JP2018009743A - Heat exchanger - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a heat exchanger capable of improving drain performance of condensate water generating in a fin, and capable of reducing manufacturing cost.SOLUTION: A heat exchanger includes: two refrigerant headers; a plurality of flat heat transfer pipes for connecting these two refrigerant headers and arrayed vertically; and a fin disposed between the flat heat transfer pipes. Also, at a portion on the side coming into contact with the flat heat transfer pipe at a lower part of the fin, a cutout part is provided for flowing condensate water. The cutout part is formed at a portion of a lower part on a downstream end in the fin or at a portion of a lower part on the central part side, with respect to an airflow.SELECTED DRAWING: Figure 4

Description

  The present invention relates to a heat exchanger used for an air conditioner or the like, and more particularly to a microchannel heat exchanger using corrugated fins.

  As a heat exchanger used in a refrigeration cycle apparatus such as an air conditioner, there is a microchannel type heat exchanger called a parallel flow type. This heat exchanger usually includes two refrigerant headers (collection tubes) and a plurality of flat heat transfer tubes arranged in the vertical direction between the two refrigerant headers, and one end of each flat heat transfer tube is one of the above-mentioned ones. The other end of the refrigerant header is connected to the other refrigerant header. Further, corrugated fins are usually arranged between the flat heat transfer tubes.

  As this kind of circulation technology, for example, there is one described in JP 2014-47975 A (Patent Document 1).

JP 2014-47975 A

  A conventional microchannel type heat exchanger used in an air conditioner or the like has a plurality of flat heat transfer tubes arranged between two refrigerant headers as shown in, for example, Patent Document 1 above, The refrigerant passage inside the flat heat transfer tube communicates with the inside of the refrigerant header, and corrugated fins are arranged between the flat heat transfer tubes. That is, the conventional heat exchanger is composed of a pair of pipe-like refrigerant headers, flat heat transfer tubes, corrugated fins formed by being bent in a waveform, and the like.

  A plurality of the flat heat transfer tubes are horizontally arranged between the two refrigerant headers arranged in parallel at a predetermined interval in the vertical direction, and both ends communicate with the two refrigerant headers. The corrugated fins are arranged between the flat heat transfer tubes so that the corrugated top (bent portion) is in contact with the flat heat transfer tubes.

  Air is blown to the heat exchanger by a fan and flows between the corrugated fins. On the other hand, the refrigerant flowing through the refrigeration cycle flows from the refrigerant header on the refrigerant inlet side, flows through the flow path inside the flat heat transfer tube, flows to the refrigerant header on the refrigerant outlet side, and flows out to the refrigeration cycle. At this time, the refrigerant flowing inside the flat heat transfer tube and the external air exchange heat through the corrugated fins.

  In the heat exchanger described above, since the flat heat transfer tubes are installed in a horizontal state, the corrugated fins installed between the flat heat transfer tubes are also in a horizontal state. For this reason, when a heat exchanger is used as an evaporator, condensed water may be generated on the surface of the corrugated fins, and when this condensed water accumulates in the lower part of the corrugated fins, The pressure loss increases and the air volume decreases, or the effective area where the fins come into contact with the air decreases, which causes a decrease in the performance of the air conditioner or the like. Further, an increase in pressure loss in the air flow path between the corrugated fins increases the power consumption of the fan, causing a reduction in efficiency. Furthermore, if the condensed water accumulates between the fins, the condensed water may be blown out together with the air from the outlet of the heat exchanger on the flow of air blown from the fan.

For this reason, it is desirable to quickly move the condensed water generated in the heat exchanger from the fin surface to the drain pan below the heat exchanger with the help of gravity.
In the thing of the said patent document 1, the width | variety of a corrugated fin is formed larger than the width | variety of a flat heat exchanger tube, a corrugated fin is cut out in the shape of a flat heat exchanger tube, and a corrugated fin is partially protruded from the flat heat exchanger tube. Further, the protruding end portion is cut open so that the upper and lower corrugated fins are brought into contact with each other, thereby allowing the condensed water to flow downward, thereby improving the drainage performance.

