condensers, the refrigerant in the gas state is quickly condensed while passing through the back side heat exchanger having a relatively large channel area, and the condensed liquid refrigerant is exchanged with the back side heat exchange. Since the refrigerant flow rate is not lowered and the supercooling state is achieved while passing through the side surface side heat exchanger having a smaller flow path area than the condenser, the supercooling can be efficiently advanced. Further, since the side heat exchanger is cooled by the external air sucked from the side air inlet, the cooling air of the side heat exchanger can be sufficiently secured, and the supercooling can be sufficiently promoted.

  Furthermore, at least one of the rear side heat exchanger and the side side heat exchanger is configured by a plurality of heat exchangers aligned in the airflow direction, and the heat exchanger on the leeward side during the condensation is between the plurality of heat exchangers. Since the refrigerant circuit that flows from the heat exchanger to the windward heat exchanger is formed, the heat exchange area of the rear heat exchanger or the side heat exchanger is increased, and the heat exchange capacity as an outdoor unit is increased. Can do.

  In the outdoor unit of the air conditioner having the above-described configuration, in the back side heat exchanger or the side side heat exchanger configured by a plurality of heat exchangers aligned in the airflow direction, the refrigerant is in the lee side heat during condensation. A refrigerant that flows into the upper header pipe of the exchanger and flows out of the lower header pipe of the heat exchanger, and then flows into the upper header pipe of the adjacent upwind heat exchanger and flows out of the lower header pipe of the heat exchanger A circuit is preferably constructed.

  With such a configuration, it is possible to reasonably create a form in which the condensed refrigerant flows downward without resisting gravity, and the heat exchange efficiency can be improved.

  In the outdoor unit of the air conditioner having the above-described configuration, in the back side heat exchanger or the side heat exchanger configured by a plurality of heat exchangers aligned in the airflow direction, an adjacent leeward heat exchanger and It is preferable that the upper header pipes or the lower header pipes of the upwind heat exchanger are integrated.

  With such a configuration, the structure of the heat exchanger can be strengthened.

  In the outdoor unit of the air conditioner configured as described above, in the refrigerant circuit passing through the side heat exchanger from the back side heat exchanger, the refrigerant flow path is located closer to the downstream side of the refrigerant flow at the time of condensation. The cross-sectional area is preferably small.

  With such a configuration, the condensed liquid refrigerant is in a supercooled state while passing through a plurality of heat exchangers in which the refrigerant channel cross-sectional area sequentially decreases, so that a decrease in the refrigerant flow rate can be suppressed. Supercooling can be efficiently advanced.

  In the outdoor unit of the air conditioner having the above-described configuration, it is preferable that a gas-liquid separator is disposed in the middle of the refrigerant circuit that passes through the back-side heat exchanger and the side-side heat exchanger.

  With such a configuration, when used as an evaporator, the gas-liquid two-phase refrigerant that has passed through the side heat exchanger and has been vaporized is separated into a gas and a liquid, and the liquid is the back heat exchanger. By passing through the refrigerant, the flow of refrigerant can be improved and the heat exchange efficiency can be increased.

  In the outdoor unit for an air conditioner configured as described above, the back-side heat exchanger is disposed with a predetermined gap between the bottom plate of the casing and flows out of the side-side heat exchanger during condensation. Preferably, the refrigerant pipe through which the refrigerant flows crosses the airflow passing through the gap.

  With such a configuration, heat exchange can be performed between the airflow passing through the gap between the back-side heat exchanger and the housing bottom plate and the refrigerant that has flowed out of the side-side heat exchanger during condensation. Supercooling can be promoted.

  According to the present invention, by providing the side heat exchanger in addition to the rear heat exchanger, the space in the housing of the outdoor unit is effectively utilized to expand the heat exchange area, and the refrigerant in the gas state is relatively Since the refrigerant is quickly condensed in the rear side heat exchanger with a large channel area, the refrigerant enters the side heat exchanger with a relatively small channel area. Therefore, supercooling can be promoted efficiently. Further, since the side heat exchanger is cooled by the external air sucked from the side air inlet, the cooling air of the side heat exchanger can be sufficiently secured, and the supercooling can be sufficiently promoted. And at least one of the back side heat exchanger and the side side heat exchanger is composed of a plurality of heat exchangers aligned in the airflow direction, and between the plurality of heat exchangers, from the leeward side heat exchanger during condensation Since the refrigerant circuit that flows to the heat exchanger on the windward side is formed, the heat exchange area of the rear heat exchanger or the side heat exchanger can be increased, and the heat exchange capacity as an outdoor unit can be increased. it can.

