JP2014043985A - Parallel flow type heat exchanger and air conditioner mounted with the same - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a side flow system parallel flow type heat exchanger having a configuration in which condensed water accumulating near the center of a flat tube in the direction of a passing air flow can be discharged quickly.SOLUTION: A parallel flow type heat exchanger 50 includes: header pipes 51 and 52 arranged in parallel at an interval; flat tubes 53 which are arranged in a plural number between the header pipes 51 and 52, and in which a cooling medium path 54 provided inside is communicated with the inside part of the header pipes 51 and 52; and a corrugated fin 55 arranged between the flat tubes 53. At the flat tube 53, a through hole 53c penetrating a flat surface at the position near the center in the direction of air flow passing through a heat exchanger 50 is formed. The through hole 53c is configured by a slit with its longitudinal direction matched with the longitudinal direction of the flat tube 53.

Description

  The present invention relates to a parallel flow heat exchanger and an air conditioner equipped with the heat exchanger.

  A parallel flow type heat in which a plurality of flat tubes are arranged between a plurality of header pipes so that a plurality of refrigerant passages in the flat tubes communicate with the inside of the header pipe, and fins such as corrugated fins are arranged between the flat tubes. Exchangers are widely used in car air conditioners and outdoor air conditioners for buildings.

  Patent Documents 1 to 4 describe side flow type parallel flow heat exchangers including two vertical header pipes and a plurality of horizontal flat tubes connecting the two header pipes. In these heat exchangers, corrugated fins are arranged between the flat tubes.

  When the heat exchanger is used as an evaporator, moisture in the atmosphere is condensed on the surface of the heat exchanger that has become low temperature. When the temperature is low, the condensed water turns into frost on the surface of the heat exchanger. That is, frost formation occurs. Frost can become ice over time. Condensed water, whether it is in a liquid state or transformed into frost or ice, narrows the cross-sectional area of the air flow passage of the heat exchanger and reduces the heat exchange performance of the heat exchanger Let

  Adhesion of condensed water becomes a problem particularly in a side flow type parallel flow heat exchanger. Patent Documents 1 and 2 propose measures for quickly draining condensed water adhering to a side flow parallel flow heat exchanger.

  In the parallel flow heat exchanger described in Patent Document 1, the end of the corrugated fin on the surface on the side where condensed water collects protrudes from the end of the flat tube, and a linear water guide member is formed in the gap formed by the protruding portions. The condensed water that has accumulated at the end of the corrugated fin flows down by a bridge phenomenon that occurs between itself and the water guide member due to its surface tension.

  In the parallel flow type heat exchanger described in Patent Document 2, a drainage guide of a linear member that contacts the corrugated fin is provided on the condensed water collecting side, and the drainage guide is inclined with respect to the flat tube, At least one of both ends reaches the lower end side or side end side of the heat exchanger.

  The structure of the parallel flow type heat exchanger described in Patent Documents 1 and 2 is intended to quickly drain the condensed water from the surface of the condensed water condensing side, and the airflow passing through the heat exchanger The drainage of condensate collected near the center of the flat tube in the direction of is not considered. Regarding the drainage of the condensed water that accumulates near the center of the flat tube in the wind flow direction, the structures described in Patent Documents 3 and 4 can be referred to.

  The heat exchanger described in Patent Document 3 is mounted on an automobile, and a radiator tube and a condenser tube and a corrugated fin extending over both the tubes are integrally joined by brazing. A gap placed between the radiator tube and the condenser tube can be used as a drainage for condensed water.

  The heat exchanger described in Patent Document 4 has a first header pipe separated into a first compartment and a third compartment by a partition extending in the axial direction, and a second interior by a partition extending in the axial direction. A second header pipe separated into a compartment and a fourth compartment, wherein the first compartment of the first header pipe and the second compartment of the second header pipe communicate with each other through a flat tube; The three compartments and the fourth compartment of the second header pipe communicate with each other through a flat tube. A gap between the flat tube that communicates the first compartment and the second compartment and the flat tube that communicates the third compartment and the fourth compartment can be used as a drainage for condensed water.