  However, since it is necessary to make the width of the corrugated fin larger than the width of the flat heat transfer tube, a large amount of material is required, and the manufacturing process is complicated, resulting in an increase in manufacturing cost.

  The objective of this invention is obtaining the heat exchanger which can improve the drainage performance of the condensed water which generate | occur | produces with a fin, and can also reduce manufacturing cost.

  In order to achieve the above object, the present invention is provided between two refrigerant headers, a plurality of flat heat transfer tubes that connect the two refrigerant headers and are arranged in the vertical direction, and the flat heat transfer tubes. In the heat exchanger provided with fins, a notch for flowing condensed water is provided in a portion of the lower part of the fin that is in contact with the flat heat transfer tube.

  ADVANTAGE OF THE INVENTION According to this invention, there exists an effect which can obtain the heat exchanger which can improve the drainage performance of the condensed water which generate | occur | produces with a fin, and can also reduce manufacturing cost.

It is a front view which shows an example of the microchannel type heat exchanger using a corrugated fin. It is a principal part expanded horizontal sectional view equivalent to the cross-sectional shape of the principal part of FIG. 1, and is a figure explaining the structure of the flat heat exchanger tube and the corrugated fin in the general microchannel type heat exchanger. It is the enlarged view which looked at the heat exchanger shown in FIG. 2 from the downstream of an air flow, and is the principal part enlarged front view explaining the state of the condensed water in a general microchannel type heat exchanger. It is an expanded horizontal sectional view of the principal part of FIG. 1, It is a figure explaining the structure of the flat heat exchanger tube and corrugated fin to which Example 1 of this invention is applied. 5 is an enlarged view of the heat exchanger shown in FIG. 4 as viewed from the downstream side of the air flow, and is an enlarged front view of a main part for explaining the state of condensed water in the microchannel heat exchanger of Example 1. FIG. It is a figure explaining Example 2 of the heat exchanger of this invention, and is a figure equivalent to FIG. It is a figure explaining Example 3 of the heat exchanger of this invention, and is a figure equivalent to FIG. It is a figure explaining Example 4 of the heat exchanger of this invention, and is a figure equivalent to FIG. It is a figure explaining Example 5 of the heat exchanger of this invention, and is a figure equivalent to FIG.

  Hereinafter, specific examples of the heat exchanger of the present invention will be described with reference to the drawings. In each figure, the part which attached | subjected the same code | symbol has shown the part which is the same or it corresponds.

A heat exchanger according to a first embodiment of the present invention will be described with reference to FIGS. First, the overall configuration of a microchannel heat exchanger to which the first embodiment is applied will be described with reference to FIG.
FIG. 1 is a front view showing an example of a microchannel type heat exchanger using corrugated fins. This heat exchanger is used in, for example, an air conditioner and the like, and external air such as outdoor air and the inside of the heat exchanger. It is a heat exchanger which performs heat exchange with the refrigerant | coolant which flows.

  As shown in FIG. 1, the heat exchanger 1 connects two refrigerant headers 100, 101 and a plurality of flat plates connected between the two refrigerant headers 100, 101 and arranged substantially horizontally in parallel in the vertical direction. A heat transfer tube 102 and a corrugated fin (hereinafter also simply referred to as a fin) 103 disposed so as to be in contact with the flat heat transfer tube 102 between the flat heat transfer tube 102 and the like.

  Air is blown by a fan (not shown) from the back side to the front side of the heat exchanger 1 and flows between the corrugated fins 103. On the other hand, the refrigerant flowing through the refrigeration cycle flows from, for example, the refrigerant header 100 on the refrigerant inlet side, flows through the refrigerant flow path formed inside the flat heat transfer tube 102, and enters the refrigerant outlet side, for example, the refrigerant header 101. And flows out to the refrigeration cycle.