  Hereinafter, a first embodiment of the present invention will be described with reference to FIGS. FIG. 1 is a schematic horizontal sectional view showing a schematic configuration of an outdoor unit of an air conditioner, FIG. 2 is a development view of a heat exchanger, and FIG. 3 is a development view of a heat exchanger showing an operation mode different from FIG. The structure of the embodiment is common to the conventional structure shown in FIGS. Therefore, in order to avoid duplication of explanation, the same reference numerals as those used in FIG. 13 and FIG. 14 are attached to the components common to the conventional structure of FIG. 13 and FIG.

  The back-side heat exchanger and the side-side heat exchanger of the embodiment are a parallel-flow downflow type as in the conventional structure. However, the back-side heat exchanger and the side-side heat exchanger are connected in series instead of in parallel as in the conventional structure. Each of the back surface side heat exchanger and the side surface side heat exchanger is composed of two heat exchangers aligned in the airflow direction. That is, the back side heat exchanger is configured by a first back side heat exchanger 4-1 located on the leeward side and a second back side heat exchanger 4-2 located on the leeward side, and the side heat exchanger is on the leeward side. The first side surface side heat exchanger 4a-1 located on the upper side and the second side surface side heat exchanger 4a-2 located on the windward side. And these four heat exchangers are provided with the structure shown in FIG. 2, and a mutual refrigerant circuit is comprised as shown in FIG. Roughly speaking, the first back side heat exchanger 4-1 and the second back side heat exchanger 4-2 are connected in series, and the second side heat exchanger 4a-1 and the second side heat The exchanger 4a-2 is also connected in series.

  The first back side heat exchanger 4-1 has basically the same structure as the back side heat exchanger 4 of FIG. 13, and the upper header pipe 21-1 and the lower header pipe 22-1 are horizontally spaced from each other. In other words, a plurality of vertical flat tubes 23-1 are arranged at a predetermined pitch between the upper header pipe 21-1 and the lower header pipe 22-1 and arranged adjacent to each other. A corrugated fin 24-1 is disposed between the two. A refrigerant pipe 25 is connected to the upper header pipe 21-1. The refrigerant pipe 25 is divided into two pipes in the middle, and one pipe is connected to each end of the upper header pipe 21-1. One refrigerant pipe 27 is connected to each end of the lower header pipe 22-1.

  When using the 1st back side heat exchanger 4-1 as an evaporator, it becomes the composition of the refrigerant circuit which a refrigerant flows in from lower header pipe 22-1 and a refrigerant flows out from upper header pipe 21-1. In this case, when the refrigerant flows only from one end of the lower header pipe 22-1 and the refrigerant flows out only from one end of the upper header pipe 21-1, the number of the flat tubes 23-1 is large. Depending on the operating conditions, there is a considerable difference in the amount of refrigerant flowing through each flat tube 23-1. The so-called “diversion” is in a bad state. If the refrigerant flows in from both ends of the lower header pipe 22-1 and the refrigerant flows out from both ends of the upper header pipe 21-1, as in the configuration of the present embodiment, the diversion is improved.

  The second back side heat exchanger 4-2 has basically the same structure as the back side heat exchanger 4 of FIG. 13, and the upper header pipe 21-2 and the lower header pipe 22-2 are spaced horizontally from each other. In other words, a plurality of vertical flat tubes 23-2 are arranged at a predetermined pitch between the upper header pipe 21-2 and the lower header pipe 22-2, and arranged adjacent to each other. A corrugated fin 24-2 is disposed between the two. One refrigerant pipe 27 is connected to each end of the upper header pipe 21-2. One refrigerant pipe 28 is connected to each end of the lower header pipe 22-2. When using the 2nd back side heat exchanger 4-2 as an evaporator, like the 1st back side heat exchanger 4-1, a refrigerant flows in from both ends of lower header pipe 22-2, and upper header pipe 21- Since the refrigerant flows out from both ends of 2, the shunt flow is improved.

