JP5141840B2 - Heat exchanger and air conditioner - Google Patents

Abstract

A heat exchanger (30) includes flat tubes (33) and fins (36). The plate-like fins (36) are spaced from one another by a predetermined distance in the direction in which the flat tubes (33) extend. The flat tubes (33) are inserted in pipe insertion portions (46) of the fins (36). In the fins (36), parts of the fins (36) between vertically adjacent ones of the flat tubes (33) are heat transfer parts (70). Each of the heat transfer parts (70) includes protrusions (81-83) and louvers (50, 60). The protrusions (81-83) are located at a windward region of the heat transfer part (70) and formed by making the heat transfer part (70) protrude in an inverted V shape. The louvers (50, 60) are located in a leeward region of the heat transfer part (70) and bend out from the heat transfer part (70).

Description

  The present invention relates to a heat exchanger that includes a flat tube and fins and exchanges heat between fluid flowing in the flat tube and air.

  Conventionally, a heat exchanger including a flat tube and fins is known. For example, in the heat exchanger described in Patent Document 1, a plurality of flat tubes extending in the left-right direction are arranged one above the other at a predetermined interval, and plate-like fins are arranged at a predetermined interval from each other. They are arranged in the direction of extension. Further, in the heat exchangers described in Patent Document 2 and Patent Document 3, a plurality of flat tubes extending in the left-right direction are arranged one above the other at a predetermined interval, and one corrugated fin is provided between adjacent flat tubes. It is provided one by one. In these heat exchangers, the air flowing while contacting the fins exchanges heat with the fluid flowing in the flat tube.

  Usually, a louver for promoting heat transfer is formed on the fin of this type of heat exchanger. For example, as described in FIG. 4 of Patent Document 3, in the fins of the conventional heat exchanger, a plurality of louvers having the same cut and raised height are arranged in the air passage direction.

JP 2003-262485 A JP 2010-002138 A JP 11-294984 A

  By the way, the refrigerant circuit of the air conditioner is provided with an outdoor heat exchanger that exchanges heat between the refrigerant and outdoor air. During the heating operation of the air conditioner, the outdoor heat exchanger functions as an evaporator. When the evaporation temperature of the refrigerant in the outdoor heat exchanger falls below 0 ° C., moisture in the air becomes frost (that is, ice) and adheres to the outdoor heat exchanger. Therefore, during the heating operation in a state where the outside air temperature is low, a defrosting operation for melting frost attached to the outdoor heat exchanger is performed, for example, every time a predetermined time elapses. During the defrosting operation, the high-temperature refrigerant discharged from the compressor is supplied to the outdoor heat exchanger, and the frost attached to the outdoor heat exchanger is heated by the refrigerant and melts. During the defrosting operation, since the refrigerant discharged from the compressor is supplied not to the indoor heat exchanger but to the outdoor heat exchanger, the blowing of warm air into the room is interrupted.

  On the other hand, a heat exchanger provided with flat tubes and fins can be used as an outdoor heat exchanger of an air conditioner. However, in this type of conventional heat exchanger, a louver is usually provided from the vicinity of the front edge of the fin to the vicinity of the rear edge. For this reason, in the outdoor heat exchanger comprised with this kind of heat exchanger, frost concentrates on the windward side part of a fin, and the flow of air will be inhibited by the attached frost. As a result, the flow of air passing through the heat exchanger is reduced and the amount of heat exchange between the refrigerant and the air is reduced, although the frost is hardly attached to the leeward side portion of the fin, and the defrosting is performed. It falls into a situation that requires action. Therefore, when this type of heat exchanger is used as an outdoor heat exchanger of an air conditioner, the frequency of interruption of warm air blowing into the room is increased by performing the defrosting operation. There was a risk of reducing the heating capacity of the machine.