  When the heat exchanger 1 is an outdoor heat exchanger and is used as a condenser, when the refrigerant flows in the flat heat transfer tube 102, the corrugated fins 103 come into contact with the flat heat transfer tube 102. The refrigerant exchanges heat with the outdoor air, and the refrigerant dissipates heat into the outdoor air and condenses. The condensed liquid refrigerant is decompressed and expanded and allowed to flow to the indoor heat exchanger, thereby cooling the indoor air and performing a cooling operation or the like.

  Further, when the heat exchanger 1 is an outdoor heat exchanger and is used as an evaporator, the corrugated fin 103 that contacts the flat heat transfer tube 102 when the refrigerant flows in the flat heat transfer tube 102. The refrigerant exchanges heat with the outdoor air, and the refrigerant removes heat from the air and evaporates. The evaporated gas refrigerant is sent to the compressor and is compressed to become a high-temperature and high-pressure gas refrigerant. By flowing this gas refrigerant through the indoor heat exchanger, the indoor air can be heated and a heating operation or the like can be performed.

  The configuration of flat heat transfer tubes and corrugated fins in a general microchannel heat exchanger will be described with reference to FIG. FIG. 2 is an enlarged cross-sectional view of a main part corresponding to, for example, a cross-sectional shape near the center in the heat exchanger shown in FIG.

  As shown in FIG. 2, a general microchannel heat exchanger 1 includes a plurality of refrigerant flow paths 104 inside a flat heat transfer tube 102, and the refrigerant flow paths are refrigerant headers 100 and 101. (See FIG. 1). Further, a corrugated fin 103 is disposed between the upper and lower flat heat transfer tubes 102 so as to come into contact therewith.

  Air flows from the right (back side) to the left (front side) as indicated by the arrow 106. The refrigerant in the refrigerant flow path 104 exchanges heat with air via the flat heat transfer tubes 102 and the corrugated fins 103. Reference numeral 105 denotes a slit formed in the corrugated fin 103 to promote heat transfer.

  When the microchannel heat exchanger 1 shown in FIG. 2 is used as an evaporator, the air is cooled on the surface of the corrugated fins 103. When the air is cooled, the amount of saturated water vapor is decreased, so that moisture in the air may be condensed to generate condensed water. Condensed water is generated on the surface of the corrugated fins 103 and is pulled by the air flow 106 and is likely to gather relatively downstream of the air flow, that is, to the left in FIG.

  FIG. 3 is an enlarged view of the heat exchanger shown in FIG. 2 as viewed from the downstream side of the air flow, and is an enlarged front view of a main part for explaining the state of condensed water in a general microchannel heat exchanger. As shown in FIG. 3, corrugated fins 103 are disposed between the upper and lower flat heat transfer tubes 102, and the corrugated fins 103 are bent in a U-shape so that mountain folds and valley folds are repeated alternately. Condensed water 201a, 201b is accumulated in the lower part between one fold and one fold.

Condensed water 201a accumulated in the lower part of the corrugated fin 103 that is a mountain fold (lower lower part of the fin) is easy to flow down and be discharged because the lower part is open.
However, the condensed water 201b accumulated in the lower part of the valley part (upper lower part of the fin) of the corrugated fin 103 is closed because the bent part (the valley part) of the lower part of the corrugated fin is closed. There is a problem that the water is blocked and it is difficult for the water to flow downward and to be discharged.

  Further, the condensed water 201a collected at the lower part of the corrugated fin 103 that is mountain-folded is easier to discharge than the condensed water collected in the valley, but if there is no trigger, the flat heat transfer tube 102 There is a problem that it is difficult to fall down through the side of the.

  Therefore, the condensed water collected in the valley portion significantly reduces the air flow path area particularly in the valley-folded portion, and the condensed water accumulated in the mountain-folded portion is also somewhat large. Otherwise, it is difficult to discharge, so the air flow path area of this part is also reduced. For this reason, the pressure loss of the air flow path between the corrugated fins increases, the air volume decreases, and the effective area where the fins come into contact with air also decreases. In addition, the power consumption of the fan increases due to an increase in pressure loss in the air flow path. Therefore, there has been a problem of causing performance degradation of air conditioners and the like.