Japanese Patent No. 4503682 JP 2007-285673 A JP-A-10-263801 JP 2003-121092 A

  Like the heat exchangers described in Patent Documents 3 and 4, two flat tubes are arranged so as to align with the direction of the airflow passing through the heat exchanger, and the gap between the flat tubes is drained of condensed water. In the case of a road, if the condensed water adhering to the surfaces of both flat tubes is to be combined and flowed down at the gap, the gap needs to be made considerably small. However, it is technically difficult to form two holes through the two flat tubes in the header pipe at such a narrow interval. Even if the hole is successfully drilled, brazing the header pipe and the flat tube at the location of the holes so close also has technical difficulties. There is also a possibility that refrigerant may leak from the header pipe and the flat tube due to poor brazing and a gap between the header pipe and the flat tube.

  The present invention has been made in view of the above points, and in a parallel flow type heat exchanger of a side flow method, condensed water that accumulates in the vicinity of the center of the flat tube in the direction of airflow passing through the heat exchanger can be quickly drained. The purpose is to have a structure.

  The parallel flow heat exchanger according to the present invention includes a plurality of header pipes arranged in parallel at intervals, and a plurality of header pipes arranged between the plurality of header pipes, and a refrigerant passage provided therein is provided in the header pipe. A flat tube communicated with the inside and a corrugated fin disposed between the flat tubes, and the flat tube has a flat surface at a position near the center in the direction of the airflow passing through the heat exchanger. It is characterized in that a through-hole penetrating through is formed.

  According to this structure, the condensed water which accumulates in the vicinity of the center of the flat tube in the direction of the airflow passing through the heat exchanger can be quickly drained from the through hole formed in the flat tube. It is also easy to set the size of the through hole so that the condensed water adhering to the surface of the flat tube is formed at the through hole. Moreover, since it is not necessary to form two holes for passing a flat tube side by side in the header pipe, it is easy to process the holes in the header pipe. Brazing between the header pipe and the flat tube does not become difficult, and brazing can be obtained in which the refrigerant does not leak.

  In the parallel flow heat exchanger having the above-described configuration, it is preferable that the through holes are arranged along the longitudinal direction of the flat tube.

  According to this configuration, a drainage channel having a sufficient area for draining the condensed water can be secured.

  In the parallel flow heat exchanger having the above-described configuration, it is preferable that the through hole is formed by a slit whose longitudinal direction coincides with the longitudinal direction of the flat tube.

  According to this configuration, it is possible to easily form a through-hole having an area sufficient for draining condensed water.

  In the parallel flow heat exchanger configured as described above, it is preferable that the slit has a shape in which narrow portions and wide portions alternately appear.

  According to this configuration, when there is little condensate, water is drained from a narrow part, and when there is much condensate, water is drained not only from a narrow part but also from a wide part. It can drain quickly.

  In the parallel flow heat exchanger configured as described above, it is preferable that a valley-shaped portion is formed on the flat surface of the flat tube, and the through hole is formed at the bottom of the valley-shaped portion.

  According to this configuration, the condensed water is likely to collect in the valley portion, and thus can be drained efficiently.

  In the parallel flow heat exchanger configured as described above, it is preferable that a water guide member that penetrates the through hole in the vertical direction is disposed.

  According to this structure, since the condensed water flows down through the water guide member, drainage efficiency is improved.

  In the parallel flow heat exchanger configured as described above, it is preferable that a through hole is formed in the corrugated fin at a position aligned with the through hole in the vertical direction.

  According to this configuration, since the condensed water dripping from the through hole of the flat tube is drawn into the through hole of the corrugated fin, the drainage efficiency is improved.

  Further, the present invention is an air conditioner in which the parallel flow heat exchanger having the above-described configuration is mounted on an outdoor unit or an indoor unit.

  According to this configuration, it is possible to provide a high-performance air conditioner in which the air permeability of the outdoor unit or the heat exchanger of the indoor unit is less impaired by the condensed water.