  The present invention has been made in view of the above point, and the purpose of the present invention is to reduce the capacity reduction of the heat exchanger due to frost attached to the fin in the heat exchanger including the flat tube and the fin. Is to extend the time.

  According to the first aspect of the present invention, air is provided between a plurality of flat tubes (33) that are arranged one above the other so that the side surfaces face each other and in which a fluid passage (34) is formed, and between the adjacent flat tubes (33). A plurality of fins (35, 36) partitioned into a plurality of ventilation paths (40) through which the air flows, and the fins (35, 36) are in a plate shape extending from one to the other of the adjacent flat tubes (33). A heat exchanger having a plurality of heat transfer portions (70) formed and constituting the side walls of the ventilation path (40) is made symmetrical. And in each heat-transfer part (70) of the said fin (35,36), several louvers (50,60) formed by cutting and raising this heat-transfer part (70), and the said louver (50, 60) disposed on the windward side and provided with a bulging portion (81 to 83) formed by bulging the heat transfer portion (70) and extending in a direction intersecting the air passage direction It is.

  In the first invention, the heat exchanger (30) is provided with a plurality of flat tubes (33) and a plurality of fins (35, 36). Between the flat tubes (33) lined up and down, the heat transfer section (70) of the fins (35, 36) is arranged. In the heat exchanger (30), air passes through the ventilation path (40) between the flat tubes (33) arranged in the vertical direction, and this air and heat flow through the passage (34) in the flat tubes (33). Exchange.

  In the first invention, each heat transfer portion (70) of the fin (35, 36) is provided with a bulging portion (81-83) and a louver (50, 60). The bulging part (81-83) is provided in a part above the louver (50, 60) in the heat transfer part (70). If the bulging part (81-83) or louver (50, 60) is formed in the heat transfer part (70), the air flow in the ventilation path (40) is disturbed and heat transfer between the air and the fins Is promoted.

  In general, the effect of disturbing the air flow is that the louver (50, 60) formed by cutting and raising the heat transfer section (70) causes the heat transfer section (70) to bulge. It is larger than the protruding part (81-83). Therefore, normally, the louver (50, 60) is also larger than the bulging portion (81-83) in terms of the heat transfer promoting effect.

  By the way, when the temperature of the fluid flowing in the flat tube (33) is lower than 0 ° C., moisture in the air becomes frost and adheres to the surface of the heat transfer section (70). On the other hand, in each heat transfer part (70) of the fins (35, 36) of the first invention, the heat transfer promoting effect is provided in the windward portion of the louver (50, 60) having a relatively high heat transfer promoting effect. A relatively low bulge (81-83) is formed. For this reason, compared with the case where the louvers (50, 60) are formed over the entire heat transfer section (70), the amount of frost adhering to the windward portion of the heat transfer section (70) is reduced. However, the amount of frost attached to the leeward portion of the heat transfer section (70) increases. Accordingly, in the heat transfer section (70) of the present invention, the difference between the amount of frost attached to the leeward portion and the amount of frost attached to the leeward portion is reduced.

The first invention, in addition to the above arrangement, each of the heat transfer part the louvers (50, 60) No Chi upper Symbol bulge provided in (70) of the fin (35, 36) ( 81-83) Lulu Ba (50 to position the closer) protrudes in the protruding direction of the wind under the side of the cut-and-raised end (53) is bulging portion (81 to 83), the windward side of the cut-and-raised end ( 53) protrudes on the opposite side to the bulging direction of the bulging portions (81 to 83) .

In each heat transfer part (70) of the fins (35, 36) of the first invention, a part of the louvers (50) located closer to the bulging part (81 to 83) are cut and raised on the leeward side ( 53) protrudes in the bulging direction of the bulging portions (81 to 83). That is, a part of the louvers (50) located closer to the bulging part (81 to 83) are inclined in the direction opposite to the leeward part of the bulging part (81 to 83). The air flowing over the bulging portion (81 to 83) hits the louver (50) located closer to the bulging portion (81 to 83), and the direction of the flow changes. Therefore, the air flow that has passed over the bulging portions (81 to 83) is further disturbed by hitting the louver (50) located closer to the bulging portions (81 to 83).