  A first embodiment of the heat exchanger of the present invention for solving this problem will be described with reference to FIGS. FIG. 4 is an enlarged cross-sectional view of the main part of FIG. 1, illustrating the configuration of the flat heat transfer tube and the corrugated fin to which the first embodiment of the present invention is applied, and FIG. 5 shows the air flow in the heat exchanger shown in FIG. It is the enlarged view seen from the downstream of this, It is a principal part enlarged front view explaining the state of the condensed water in the microchannel heat exchanger of Example 1. FIG.

  The overall configuration of the heat exchanger of the first embodiment is the same as that shown in FIGS. 2 and 3, and as shown in FIGS. 1 and 4, the heat exchanger 1 includes two refrigerant headers 100 and 101. The two refrigerant headers are connected and arranged between a plurality of flat heat transfer tubes 102 arranged in parallel in the vertical direction and the upper and lower flat heat transfer tubes 102 so as to contact the flat heat transfer tubes. Corrugated fins 103 are provided. In addition, a plurality of refrigerant flow paths 104 that communicate the two refrigerant headers 100 and 101 are formed inside the flat heat transfer tube 102. Reference numeral 105 denotes a slit formed in the corrugated fin 103 for promoting heat transfer.

  Moreover, the heat exchanger 1 of the first embodiment is provided with a notch 107 for allowing condensed water to flow in the lower part of the corrugated fin 103 on the side in contact with the flat heat transfer tube 102. The notch 107 is formed in a lower portion of the downstream end with respect to the air flow in the fin 103. That is, air flows from the right (rear side) to the left (front side) as indicated by the arrow 106, but the notch is formed at the fin downstream end lower portion (the left end lower portion of the fin 103 in FIG. 4) in the air flow direction. A portion 107 is formed.

The refrigerant flowing in the refrigerant flow path 104 exchanges heat with the air flowing through the flat heat transfer tubes 102 and the corrugated fins 103 as indicated by arrows 106 by the fan.
When the microchannel heat exchanger 1 shown in FIG. 4 is used as an evaporator, the air is cooled on the surface of the corrugated fins 103. At this time, when moisture in the air is condensed and condensed water is generated, This condensed water is transmitted along the surface of the corrugated fin 103 and the upper surface of the flat heat transfer tube 102, and along the air flow 106, on the downstream end side (left side in FIG. 4) of the fin 103 with respect to the air flow direction. Moving.

  For this reason, the condensed water tends to accumulate in the lower part of the downstream side of the corrugated fin 103 as shown in FIG. However, in the first embodiment, since the notch 107 is provided in the lower portion of the downstream end with respect to the air flow in the corrugated fin 103, the condensed water accumulated in the lower downstream portion of the corrugated fin 103 can be easily obtained. Can flow down. The reason for this will be described with reference to FIG.

  FIG. 5 is an enlarged view of the heat exchanger shown in FIG. 4 as viewed from the downstream side of the air flow. As shown in FIG. 5, the corrugated fin 103 is formed in a corrugated shape by bending a thin plate into a U shape. The notch 107 is provided at the lower part of the downstream end of the. 201a is condensed water accumulated in the lower part of the corrugated fin 103 (lower lower part of the fin), and 201b is the lower part of the corrugated fin 103 (lower upper part of the fin). ). Condensed water 201a indicated by a solid line and condensed water 201b indicated by an alternate long and short dash line indicate a state in which each condensed water is separated by fins, similarly to condensed water 201a and 201b shown in FIG.