  According to the present invention, the condensed water that accumulates in the vicinity of the center of the flat tube in the direction of the airflow passing through the heat exchanger can be quickly drained from the through-hole formed in the flat tube, so the flow direction of the flat tube wind Even if the width at is wide, it is possible to prevent the condensed water from obstructing ventilation. It is also easy to set the size of the through hole so that the condensed water is coalesced at the through hole. In addition, since it is not necessary to form two holes for passing the flat tube in the direction of the airflow in the header pipe, it is easy to drill the header pipe, and for the brazing of the header pipe and the flat tube, Can be easily obtained.

It is a schematic block diagram of the air conditioner carrying the parallel flow type heat exchanger which concerns on this invention, and shows the state at the time of air_conditionaing | cooling operation. It is a schematic block diagram of the air conditioner carrying the parallel flow type heat exchanger which concerns on this invention, and shows the state at the time of heating operation. It is a horizontal sectional view which shows schematic structure of the outdoor unit of the air conditioner of FIG. It is a control block diagram of the air conditioner of FIG. It is a schematic block diagram of a parallel flow type heat exchanger. It is sectional drawing along the VI-VI line of FIG. It is a partial expanded sectional view of the parallel flow type heat exchanger concerning a 1st embodiment of the present invention. It is a partial enlarged plan view of the parallel flow type heat exchanger concerning a 1st embodiment of the present invention. It is a partial expanded sectional view of the parallel flow type heat exchanger which concerns on 2nd Embodiment of this invention. It is a partial enlarged plan view of a parallel flow type heat exchanger concerning a 3rd embodiment of the present invention. It is a partial enlarged plan view of the parallel flow type heat exchanger concerning a 4th embodiment of the present invention. It is a partial expanded sectional view of the parallel flow type heat exchanger which concerns on 5th Embodiment of this invention. It is a partial enlarged plan view of a parallel flow type heat exchanger concerning a 5th embodiment of the present invention. It is a partial expanded sectional view of the parallel flow type heat exchanger which concerns on 6th Embodiment of this invention. It is a partial enlarged plan view of a parallel flow type heat exchanger concerning a 6th embodiment of the present invention.

  Based on FIGS. 1-6, the air conditioner 1 in which the parallel flow type heat exchanger which concerns on this invention is mounted is demonstrated.

  The basic structure of a side flow parallel flow heat exchanger is shown in FIG. In FIG. 5, the upper side of the paper is the upper side of the heat exchanger, and the lower side of the paper is the lower side of the heat exchanger. The parallel flow heat exchanger 50 includes two vertical header pipes 51 and 52 and a plurality of horizontal flat tubes 53 disposed therebetween. The header pipes 51 and 52 are arranged in parallel at intervals in the horizontal direction, and the flat tubes 53 are arranged at a predetermined pitch in the vertical direction. Since the heat exchanger 50 is installed at various angles according to design requirements at the stage of actually mounting on equipment, the “vertical direction” and “horizontal direction” in this specification should not be interpreted strictly. It should be understood as a mere measure of direction.

  The flat tube 53 is an elongated molded product obtained by extruding a metal, and as shown in FIG. 6, a refrigerant passage 54 through which a refrigerant flows is formed. Since the flat tube 53 is arranged so that the extrusion molding direction, which is the longitudinal direction, is horizontal, the refrigerant flow direction of the refrigerant passage 54 is also horizontal. A plurality of refrigerant passages 44 having the same cross-sectional shape and the same cross-sectional area are arranged in the left-right direction of FIG. Each refrigerant passage 54 communicates with the header pipes 51 and 52. FIG. 6 shows a cross section of the flat tube 53 in the first embodiment of the parallel flow heat exchanger 50 described later.

  Corrugated fins 55 are attached to the flat surface of the flat tube 53. Of the corrugated fins 55 arranged vertically, side plates 56 are arranged outside the uppermost and lowermost ones. In order to increase the heat exchange efficiency, the corrugated fin 55 is formed with a plurality of slits 55a perpendicular to the airflow passage direction.

  The header pipes 51 and 52, the flat tubes 53, the corrugated fins 55, and the side plates 56 are all made of aluminum or an aluminum alloy. The flat tubes 53 are for the header pipes 51 and 52, and the corrugated fins 55 are for the flat tubes 53. The side plates 56 are fixed to the corrugated fins 55 by brazing or welding, respectively.