  The first side heat exchanger 4a-1 has basically the same structure as the side heat exchanger 4a of FIG. 14, and the upper header pipe 21a-1 and the lower header pipe 22a-1 are horizontally spaced from each other. In other words, the flat tubes 23a-1 are arranged in parallel with each other, and a plurality of vertical flat tubes 23a-1 are arranged at a predetermined pitch between the upper header pipe 21a-1 and the lower header pipe 22a-1. Corrugated fins 24a-1 are arranged between the two. One refrigerant pipe 28 is connected to each end of the upper header pipe 21a-1. One refrigerant pipe 29 is connected to each end of the lower header pipe 22a-1. When the first side heat exchanger 4a-1 is used as an evaporator, the refrigerant flows from both ends of the lower header pipe 22a-1 as in the first rear heat exchanger 4-1, and the upper header pipe 21a- Since the refrigerant flows out from both ends of 1, the shunt flow is improved.

  Unlike the refrigerant pipe 27 and the refrigerant pipe 28, the refrigerant pipe 29 remains divided into two and does not go toward the second side heat exchanger 4a-2. It is integrated into one on the way.

  The second side heat exchanger 4a-2 has basically the same structure as the side heat exchanger 4a in FIG. 14, and the upper header pipe 21a-2 and the lower header pipe 22a-2 are horizontally spaced from each other. That is, a plurality of vertical flat tubes 23a-2 are arranged at a predetermined pitch between the upper header pipe 21a-2 and the lower header pipe 22a-2, and arranged adjacent to each other. Corrugated fins 24a-2 are disposed between the two. As described above, the upper header pipe 21a-2 is integrated into one at the left end (referring to the left end in FIG. 2; hereinafter, "left end" or "right end" means the left end or right end in FIG. 2). Refrigerant piping 29 is connected. A refrigerant pipe 30 is connected to the right end of the lower header pipe 22a-2.

  A partition wall 31a is formed in the upper header pipe 21a-2 at a position spaced a predetermined distance from the left end. A partition wall 31b is also formed in the lower header pipe 22a-2 at a position spaced a predetermined distance from the left end. The partition wall 31b is located further to the right than the partition wall 31a, and as a result, the second side heat exchanger 4a-2 is divided into three sections. That is, the first section 4a-2A from the left end to the partition 31a, the second section 4a-2B from the partition 31a to the partition 31b, and the third section 4a-2C from the partition 31b to the right end.

  As described above, during the cooling operation or the defrosting operation (that is, when the outdoor heat exchanger is used as a condenser), the upper header pipe 21- of the first rear side heat exchanger 4-1 is connected from the refrigerant pipe 25. 1 is supplied with a high-temperature and high-pressure refrigerant at least partially in a gaseous state. The refrigerant dissipates heat to the outdoor air while descending the refrigerant passage of the flat tube 23-1, and at least a part of the refrigerant is condensed. The refrigerant that has passed through the first back-side heat exchanger 4-1 flows into the upper header pipe 21-2 of the second back-side heat exchanger 4-2 through the refrigerant pipe 27. While the refrigerant descends the refrigerant passage of the flat tube 23-2, it dissipates heat to the outdoor air and condenses, and further liquefaction proceeds.

  The refrigerant that has passed through the second back side heat exchanger 4-2 flows into the upper header pipe 21a-1 of the first side face side heat exchanger 4a-1 through the refrigerant pipe 28. The refrigerant again dissipates heat into the outdoor air while descending the refrigerant passage of the flat tube 23a-1. The refrigerant that has passed through the first side heat exchanger 4a-1 flows through the refrigerant pipe 29 into the upper header pipe 21a-2 of the second side heat exchanger 4a-2.

  The refrigerant that has flowed into the upper header pipe 21a-2 of the second side heat exchanger 4a-2 descends the refrigerant passage of the flat tube 23a-2 included in the first section 4a-2A, and the lower header pipe 22a-2. To reach. The refrigerant then moves to the second section 4a-2B, rises in the refrigerant passage of the flat tube 23a-2 included in the second section 4a-2B, and reaches the upper header pipe 21a-2. The refrigerant then moves to the third section 4a-2C, descends the refrigerant passage of the flat tube 23a-2 included in the third section 4a-2C, and reaches the lower header pipe 22a-2. In this way, the refrigerant dissipates heat to the outdoor air while repeatedly descending and raising, so that the refrigerant can be easily supercooled. The refrigerant descending the third section 4a-2C and reaching the lower header pipe 22a-2 flows out through the refrigerant pipe 30 and is sent to the indoor unit.