  In this embodiment, the corrugated fin 103 has a valley-folded portion where the lower bent portion (valley) is closed, but the notch 107 is formed at the lower end of the corrugated fin 103 at the downstream end. Has been. For this reason, the condensed water 201b accumulated in the lower part of the valley-folded portion of the corrugated fin 103 is separated from the mountain fold of the corrugated fin 103 through the notch 107 as shown by the broken line arrow in FIG. It flows out to the lower part (upper surface of the flat heat transfer tube below the fins) of the part, and merges with the condensed water 201a accumulated in this part. As a result, as indicated by 201ab, the combined condensed water increases, but the larger the mass of water, the easier it is to flow down from the flat heat transfer tube 102 and be discharged.

  In addition, the condensed water 201a that has accumulated in the lower portion of the corrugated fin 103 that is mountain-folded also flows into the condensed water 201b that has accumulated in the valley portion, and due to its inertia, this is a trigger. It is easy to fall down along the side surface of the flat heat transfer tube 102.

  Therefore, according to the present embodiment, the condensed water 201b does not easily collect in the valley portion of the corrugated fin 103, and the condensed water 201a collected in the lower portion of the mountain-folded portion is easily discharged. And the area of the air flow path formed by the flat heat transfer tube 102 can be suppressed from being reduced by condensed water. As a result, the pressure loss in the air flow path formed by the corrugated fins 103 and the flat heat transfer tubes 102 can be reduced, so that the air volume can be increased and the effective area where the fins come into contact with air can be increased. Moreover, the power consumption of the fan can be reduced by reducing the pressure loss of the air flow path. Therefore, there is an effect of improving the performance of the air conditioner or the like.

  Further, according to this embodiment, before assembling the corrugated fins 103 and the flat heat transfer tubes 102, it is only necessary to cut out a part of the corrugated fins 103, and the rest of the conventional heat exchanger without the cutouts 107 is used. Since it may be the same as that of a manufacturing process, the effect that the manufacturing cost of a heat exchanger can also be reduced compared with the thing of the said patent document 1 etc. is acquired.

  In this embodiment, since the notch 107 is provided in a part of the corrugated fin 103, the surface area of the corrugated fin 103 is reduced, and the contact area between the corrugated fin 103 and the flat heat transfer tube 102 is also reduced. . However, in this embodiment, the notch 107 is provided on the downstream end of the fin with respect to the air flow 106, and the air approaching the fin temperature after heat exchange on the upstream side is provided. Since it is a flowing part, the influence on the heat exchange amount due to the reduction of the fin surface area and the contact area is negligible. In addition, since at least the upper part of the portion of the corrugated fin 103 where the notch 107 is formed is in contact with the flat heat transfer tube 102, heat exchange is sufficiently possible through this portion.

  Further, when the condensed water occupies 30% of the volume between the flat heat transfer tubes 102, the effective heat transfer area of the fin that is not affected by the thermal resistance due to the condensed water is reduced by 30%. On the other hand, in this embodiment, even if the notch 107 is provided, if the area of the notch 107 is 15% of the area of the corrugated fin not provided with the notch, The reduction of the effective heat transfer area by adopting the example is only 15%.

  Therefore, the effective heat transfer area of the fin by adopting this embodiment is 85%, and the effective heat transfer area of the fin is 70% compared to the conventional one in which the condensed heat is accumulated and the effective heat transfer area of the fin is 70%. Since the area can be increased, the heat exchange performance of the heat exchanger can also be improved.

In this embodiment, as shown in FIG. 4, the slit 105 a is also provided in the portion of the corrugated fin 103 where the notched portion 107 is provided. However, the slit 105 a does not cover the notched portion 107. It should be formed short.
Further, the notch 107 may have a substantially triangular shape as shown in FIG. 4, or may have a substantially rectangular shape or a substantially arc shape instead.
Furthermore, in this embodiment, the notch 107 is formed on both the left and right sides of the lower bent portion (valley) of the corrugated fin 103 that is the valley fold as shown in FIG. The notch 107 may be formed only on one side of the left side or the right side.