  The inside of the header pipe 51 is partitioned into two sections S1 and S2 by one partition portion P1. The partition part P1 divides the plurality of flat tubes 53 into a plurality of flat tube groups. A flat tube group consisting of 12 out of a total of 24 flat tubes 53 is connected to the section S1, and a flat tube group consisting of 12 flat tubes 53 is connected to the section S2.

  The inside of the header pipe 52 is partitioned into three sections S3, S4, and S5 by two partition portions P2 and P3. The partition parts P2 and P3 divide the plurality of flat tubes 53 into a plurality of flat tube groups. A flat tube group consisting of 4 of the 24 flat tubes 53 in total is connected to the section S3, a flat tube group consisting of 15 flat tubes 53 is connected to the section S4, and 5 pieces are connected to the section S5. A flat tube group consisting of the flat tubes 53 is connected.

  The total number of the flat tubes 53 described above, the number of partition portions inside each header pipe and the number of partitions partitioned thereby, and the number of flat tubes 53 for each flat tube group divided by the partition portions are merely examples. Yes, it does not limit the invention.

  A refrigerant inlet / outlet pipe 57 is connected to the section S3. A refrigerant inlet / outlet pipe 58 is connected to the section S5.

  The function of the heat exchanger 50 is as follows. When the heat exchanger 50 is used as a condenser, the refrigerant is supplied to the compartment S3 through the refrigerant inlet / outlet pipe 57. The refrigerant that has entered the compartment S3 travels through the four flat tubes 53 connecting the compartment S3 and the compartment S1 to the compartment S1. The flat tube group formed by the four flat tubes 53 constitutes the refrigerant path A. The refrigerant path A is symbolized by a block arrow. Other refrigerant paths are also symbolized by block arrows.

  The refrigerant that has entered the section S1 is turned back there, and travels to the section S4 through the eight flat tubes 53 that connect the sections S1 and S4. The flat tube group formed by the eight flat tubes 53 constitutes the refrigerant path B.

  The refrigerant that has entered the section S4 is turned back there, and travels to the section S2 through the seven flat tubes 53 that connect the sections S4 and S2. The flat tube group formed by the seven flat tubes 53 constitutes the refrigerant path C.

  The refrigerant that has entered the compartment S2 turns back there, and travels to the compartment S5 through the five flat tubes 53 that connect the compartment S2 and the compartment S5. The flat tube group formed by the five flat tubes 53 constitutes the refrigerant path D. The refrigerant entering the compartment S5 flows out from the refrigerant inlet / outlet pipe 58.

  When the heat exchanger 50 is used as an evaporator, the refrigerant is supplied to the compartment S5 through the refrigerant inlet / outlet pipe 58. Subsequent refrigerant flows follow the refrigerant path when the heat exchanger 50 is used as a condenser. That is, the refrigerant enters the section S <b> 1 through the route of the refrigerant path D → refrigerant path C → refrigerant path B → refrigerant path A and flows out from the refrigerant inlet / outlet pipe 57.

  A schematic configuration of a separate air conditioner 1 using the heat exchanger 50 as a component of a heat pump cycle is shown in FIG. The air conditioner 1 includes an outdoor unit 10 and an indoor unit 30.

  The outdoor unit 10 houses a compressor 12, a switching valve 13, an outdoor heat exchanger 14, an expansion valve 15, an outdoor blower 16, and the like in a housing 11 made of sheet metal parts and synthetic resin parts. doing. The switching valve 13 is a four-way valve. A heat exchanger 50 is used as the outdoor heat exchanger 14. As the expansion valve 15, a valve whose opening degree can be controlled is used. The outdoor blower 16 is a combination of a propeller fan and a motor.

  The outdoor unit 10 is connected to the indoor unit 30 through two refrigerant pipes 17 and 18. Liquid refrigerant flows through the refrigerant pipe 17 during the cooling operation, and a pipe that is thinner than the refrigerant pipe 18 is used. Therefore, the refrigerant pipe 17 may be referred to as “liquid pipe”, “narrow pipe”, or the like. A gas refrigerant flows through the refrigerant pipe 18 during the cooling operation, and a pipe that is thicker than the refrigerant pipe 17 is used. Therefore, the refrigerant pipe 18 may be referred to as “gas pipe”, “thick pipe”, or the like. For example, HFC R410A or R32 is used as the refrigerant.