According to a second invention, in the first invention, the cut and raised ends (53, 63) of the louver (50, 60) include a main edge (54, 64) and the main edge (54, 64). An upper edge (55,65) inclined from the upper edge of the louver (50,60) to the upper edge of the main edge (54,64), and the main edge (54,64). ) And the lower edge (56, 66) inclined from the main edge (54, 64) to the lower end of the louver (50, 60), 35, 36) In each heat transfer section (70), at least a part of the louver (50, 60) is inclined with respect to the main edge (54) of the lower edge (56). This is an asymmetric louver that is gentler than the inclination of (55) with respect to the main edge (54).

In the second invention, the cut-and-raised end (53,63) of the louver (50,60) includes the main edge (54,64), the upper edge (55,65), and the lower edge (56,66). It is comprised by. In each heat transfer section (70) of the fins (35, 36), at least a part of the louvers (50, 60) formed therein are asymmetric louvers (50a). In the asymmetric louver (50a), the inclination of the lower edge (56) relative to the main edge (54) is gentler than the inclination of the upper edge (55) relative to the main edge (54). For this reason, between the cut-and-raised ends (53) of the asymmetric louvers (50a) adjacent to each other in the air passage direction, the gap between the lower edges (56) is larger than the gap between the upper edges (55). And become elongated.

On the surface of the fin (35, 36) of the heat exchanger (30) of the second invention, water in the air is condensed or frost adhering to the fin (35, 36) is melted to generate drain water. To do. The drain water generated on the surfaces of the fins (35, 36) also enters between the cut and raised ends (53) of the asymmetric louvers (50a) adjacent to each other in the air passing direction. The drain water that has entered between the asymmetric louvers (50a) is drawn into the gap between the elongated lower edges (56) by capillary action.

According to a third invention, in the second invention, in each heat transfer section (70) of the fin (35, 36), a louver (50) formed in a portion adjacent to the flat tube (33) is It is an asymmetric louver.

In the third invention, in each heat transfer section (70) of the fins (35, 36), a louver (50) is formed in a portion adjacent to the flat tube (33), and a part of the louver (50) Or all become asymmetric louvers.

According to a fourth invention, in any one of the first to third inventions, each heat transfer section (70) of the fins (35, 36) is located on the leeward side of the flat tube (33). A lower end portion (73) is provided, and in each heat transfer portion (70) of the fins (35, 36), the louver (60) is provided at the wind lower end portion (73).

In 4th invention, each heat-transfer part (70) of a fin (35, 36) is provided with the wind lower end part (73). The lee end part (73) of the heat transfer part (70) protrudes further to the leeward side than the flat tube (33). In the heat transfer section (70) of the present invention, the louver (60) is provided at the wind lower end (73). In the heat transfer section (70) of the present invention, it is only necessary that the louvers (50, 60) are provided at least at the wind lower end (73). That is, in the heat transfer section (70) of the present invention, even if a plurality of louvers (50, 60) are provided across the windward lower end part (73) and the windward lower end part (73). Good.

According to a fifth invention, in any one of the first to fourth inventions, in each of the heat transfer parts (70) of the fins (35, 36), the plurality of bulge parts (81 to 83) are air. Are provided side by side in the passing direction.

In the fifth invention, a plurality of bulge portions (81 to 83) are provided in each heat transfer portion (70) of the fins (35, 36). In each heat transfer section (70), the plurality of bulging sections (81 to 83) are arranged in the air passage direction. The air flow in the ventilation path (40) is disturbed every time the air passes over the plurality of bulges (81 to 83).

In a sixth aspect based on the fifth aspect , the plurality of bulging portions (81 to 83) formed in the heat transfer portions (70) of the fins (35, 36) are located on the most upwind side. The width of the bulging portion (81) in the air passage direction is the widest.