  Next, a second embodiment of the heat exchanger of the present invention will be described with reference to FIG. FIG. 6 is a diagram for explaining the second embodiment and corresponds to FIG. FIG. 6 shows an example in which the second embodiment is applied to the corrugated fin 103 of the microchannel heat exchanger 1 shown in FIG. 1, and the first embodiment described with reference to FIGS. The parts denoted by the same reference numerals indicate the same or corresponding parts, and in the description of the second embodiment, the description will focus on parts different from the first embodiment.

Corrugated fins 103 according to the second embodiment are provided between a plurality of flat heat transfer tubes 102 arranged in parallel in the vertical direction. In the first embodiment described above, as shown in FIGS. 1 and 5, as the corrugated fin 103, an example in which a thin plate is bent in a U shape, and a mountain fold and a valley fold are alternately repeated to form a corrugated shape. showed that. On the other hand, in the second embodiment, as the corrugated fin 103, a corrugated fin 103 having a waveform shape by bending a thin plate into a V shape and alternately repeating a mountain fold and a valley fold is used. Also in the second embodiment, similarly to the first embodiment, the notch 107 is provided in the lower portion of the corrugated fin 103 on the side in contact with the flat heat transfer tube 102. The notch 107 is formed in the lower portion of the downstream end with respect to the air flow in the corrugated fin 103.
Other configurations are the same as those of the first embodiment.

  Even if it is configured as in the second embodiment, the same effect as in the first embodiment can be obtained. Furthermore, according to the present embodiment, since the corrugated fin 103 is bent in a V shape, the lower portion of the corrugated fin 103 is opened compared to the bent shape in the U shape as shown in FIG. The width of the opening is increased. For this reason, there is an advantage that the condensed water 201a that accumulates at the lower part of the portion of the corrugated fin 103 that is mountain-folded flows down more easily.

Further, the condensed water 201b accumulated in the lower part of the corrugated fin 103 that is the valley fold flows out to the lower part of the corrugated fin 103 that is the mountain fold through the notch 107. The action of joining the condensed water 201a accumulated in the portion is the same as in the first embodiment. However, in the case of the present Example 2, since the corrugated fin 103 is V-shaped, as shown by the arrow 202, the condensed water 201b moves from a higher position to a lower position. There is also an effect of facilitating movement.
Therefore, according to the second embodiment, it is possible to obtain an effect that the condensed water is more easily discharged downward than that of the first embodiment.

  Embodiment 3 of the heat exchanger of the present invention will be described with reference to FIG. FIG. 7 is a diagram for explaining the third embodiment and corresponds to FIG. FIG. 7 shows an example in which the third embodiment is applied to the corrugated fin 103 of the microchannel heat exchanger 1 shown in FIG. 1, and the first embodiment described with reference to FIGS. The parts denoted by the same reference numerals indicate the same or corresponding parts. In the description of the third embodiment, the description will focus on the parts different from the first embodiment.

In the first embodiment, as shown in FIG. 4, the notch 107 is formed at the lower end of the downstream end of the corrugated fin 103 with respect to the air flow, but in the third embodiment, as shown in FIG. Instead of the notch 107, a notch 108 is formed at the lower part of the center with respect to the air flow in the corrugated fin 103. The notch 108 is not limited to the center, and may be formed at the center side of the downstream end side and the upstream end side, such as the downstream side and the upstream side of the center.
Other configurations are the same as those of the first embodiment.

  Even if it is configured as in the third embodiment, the same effect as in the first embodiment can be obtained. That is, in the present embodiment, the notch 108 is formed in the middle of the air flow in the fin 103, but the notch 108 has accumulated in the valley of the corrugated fin 103 as shown in FIG. The action of allowing the condensed water 201b to flow out to the upper part of the flat heat transfer tube at the lower part of the mountain fold is the same. Therefore, even if comprised like a present Example, the condensed water 201b can be merged with the condensed water 201a similarly to Example 1, and the effect which makes condensed water large and can be easily discharged | emitted below can be acquired.

  Further, according to the third embodiment, the notch 108 is formed not on the downstream end of the corrugated fin 103 but on the center side, so that the condensation of the end of the corrugated fin 103 is not reduced. The effect that water can be easily discharged downward is also obtained.