  In the refrigerant pipe inside the outdoor unit 10, a two-way valve 19 is provided in the refrigerant pipe connected to the refrigerant pipe 17, and a three-way valve 20 is provided in the refrigerant pipe connected to the refrigerant pipe 18. The two-way valve 19 and the three-way valve 20 are closed when the refrigerant pipes 17 and 18 are removed from the outdoor unit 10 to prevent the refrigerant from leaking from the outdoor unit 10 to the outside. When it is necessary to recover the refrigerant from the outdoor unit 10 or the entire refrigeration cycle including the indoor unit 30, the recovery is performed through the three-way valve 20.

  FIG. 3 shows the structure of the outdoor unit 10 more substantively. The casing 11 of the outdoor unit 10 is made of sheet metal, and is drawn in a substantially rectangular shape in FIG. The casing 11 has a long side as a front surface 11F and a back surface 11B, and a short side as a left side surface 11L and a right side surface 11R. An exhaust port 11E is formed on the front surface 11F, a back surface intake port 11BS is formed on the back surface 11B, and a side surface intake port 11LS is formed on the left side surface 11L. The exhaust port 11E is composed of a set of a plurality of horizontal slit-shaped openings, and the back surface intake port 11BS and the side surface intake ports 11LS are composed of lattice-shaped openings. A top plate and a bottom plate (not shown in FIG. 3) are added to the four sheet metal members of the front surface 11F, the back surface 11B, the left side surface 11L, and the right side surface 11R to form the hexahedron-shaped casing 11.

  There is no limitation that one part constitutes each of the six surfaces of the housing 11. Some surfaces are composed of a single component, while others are composed of a plurality of components.

  Inside the housing 11, a planar L-shaped outdoor heat exchanger 14 is arranged immediately inside the rear intake port 11BS and the side intake port 11LS. In order to force heat exchange between the outdoor heat exchanger 14 and the outdoor air, an outdoor blower 16 is disposed between the outdoor heat exchanger 14 and the exhaust port 11E. The outdoor blower 16 includes a combination of a propeller fan 16a and a motor 16b. In order to improve the blowing efficiency, a bell mouth 11BM surrounding the propeller fan 16a is attached to the inner surface of the front surface 11F of the housing 11. The space inside the right side surface 11R of the casing 11 is isolated by a partition wall 11P from the air flow flowing from the rear intake port 11BS to the exhaust port 11E, and the compressor 12 is accommodated in this space.

  The indoor unit 30 houses an indoor heat exchanger 32, an indoor blower 33, and the like in a housing 31 formed of synthetic resin parts. The indoor heat exchanger 32 is a combination of three heat exchangers 32 </ b> A, 32 </ b> B, and 32 </ b> C like a roof that covers the indoor blower 33. The indoor blower 33 is a combination of a motor and a cross flow fan.

  In order to control the operation of the air conditioner 1, it is indispensable to know the temperature of each place. For this purpose, temperature detectors are arranged in the outdoor unit 10 and the indoor unit 30. In the outdoor unit 10, a temperature detector 21 is disposed in the outdoor heat exchanger 14, and a temperature detector 22 is disposed in the discharge pipe 12 a serving as the discharge unit of the compressor 12, and the suction serving as the suction unit of the compressor 12. A temperature detector 23 is disposed in the pipe 12 b, a temperature detector 24 is disposed in the refrigerant pipe between the expansion valve 15 and the two-way valve 19, and a temperature detector for measuring the outside air temperature at a predetermined location inside the housing 11. 25 is arranged. In the indoor unit 30, a temperature detector 34 is disposed in the indoor heat exchanger 32. Each of the temperature detectors 21, 22, 23, 24, 25, and 34 is formed of a thermistor.

  The control unit 40 shown in FIG. 4 controls the overall control of the air conditioner 1. The control unit 40 performs control so that the room temperature reaches a target value set by the user.