  In this way, the gaseous refrigerant is quickly condensed while passing through the back-side heat exchanger having a larger flow path area than the side-side heat exchanger, and the condensed liquid refrigerant is flowed more than the back-side heat exchanger. Since the refrigerant flow rate is not lowered while passing through the side surface side heat exchanger having a small area, the supercooling state can be achieved efficiently. Further, since the side heat exchanger is cooled by the external air sucked from the side air inlet 12a, the cooling air for the side heat exchanger can be sufficiently secured, and the supercooling can be promoted sufficiently.

  The rear-side heat exchanger is configured by arranging the first rear-side heat exchanger 4-1 on the leeward side and the second rear-side heat exchanger 4-2 on the leeward side in the airflow direction, and the first side at the time of condensation. A refrigerant circuit that flows from the back side heat exchanger 4-1 to the second back side heat exchanger 4-2 is formed, and the side surface side heat exchanger is connected to the first side surface side heat exchanger 4a-1 on the leeward side and the windward side. The second side heat exchanger 4a-2 is arranged in the direction of the airflow, and the refrigerant circuit flows from the first side heat exchanger 4a-1 to the second side heat exchanger 4a-2 during condensation. Therefore, the heat exchange area of the back side heat exchanger and the side side heat exchanger can be increased, and the heat exchange capacity of the outdoor unit 10 can be increased.

  In the back side heat exchanger, at the time of condensation, the refrigerant flows into the upper header pipe 21-1 of the first back side heat exchanger 4-1 on the leeward side, flows out from the lower header pipe 22-1, and then It flows into the upper header pipe 21-2 of the second rear side heat exchanger 4-2 on the windward side and flows out from the lower header pipe 22-2. In the side heat exchanger, during condensation, the refrigerant flows into the upper header pipe 21a-1 of the first side heat exchanger 4a-1 on the leeward side, flows out from the lower header pipe 22a-1, and then It flows into the upper header pipe 21a-2 of the second side heat exchanger 4a-2 on the windward side and flows out from the lower header pipe 22a-2. As a result, a form in which the condensed refrigerant flows downward can be created without difficulty, and the heat exchange efficiency can be improved.

  As shown in FIG. 3, during the heating operation, the refrigerant flows into the lower header pipe 22a-2 of the second side heat exchanger 4a-2 from the refrigerant pipe 30. The refrigerant takes in heat from the outdoor air and evaporates while flowing from the third section 4a-2C to the second section 4a-2B and the first section 4a-2A. The refrigerant flows from the upper header pipe 21a-2 into the lower header pipe 22a-1 of the first side heat exchanger 4a-1 through the refrigerant pipe 29. While the refrigerant rises from the lower header pipe 22a-1 to the upper header pipe 21a-1, it further takes in heat from the outdoor air and evaporates. The refrigerant flows from the upper header pipe 21a-1 into the lower header pipe 22-2 of the second back side heat exchanger 4-2 through the refrigerant pipe 28. While the refrigerant rises from the lower header pipe 22-2 to the upper header pipe 21-2, it further takes in heat from the outdoor air and evaporates. The refrigerant flows from the upper header pipe 21-2 through the refrigerant pipe 27 into the lower header pipe 22-1 of the first back side heat exchanger 4-1. While the refrigerant rises from the lower header pipe 22-1 to the upper header pipe 21-1, it further takes in heat from the outdoor air and evaporates.

  In the configuration of the first embodiment, the first back-side heat exchanger 4-1 and the second back-side heat exchanger 4-2 have the same shape and the same refrigerant flow path cross-sectional area, and the first side-side heat exchanger. 4a-1 has a smaller refrigerant flow path cross-sectional area than the first backside heat exchanger 4-1 and the second backside heat exchanger 4-2, and the second side heat exchanger 4a-2 is the first side. Although the external dimensions are the same as those of the heat exchanger 4a-2, the refrigerant channel cross-sectional area is smaller than that of the first side heat exchanger 4a-1 because it is divided into three sections. When comparing the second back-side heat exchanger 4-2, the first side-side heat exchanger 4a-1, and the second side-side heat exchanger 4a-2, heat exchange located on the downstream side of the refrigerant flow during condensation The cross-sectional area of the refrigerant flow path is smaller as the container is used. For this reason, the condensed liquid refrigerant is in a supercooled state without decreasing the refrigerant flow velocity while passing through a plurality of heat exchangers in which the refrigerant flow passage cross-sectional area is gradually reduced, so that the supercooling is efficiently performed. Can proceed. The refrigerant channel cross-sectional area of the second back-side heat exchanger 4-2 is made smaller than the refrigerant channel cross-sectional area of the first back-side heat exchanger 4-1, and the first back-side heat exchanger 4-1 and the first You may make a difference in the refrigerant | coolant flow path cross-sectional area from the stage of 2 back surface side heat exchanger 4-2.