  Embodiment 4 of the heat exchanger of the present invention will be described with reference to FIG. FIG. 8 is a diagram for explaining the fourth embodiment and corresponds to FIG. 4 and FIG. FIG. 8 shows a case where the fourth embodiment is applied to the corrugated fin 103 of the microchannel heat exchanger 1 shown in FIG. 1, and the embodiment described with reference to FIGS. 1 to 5 and FIG. The parts denoted by the same reference numerals as those in Examples 1 and 3 indicate the same or corresponding parts. In the description of the fourth embodiment, the description will focus on the parts different from the first and third embodiments.

  In the fourth embodiment, as in the first embodiment, the notch 107 provided in the lower portion of the downstream end with respect to the air flow of the corrugated fin 103 and the corrugated fin 103 as in the third embodiment. The notch part 108 provided in the lower part of the center part side with respect to the air flow is arranged in parallel. Further, in the fourth embodiment, the notch 109 is also formed in the lower portion of the upstream end with respect to the air flow of the corrugated fin 103.

Thus, in the present embodiment, a plurality of notches 107 to 109 are provided along the air flow at the lower part of the corrugated fin 103. In the example shown in FIG. 8, the notch portions are provided at three locations of the lower end of the fin, the lower portion of the central portion, and the lower portion of the upstream end with respect to the air flow. It is not restricted to a thing, You may make it provide in the part of at least 2 or more places among these.
Other configurations are the same as those of the first embodiment.

  According to the fourth embodiment, since the plurality of notches 107 to 109 are provided along the air flow in the lower part of the corrugated fin 103, the valleys of the corrugated fin 103 are similar to those shown in FIGS. The condensed water 201b accumulated in the section can be discharged to the upper part of the flat heat transfer tube at the lower part of the mountain fold, and the condensed water 201b can be joined to the condensed water 201a and easily discharged downward. Can do.

  Furthermore, according to the fourth embodiment, even if a large amount of condensed water 201b accumulates in any position in the air flow direction in the corrugated fin 103, an effect can be obtained in which the condensed water 201a is immediately joined to the condensed water 201a and discharged downward. That is, condensate may accumulate in various parts of the corrugated fin in the air flow direction due to dirt on the surface of the corrugated fin, deformation of the fin, turbulence in the air flow, etc. However, according to the present embodiment, it can be dealt with.

  Embodiment 5 of the heat exchanger of the present invention will be described with reference to FIG. FIG. 9 is a diagram for explaining the fifth embodiment and corresponds to FIG. FIG. 9 shows an example in which the fifth embodiment is applied to the fins of the microchannel heat exchanger 1 shown in FIG. 1, and the same reference numerals as those in the first embodiment described with reference to FIGS. The attached parts indicate the same or corresponding parts, and in the description of the fifth embodiment, the description will focus on parts different from the first embodiment.

As shown in FIG. 9, the fifth embodiment is a microchannel heat exchanger 1 that employs plate fins 113 instead of corrugated fins 103 as shown in FIGS. 1 to 5 as fins. is there.
The plate fins 113 are vertically long plate-like fins joined to all of the flat heat transfer tubes 102 arranged in parallel in the vertical direction, and are disposed between the plurality of refrigerant headers 100 and 101 (see FIG. 1). Many sheets are arranged in parallel at equal intervals.

  As shown in FIG. 9, each plate fin 113 has a flat plate portion 113 a extending in the vertical direction and a plurality of openings for inserting the flat heat transfer tube 102 into one end side (downstream side in this example) of the flat plate portion 113 a. The notches 113b are formed so as to correspond to the installation positions of the flat heat transfer tubes 102. The plate fins 113 are inserted into the flat heat transfer tubes 102 such that the plurality of flat heat transfer tubes 102 arranged in the vertical direction are inserted into the cuts 113b. After inserting all of the plate fins 113 arranged between the plurality of refrigerant headers 100 and 101 into the flat heat transfer tube 102, the flat heat transfer tube 102 and the plate fin 113 are joined by brazing or the like. The

  As described above, the plate fins 113 are configured as plug-in type plate fins, and the upstream side of the air flow 106 of each plate fin 113 is integrated by the flat plate portion 113a, and between the upper and lower cuts 113b. The portion where the slit 105 is formed is a fin portion 113 c and is in contact with each flat heat transfer tube 102.