  The control unit 40 issues operation commands to the compressor 12, the switching valve 13, the expansion valve 15, the outdoor fan 16, and the indoor fan 33. The control unit 40 receives output signals of the detected temperatures from the temperature detectors 21 to 25 and the temperature detector 34. While referring to the output signals from the temperature detectors 21 to 25 and the temperature detector 34, the control unit 40 issues an operation command to the compressor 12, the outdoor fan 16, and the indoor fan 33, and the expansion valve 13 and the expansion valve 13 are expanded. A command for switching the state is issued to the valve 15.

  FIG. 1 shows a state in which the air conditioner 1 is performing a cooling operation or a defrosting operation. At this time, the compressor 12 circulates the refrigerant in a cooling mode, that is, a circulation mode in which the refrigerant discharged from the compressor 12 first enters the outdoor heat exchanger 14.

  The high-temperature and high-pressure refrigerant discharged from the compressor 12 enters the outdoor heat exchanger 14 where heat exchange with outdoor air is performed. The refrigerant dissipates heat to the outdoor air and condenses. The refrigerant that is condensed to become liquid enters the expansion valve 15 from the outdoor heat exchanger 14 and is decompressed there. The decompressed refrigerant is sent to the indoor heat exchanger 32, expands to a low temperature and low pressure, and lowers the surface temperature of the indoor heat exchanger 32. The indoor side heat exchanger 32 whose surface temperature has been lowered absorbs heat from the room air, thereby cooling the room air. After the heat absorption, the low-temperature gaseous refrigerant returns to the compressor 12. The air flow generated by the outdoor blower 16 promotes heat radiation from the outdoor heat exchanger 14, and the air flow generated by the indoor blower 33 promotes heat absorption of the indoor heat exchanger 32.

  FIG. 2 shows a state where the air conditioner 1 is performing a heating operation. At this time, the switching valve 13 is switched to reverse the refrigerant flow during the cooling operation. The compressor 12 circulates the refrigerant in a circulation mode during heating, that is, in a circulation mode in which the refrigerant discharged from the compressor 12 first enters the indoor heat exchanger 32.

  The high-temperature and high-pressure refrigerant discharged from the compressor 12 enters the indoor heat exchanger 32 where heat exchange with the indoor air is performed. The refrigerant dissipates heat to the room air, and the room air is warmed. The refrigerant that has dissipated heat and has become liquid by condensing enters the expansion valve 15 from the indoor heat exchanger 32 and is decompressed there. The decompressed refrigerant is sent to the outdoor heat exchanger 14 and expands to a low temperature and low pressure, thereby lowering the surface temperature of the outdoor heat exchanger 14. The outdoor heat exchanger 14 whose surface temperature has dropped absorbs heat from outdoor air. After the heat absorption, the low-temperature gaseous refrigerant returns to the compressor 12. The air flow generated by the indoor fan 33 promotes heat dissipation from the indoor heat exchanger 32, and the air flow generated by the outdoor fan 16 promotes heat absorption by the outdoor heat exchanger 14.

  As the outdoor heat exchanger 14 or any or all of the three heat exchangers 32A, 32B, 32C constituting the indoor heat exchanger 32, heat exchange that is a side flow parallel flow type heat exchanger A vessel 50 can be mounted. Next, the characteristic structure of the heat exchanger 50 will be described with reference to FIGS.

<First Embodiment>
7 and 8 show the structure of the parallel flow heat exchanger 50 according to the first embodiment of the present invention.
In FIG. 7, the left side of the figure is the windward side of the airflow passing through the heat exchanger 50, and the right side of the figure is the leeward side of the airflow. As shown in FIG. 7, flanges 53 a are formed on the windward and leeward edges of the flat tube 53. The flange 53a is for increasing the area of the heat transfer surface of the flat tube 53.

  A location near the center of the flat tube 53 in the direction of the airflow passing through the heat exchanger 50 is a thin portion 53b where the refrigerant passage 54 does not exist. A through hole 53c that penetrates the flat surface of the flat tube 53 is formed in the thin wall portion 53b.