  In the first embodiment, both the back-side heat exchanger and the side-side heat exchanger are configured by a plurality of heat exchangers aligned in the airflow direction, but the present invention is not limited to this. Only one of the back-side heat exchanger and the side-side heat exchanger may be composed of a plurality of heat exchangers, and the other may be a single heat exchanger. Further, “plurality” is not limited to “2”. The configuration may be such that three or more heat exchangers are aligned.

  Next, a second embodiment of the present invention will be described with reference to FIGS. FIG. 4 is a development view of the heat exchanger, and FIG. 5 is a development view of the heat exchanger showing an operation mode different from FIG.

  The second embodiment differs from the first embodiment in the configuration of the refrigerant circuit between the heat exchangers. That is, the refrigerant pipes 28 are not connected to both ends of the lower header pipe 22-2 of the second back side heat exchanger 4-2, but one refrigerant pipe 28 is connected to the center. Yes. The refrigerant pipe 28 is divided into two on the way, and one refrigerant pipe 28 is connected to each end of the upper header pipe 21a-1 of the first side heat exchanger 4a-1. Also with respect to the lower header pipe 22a-1 of the first side heat exchanger 4a-1, not only one refrigerant pipe 29 is connected to both ends but also one refrigerant pipe 29 is connected to the center. Yes.

  During the cooling operation or the defrosting operation, the refrigerant descending to the lower header pipe 22-2 of the second back side heat exchanger 4-2 is one piece from the center of the lower header pipe 22-2 as shown in FIG. The refrigerant flows out through the refrigerant pipe 28 and enters the upper header pipe 21a-1 of the first side heat exchanger 4a-1 from both ends thereof. The refrigerant that descends from the upper header pipe 21a-1 to the lower header pipe 22a-1 flows out from the center of the lower header pipe 22a-1 through one refrigerant pipe 29, and the upper part of the second side heat exchanger 4a-2. The header pipe 21a-2 is entered from the left end.

  During the heating operation, the refrigerant flowing out from the upper header pipe 21a-2 of the second side heat exchanger 4a-2 flows through the first refrigerant pipe 29 as shown in FIG. The lower header pipe 22a-1 is entered from the center. The refrigerant rising from the lower header pipe 22a-1 to the upper header pipe 21a-1 flows out from the both ends of the upper header pipe 21a-1 through one refrigerant pipe 28, and is integrated into one refrigerant pipe 28 from the middle. Then, it enters the lower header pipe 22-2 of the second back side heat exchanger 4-2 from its center.

  By forming the refrigerant circuit as in the second embodiment, the configuration of the refrigerant circuit can be further simplified. Further, the windward side heat exchanger (second back side heat exchanger 4-2, second side side heat exchanger 4a-2) and the leeward side heat exchanger (first back side heat exchanger 4-1, By changing the inflow location of the refrigerant during heating operation (when used as an evaporator) with the first side heat exchanger 4a-1), heat exchange between the windward heat exchanger and the leeward side is performed. The refrigerant diversion state of the vessel can be made different. If the inflow location of the refrigerant is the same, the diversion state will be the same or similar, and the refrigerant will easily dry (the ratio of gas increases), but the inflow locations will be different. Thus, the overlapping of the regions where the refrigerant is liable to dry is less likely to occur (in other words, the degree of overlap is reduced or does not overlap), and the heat exchange efficiency can be improved.

  Next, a third embodiment of the present invention will be described with reference to FIGS. FIG. 6 is a development view of the heat exchanger, and FIG. 7 is a development view of the heat exchanger showing an operation mode different from FIG.