  A notch 110 is formed in the lower portion of the downstream end with respect to the air flow 106 in each fin 113c. Since the plate fins 113 having the notches 110 are arranged in parallel in the left-right direction between the plurality of refrigerant headers 100 and 101, the condensed water collected between the plate fins 113 is The condensed water accumulated between the adjacent plate fins 113 can be merged through the notch 110.

Therefore, since the condensate that has merged becomes large, the condensate can be easily caused to flow down and discharged, so that even when the plate fin 113 is used, the same effect as in the first embodiment can be obtained.
In the fifth embodiment, as in the fourth embodiment described above, a plurality of notches may be provided below the fin portions 113c along the air flow.

  In the description of each embodiment described above, it has been described that the fin (corrugated fin 103, plate fin 113) and the flat heat transfer tube 102 are provided in contact with each other. In the invention, those fixed by brazing or the like are also included.

  The present invention is not limited to the above-described embodiments, and includes various modifications. Further, the above-described embodiments have been described in detail for easy understanding of the present invention, and are not necessarily limited to those having all the configurations described.

1: heat exchanger,
100, 101: Refrigerant header,
102: flat heat transfer tube,
104: refrigerant flow path, 105, 105a: slit, 106: air flow,
107-110: Notch,
103, 113: fins (103: corrugated fins, 113: plate fins),
113a: flat plate portion, 113b: notch, 113c: fin portion),
201a, 201b: Condensed water, 201ab: Condensed condensed water.

Claims (9)

In the heat exchanger comprising two refrigerant headers, a plurality of flat heat transfer tubes arranged in the vertical direction, connecting the two refrigerant headers, and fins disposed between the flat heat transfer tubes,
The heat exchanger characterized by providing the notch part for making condensed water flow in the part of the side which contacts the said flat heat exchanger tube in the lower part of the said fin.   2. The heat exchanger according to claim 1, wherein the notch portion provided in the fin is formed in a lower portion of a downstream end of the fin with respect to an air flow. vessel.   2. The heat exchanger according to claim 1, wherein the notch provided in the fin is formed in a lower portion of the fin on the center side with respect to the air flow. Exchanger.   2. The heat exchanger according to claim 1, wherein the notch portion provided in the fin is at least two of a lower downstream end lower portion, a central lower portion and an upstream lower end of the fin with respect to the air flow. A heat exchanger characterized by being formed in more than a portion.   The heat exchanger as described in any one of Claims 1-4 WHEREIN: The said fin is a corrugated fin, The heat exchanger characterized by the above-mentioned.   6. The heat exchanger according to claim 5, wherein the corrugated fin is bent in a U shape, and is formed into a wave shape by alternately repeating mountain folds and valley folds. vessel.   6. The heat exchanger according to claim 5, wherein the corrugated fin is bent into a V shape, and has a wave shape obtained by alternately repeating mountain folds and valley folds. vessel.   The heat exchanger according to any one of claims 1 to 4, wherein the fins are plate fins.   9. The heat exchanger according to claim 8, wherein the plate fins are vertically long plate-like fins joined to all of the flat heat transfer tubes arranged in parallel in the vertical direction, and the two refrigerant headers. A plurality of plate fins are arranged in parallel, and each plate fin has a flat plate portion extending in the vertical direction, and is opened on one end side of the flat plate portion, and a plurality of cuts for inserting the flat heat transfer tube are formed in the flat plate portion. A heat exchanger characterized by being formed so as to correspond to the installation position of the heat transfer tube.

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