  As shown in FIG. 8, the through-hole 53 c is configured by a slit in which the longitudinal direction of the flat tube 53 coincides with its longitudinal direction. The slits do not exist as a single slit whose both ends approach the header pipes 51 and 52 but exist as a plurality of slits arranged in a line along the longitudinal direction of the flat tube 53. . The width of the slit should be such that condensate is likely to coalesce. The width is preferably 5 mm or less. About 1 mm is optimal.

  In the parallel flow type heat exchanger 50 according to the first embodiment, the through hole 53c that penetrates the flat surface of the flat tube 53 is formed in the central portion of the flat tube 53 in the direction of the passing air flow. Condensed water that accumulates in the vicinity can be quickly drained from the through hole 53c. It is also easy to set the size of the through hole 53c so that the condensed water adhering to the surface of the flat tube 53 is generated at the through hole 53c. Further, since it is not necessary to form two holes for passing the flat tube 53 in the header pipes 51 and 52 side by side in the airflow passage direction, the header pipes 51 and 52 can be easily drilled. It is easy to braze the header pipes 51 and 52 and the flat tube 53, and brazing can be obtained in which refrigerant does not leak.

  Since the through holes 53c are arranged in a line along the longitudinal direction of the flat tube 53, a drainage channel having a sufficient area for draining the condensed water can be secured. Each of the through holes 53c arranged in a line along the longitudinal direction of the flat tube 53 is a slit in which the longitudinal direction of the flat tube 53 coincides with the longitudinal direction of the flat tube 53, and therefore has a sufficient area for draining condensed water. The through hole 53c can be easily formed.

Second Embodiment
FIG. 9 shows the structure of a parallel flow heat exchanger 50 according to the second embodiment of the present invention. Here, the thin portion 53b is a valley-shaped portion 53d having an inverted trapezoidal cross section, and a through hole 53c is formed at the bottom thereof. Since the condensed water tends to collect in the valley portion 53d, it can be drained efficiently. The cross-sectional shape of the valley portion 53d is not limited to the shape shown in FIG. It may be V-shaped or U-shaped.

<Third Embodiment>
The structure of the parallel flow type heat exchanger 50 according to the third embodiment of the present invention is shown in FIG. Here, slit-shaped through holes 53c are formed in the thin-walled portion 53b so as to be arranged in two rows. In this way, a drainage channel having a sufficient area for draining the condensed water can be obtained with certainty. There may be three or more rows of through holes 53c.

<Fourth embodiment>
FIG. 11 shows the structure of a parallel flow heat exchanger 50 according to the fourth embodiment of the present invention. The slit-shaped through-holes 53c are formed in the thin wall portion 53b so as to be arranged in a row, but the slits are alternately arranged between narrow and wide portions. The shape that appears in. In this way, when there is little condensate, it drains from a narrow part, and when there is a lot of condensate, it drains not only from a narrow part but also from a wide part. Regardless, it can drain quickly.

<Fifth Embodiment>
The structure of a parallel flow heat exchanger 50 according to the fifth embodiment of the present invention is shown in FIGS. In the parallel flow type heat exchanger 50 of the fifth embodiment, the structure of the flat tube 53 is the same as that of the first embodiment, but the structure of the corrugated fin 55 is different from that of the first embodiment. That is, a through hole is formed in the corrugated fin 55 at a position aligned with the through hole 53 c of the flat tube 53 in the vertical direction. The through hole is constituted by a through hole 55 b formed in each crest portion of the corrugated fin 55 and a through hole 55 c formed in a trough portion. Each of the through holes 55b and 55c is configured by a slit in which the longitudinal direction of the flat tube 53 coincides with its longitudinal direction.

  In the parallel flow heat exchanger 50 according to the fifth embodiment, the condensed water dripping from the through hole 53 c of the flat tube 53 is drawn into the through hole 55 b above the corrugated fin 55. The condensed water transferred to the corrugated fins 55 from the upper through hole 55b moves to the flat tube 53 below from the lower through hole 55c. In this way, the condensed water is drawn in a chain from the upper corrugated fins 55 to the lower corrugated fins 55, thereby improving drainage efficiency.