  The third embodiment is characterized in that a gas-liquid separator is arranged in the middle of the refrigerant circuit that passes through the back surface side heat exchanger and the side surface side heat exchanger. In the configuration example shown in FIGS. 6 and 7, the gas-liquid separator 32 is disposed between the first back side heat exchanger 4-1 and the second back side heat exchanger 4-2. That is, the refrigerant pipes 27 </ b> A that come out one by one from both ends of the lower header pipe 2-1 of the first back side heat exchanger 4-1 are integrated into one and connected to one connection port of the gas-liquid separator 32. In addition, the refrigerant pipes 27B that come out one by one from both ends of the upper header pipe 21-2 of the second back side heat exchanger 4-2 are integrated into one and connected to the other connection port of the gas-liquid separator 32.

  During the heating operation, as shown in FIG. 7, the refrigerant leaves the upper header pipe 21-2 of the second back side heat exchanger 4-2 and goes to the lower header pipe 22-1 of the first back side heat exchanger 4-1. The gas is separated by the gas-liquid separator 32 on the way. When used as an evaporator in this way, the gas-liquid two-phase refrigerant that has passed through the side heat exchanger and has been vaporized is separated into gas and liquid, and the liquid passes through the back heat exchanger. By doing so, the flow of refrigerant can be improved and the heat exchange efficiency can be increased.

  The arrangement of the gas-liquid separator 32 between the first back side heat exchanger 4-1 and the second back side heat exchanger 4-2 is one configuration example, and is not limited thereto. It is also possible to arrange in other places. For example, the gas-liquid separator 32 may be disposed in the refrigerant pipe 28 in FIGS.

  Next, a fourth embodiment of the present invention will be described with reference to FIG. FIG. 8 is a development view of the heat exchanger.

  In the fourth embodiment, a device is added to the arrangement of the refrigerant piping led out from the heat exchanger. Although the connection configuration of the refrigerant pipe in FIG. 8 is the same as that of the first embodiment, the connection configuration of the second embodiment or the third embodiment may be used. In FIG. 8, the housing 10a is indicated by a dotted line. 15T is a top plate of the housing 10a, and 15B is a bottom plate of the housing 10a. The first back side heat exchanger 4-1 and the second back side heat exchanger 4-2 are supported on the bottom plate 15B by a plurality of spacers 40 with a predetermined gap between the first back side heat exchanger 4-1 and the second back side heat exchanger 4-2. (In FIG. 8, the spacer 40 is drawn only on the first back side heat exchanger 4-1 side). The first side heat exchanger 4a-1 and the second side heat exchanger 4a-2 are also supported on the bottom plate 15B by a plurality of spacers 40a with a predetermined gap between the first side heat exchanger 4a-1 and the second side heat exchanger 4a-2. (In FIG. 8, the spacer 40a is drawn only on the first side heat exchanger 4a-1 side). When the material metal of the heat exchanger is aluminum, the spacers 40 and 40a are made of, for example, a non-metallic material such as synthetic resin or rubber, or stainless steel.

  The first back side heat exchanger 4-1 and the second back side heat exchanger 4-2 are supported by the spacer 40, and the first side face side heat exchanger 4a-1 and the second side face side heat exchanger 4a-2 are connected. The spacer 40a is supported for the following reason. That is, the 1st back side heat exchanger 4-1, the 2nd back side heat exchanger 4-2, the 1st side face side heat exchanger 4a-1, and the 2nd side face side heat exchanger 4a-2 have good heat conduction. On the other hand, the bottom plate 15B is generally made of a steel plate in terms of cost and strength while being made of a metal such as aluminum. The first back side heat exchanger 4-1, the second back side heat exchanger 4-2, the first side heat exchanger 4a-1, the second side heat exchanger 4a-2, and the bottom plate 15B are directly connected. When they come into contact, they are in contact with dissimilar metals, and galvanic corrosion occurs. In order to prevent this, the first backside heat exchanger 4-1, the second backside heat exchanger 4-2, the first side heat exchanger 4a-1, and the second side heat exchanger 4a-2 Spacers 40 and 40a made of a material that does not cause electrolytic corrosion, such as synthetic resin, non-metallic material such as rubber, or stainless steel, are interposed between the bottom plate 15B.