<Sixth Embodiment>
14 and 15 show the structure of a parallel flow heat exchanger 50 according to the sixth embodiment of the present invention. The cross-sectional shape of the flat tube 53 is the same as that of the second embodiment. The shape of the through-hole 53c is the same as that of the fourth embodiment, and is a slit shape in which narrow portions and wide portions appear alternately. The through holes 55b and 55c formed in the corrugated fin 55 have the same slit shape as that of the fifth embodiment, but a wide portion is formed at the center of the narrow portion.

  The interval between the wide portions in the through-hole 53c is matched with the interval between the peaks and valleys of the corrugated fins 55. Then, the wide portion of the through hole 55b of the corrugated fin 55 is aligned with the wide portion of the through hole 53c of the upper and lower flat tubes 53 in the vertical direction. The wide portion of the through hole 55c of the corrugated fin 55 is also aligned in the vertical direction with the wide portion of the through hole 53c of the upper and lower flat tubes 53. As for the wide part of the through hole 53c, the one aligned with the wide part of the through hole 55b and the one aligned with the wide part of the through hole 55c are arranged every other line.

  When the heat exchanger 50 is viewed from above, the wide portion of the through hole 53c of each flat tube 53 and the wide portion of the through hole 55b of each corrugated fin 55 are aligned from top to bottom. A linear water guide member 60 penetrates the portion in the vertical direction. The wide portion of the through hole 53c of each flat tube 53 and the wide portion of the through hole 55c of each corrugated fin 55 are also aligned from top to bottom. A linear water guide member 60 penetrates the portion in the vertical direction.

  The water guide member 60 may be configured to contact the flat tube 53 and the corrugated fin 55, or may be configured to be held with a gap between the flat tube 53 and the corrugated fin 55. When holding with a gap, the width of the gap is 5 mm or less, preferably about 1 mm. The water guide member 60 may be a metal or synthetic resin rod, may be a stranded wire thereof, or may be a synthetic fiber string.

  By providing the water guide member 60 penetrating the heat exchanger 50 in the vertical direction, the condensed water is quickly drained to the outside of the heat exchanger 50 through the water guide member 60. Thereby, drainage efficiency improves.

  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.

  The present invention is widely applicable to a parallel flow heat exchanger and an air conditioner equipped with the heat exchanger.

DESCRIPTION OF SYMBOLS 1 Air conditioner 10 Outdoor unit 14 Outdoor unit side heat exchanger 11 Case 30 Indoor unit 31 Case 32 Indoor unit side heat exchanger 50 Parallel flow type heat exchanger 51, 52 Header pipe 53 Flat tube 53b Thin part 53c Through Hole 53d Valley-like part 55 Corrugated fin 55b, 55c Through hole 60 Water guide member

Claims (8)

A plurality of header pipes arranged in parallel at intervals, a plurality of flat tubes arranged between the plurality of header pipes and having refrigerant passages provided therein communicated with the inside of the header pipes, and the flat tubes In the parallel flow type heat exchanger of the side flow type provided with corrugated fins arranged between each other,
The parallel flow heat exchanger is characterized in that the flat tube has a through-hole penetrating the flat surface at a position near the center in the direction of the airflow passing through the heat exchanger.   The parallel flow heat exchanger according to claim 1, wherein the through holes are arranged along the longitudinal direction of the flat tube.   The parallel flow heat exchanger according to claim 2, wherein the through hole is configured by a slit whose longitudinal direction coincides with the longitudinal direction of the flat tube.   The parallel flow heat exchanger according to claim 3, wherein the slit has a shape in which a narrow portion and a wide portion appear alternately.   The parallel flow heat exchange according to any one of claims 1 to 4, wherein a valley-like portion is formed on a flat surface of the flat tube, and the through-hole is formed at a bottom of the valley-like portion. vessel.   The parallel flow type heat exchanger according to any one of claims 1 to 5, wherein a water guide member that penetrates the through hole in a vertical direction is disposed.   The parallel flow heat exchanger according to any one of claims 1 to 6, wherein a through hole is formed in the corrugated fin at a position aligned with the through hole in a vertical direction.   An air conditioner in which the parallel flow heat exchanger according to any one of claims 1 to 7 is mounted on an outdoor unit or an indoor unit.

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