  The first back side heat exchanger 4-1 and the second back side heat exchanger 4-2 are arranged with a gap 41 between the bottom plate 15B and the first side side heat exchanger 4a-1 by the spacer 40. When the second side heat exchanger 4a-2 is disposed with a gap 41a between the second side heat exchanger 4a-2 and the bottom plate 15B by the spacer 40a, a part of the airflow that flows in from the rear inlet 12 passes through the gap 41, and the side intake A phenomenon occurs in which part of the airflow flowing in from the mouth 12a passes through the gap 41a. When attention is paid to the gap 41, the airflow passing through the gap only exchanges heat with the refrigerant passing through the lower header pipes 22-1 and 22-2, and the first back-side heat exchanger 4-1 and the second It does not contribute much to the heat exchange of the back side heat exchanger 4-2.

  Therefore, the refrigerant pipe through which the refrigerant that has flowed out of the second side heat exchanger 4a-2 during condensation flows, that is, the refrigerant pipe 30, is arranged so as to cross the airflow passing through the gap 41. In FIG. 8, the position of the refrigerant pipe 30 is close to the leeward in the depth direction of the gap 41, and the position where the refrigerant pipe 30 crosses the gap 41 from the viewpoint of looking at the first back-side heat exchanger 4-1 from the front 10 </ b> F side. Is set. As a result, heat exchange is performed between the airflow passing through the gap 41 and the refrigerant passing through the refrigerant pipe 30, and the supercooling of the refrigerant at the time of condensation can be promoted.

  The refrigerant pipe 30 not only crosses the airflow passing through the gap 41, but can also cross the airflow passing through the gap 41a by devising the connection location with the lower header pipe 22a-2. Thereby, the supercooling of the refrigerant is further promoted.

  The positional relationship between the refrigerant pipe 30 and the first back-side heat exchanger 4-1 is first when the first back-side heat exchanger 4-1 is on the windward side and the refrigerant pipe 30 is on the leeward side, and the refrigerant pipe 30 is on the windward side. The rear side heat exchanger 4-1 may be either on the leeward side. The refrigerant pipe 30 may pass through the inside of the gap 41, that is, directly below the first back-side heat exchanger 4-1. Between the first back-side heat exchanger 4-1 and the second back-side heat exchanger 4-2, directly below the second back-side heat exchanger 4-2, and the windward side of the second back-side heat exchanger 4-2 It is also possible to pass the refrigerant pipe 30 in such a position. In any positional relationship, the refrigerant pipe 30 is arranged so as to cross the gap 41, heat exchange is performed between the airflow passing through the gap 41 and the refrigerant passing through the refrigerant pipe 30, and the refrigerant is supercooled during condensation. Can be promoted. The positional relationship between the refrigerant pipe 30, the first side surface side heat exchanger 4a-1, and the second side surface side heat exchanger 4a-2 is the same as this.

  As can be said for any of the first to fourth embodiments described above, by integrating the upper header pipes or the lower header pipes of the adjacent leeward heat exchanger and the windward heat exchanger, The structure can be strengthened.

  FIG. 9 shows a structural example in which the upper header pipe 21-1 of the first back side heat exchanger 4-1 and the upper header pipe 21-2 of the second back side heat exchanger 4-2 are integrated. In this example, the center of a pipe 21 having an oval cross section is partitioned by a vertical partition wall 21P and divided into an upper header pipe 21-1 and an upper header pipe 21-2. The combination of the lower header pipe 22-1 of the first back side heat exchanger 4-1 and the lower header pipe 22-2 of the second back side heat exchanger 4-2, the upper part of the first side heat exchanger 4a-1. Combination of header pipe 21a-1 and upper header pipe 21a-2 of second side heat exchanger 4a-2, and lower header pipe 22a-1 and second side heat of first side heat exchanger 4a-1. Needless to say, the structure of FIG. 9 can also be applied to the combination of the lower header pipe 22a-2 of the exchanger 4a-2.

  Although the embodiments of the present invention have been described above, the scope of the present invention is not limited to these embodiments, and various modifications can be made without departing from the spirit of the invention.

  INDUSTRIAL APPLICABILITY The present invention can be widely used for an outdoor unit of an air conditioner in which heat exchangers are disposed on the back side and the side surface in the casing.

Model horizontal cross section which shows schematic structure of the air conditioner outdoor unit which concerns on 1st Embodiment of this invention. The expanded view of the heat exchanger of the air conditioner outdoor unit which concerns on 1st Embodiment of this invention. The expanded view of the heat exchanger of the air conditioner outdoor unit which concerns on 1st Embodiment of this invention, and shows the operation mode different from FIG. The expanded view of the heat exchanger of the air conditioner outdoor unit which concerns on 2nd Embodiment of this invention. FIG. 3 is a development view of a heat exchanger for an air conditioner outdoor unit according to a second embodiment of the present invention, showing an operation mode different from FIG. 1. The expanded view of the heat exchanger of the air conditioner outdoor unit which concerns on 3rd Embodiment of this invention. FIG. 7 is a development view of a heat exchanger for an air conditioner outdoor unit according to a third embodiment of the present invention, showing an operation mode different from FIG. 1. The expanded view of the heat exchanger of the air conditioner outdoor unit which concerns on 4th Embodiment of this invention. Partial sectional view of a heat exchanger showing an example in which header pipes are integrated Basic configuration diagram of separate air conditioner It is a basic configuration diagram of a separate type air conditioner, and shows a state different from FIG. Model horizontal cross section showing a configuration example of a conventional air conditioner outdoor unit Model horizontal cross-sectional view showing another configuration example of a conventional air conditioner outdoor unit FIG. 13 is an exploded view of a heat exchanger of the outdoor unit of the air conditioner in FIG.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Heat pump cycle 2 Compressor 4-1 1st back surface side heat exchanger 4-2 2nd back surface side heat exchanger 4a-1 1st side surface side heat exchanger 4a-2 2nd side surface side heat exchanger 7 Blower 10 Outdoor Machine 10a Housing 11 Exhaust port 12 Rear intake port 12a Side intake port 15T Top plate 15B Bottom plate 21-1, 21-2, 21a-1, 21a-2 Upper header pipes 22-1, 22-2, 22a-1, 22a-2 Lower header pipe 23-1, 23-2, 23a-1, 23a-2 Flat tube 24-1, 24-2, 24a-1, 24a-2 Corrugated fin 30 Refrigerant piping 41 Gap

Claims (4)

In an outdoor unit of an air conditioner that accommodates a compressor, a heat exchanger, and a blower in a casing having a rectangular shape in a planar shape with a long side on the front and back, and a short side on the left and right sides.
The housing is formed with a rear inlet and a side inlet on the back and one side, and an exhaust on the front, respectively.
Arranged inside the exhaust port is a blower that exhausts the air in the housing through the exhaust port,
The back side heat exchanger and the side side heat exchanger, both of which are parallel flow downflow types, are arranged inside the back side air inlet and the side air inlet,
The back side heat exchanger and the side side heat exchanger each have an upper header pipe and a lower header pipe,
At the time of condensation, the refrigerant passing through the flat tube of the back side heat exchanger is sent to the side heat exchanger through the first refrigerant pipe, and at least one of the back side heat exchanger and the side heat exchanger is airflow. Consists of multiple heat exchangers aligned in the direction,
A refrigerant circuit that flows from the leeward heat exchanger to the windward heat exchanger during condensation is formed between the plurality of heat exchangers, and the lower header pipe and the side surface of the rear heat exchanger The header pipe of either the upper part or the lower part of the side heat exchanger is connected by the first refrigerant pipe ,
The back side heat exchanger is disposed with a predetermined gap between the bottom plate of the housing, and the second refrigerant pipe through which the refrigerant flowing out of the side side heat exchanger during the condensation flows, An outdoor unit for an air conditioner, wherein the outdoor unit is arranged so as to cross an airflow passing through the gap .   In the back-side heat exchanger or the side-side heat exchanger configured by a plurality of heat exchangers aligned in the airflow direction, during condensation, the refrigerant flows into the upper header pipe of the leeward heat exchanger and the heat exchange A refrigerant circuit is configured to flow out from a lower header pipe of a heat exchanger, and then flow into an upper header pipe of an adjacent windward heat exchanger and flow out of the lower header pipe of the heat exchanger. The outdoor unit of the air conditioner described in 1.   The refrigerant circuit passing through the side heat exchanger from the rear heat exchanger has a smaller refrigerant flow path cross-sectional area as the heat exchanger is located downstream of the refrigerant flow during condensation. The outdoor unit of the air conditioner as described in 1 or 2.   4. The air conditioner according to claim 1, wherein a gas-liquid separator is disposed in the middle of a refrigerant circuit that passes through the back-side heat exchanger and the side-side heat exchanger. Outdoor unit.

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