  Here, the wider the width of the bulging portion (81-83) in the air passage direction, the smaller the change in the flow direction of the air flowing along the bulging portion (81-83). As a result, the bulging portion The effect of promoting heat transfer due to (81 to 83) is reduced. On the other hand, the temperature difference between the air flowing through the ventilation path (40) and the heat transfer section (70) is the largest at the inlet of the ventilation path (40) and gradually decreases toward the lee.

In the sixth aspect of the invention, in each heat transfer section (70) of the fins (35, 36), the width of the bulging section (81) located most upwind in the air passage direction is the remaining bulging section (82). , 83) is wider than the width in the air passage direction. That is, in each heat transfer part (70) of the fins (35, 36), heat transfer is promoted to a position closer to the windward where the temperature difference between the air flowing through the ventilation path (40) and the heat transfer part (70) is relatively large. The widest bulging portion (81) having a relatively small effect is provided. For this reason, in each heat-transfer part (70) of a fin (35, 36), the quantity of the frost adhering to the part near the windward provided with the widest bulging part (81) is suppressed.

In a seventh aspect based on the fifth or sixth aspect , the plurality of bulges (81 to 83) formed in the heat transfer portions (70) of the fins (35, 36) The height in the bulging direction of the bulging portion (81) located above is the lowest.

  Here, the lower the height of the bulging part (81-83) in the bulging direction, the less the change in the flow direction of the air flowing along the bulging part (81-83). As a result, the bulging part The effect of promoting heat transfer due to (81 to 83) is reduced. On the other hand, the temperature difference between the air flowing through the ventilation path (40) and the heat transfer section (70) is the largest at the inlet of the ventilation path (40) and gradually decreases toward the lee.

In 7th invention, in each heat-transfer part (70) of a fin (35, 36), the height of the bulging direction of the bulging part (81) located most upwind is the remaining bulging part (82). , 83) is lower than the height in the bulging direction. That is, in each heat transfer part (70) of the fins (35, 36), heat transfer is promoted to a position closer to the windward where the temperature difference between the air flowing through the ventilation path (40) and the heat transfer part (70) is relatively large. The lowest bulging portion (81) having a relatively small height is provided. For this reason, in each heat-transfer part (70) of a fin (35, 36), the quantity of the frost adhering to the windward near part provided with the bulging part (81) with the lowest height is suppressed.

In an eighth invention according to any one of the fifth to seventh inventions, in each heat transfer portion (70) of the fin (35, 36), an end portion on the windward side of the heat transfer portion (70) A plurality of the bulging portions (81 to 83) are provided in a portion from (38) to the leeward position from the center in the air passing direction of the heat transfer portion (70).

In the eighth invention, in each heat transfer section (70) of the fins (35, 36), a plurality of bulging sections (81 to 83) are provided in a region that is at least half the length in the air passage direction.

According to a ninth invention, in any one of the fifth to eighth inventions, each heat transfer section (70) of the fin (35, 36) is located upstream of the flat tube (33). A windward end (72) is provided, and in each heat transfer section (70) of the fin (35, 36), the windward end (72) and the leeward side of the windward end (72) A plurality of the bulging portions (81 to 83) are provided.

In the ninth aspect of the invention, the wind upper end portion (72) is provided in each heat transfer portion (70) of the fin (35, 36). And in each heat-transfer part (70), several bulging parts (81-83) straddle both the windward upper end part (72) and the part adjacent to the leeward side of the windward upper end part (72). Provided.

In a tenth aspect of the present invention, in any one of the fifth to ninth aspects, in each heat transfer section (70) of the fin (35, 36), the lower end of each bulge section (81-83) is leeward. It inclines so that it may become a lower side as it is a side.

In the 10th invention, the lower end of the bulging part (81-83) provided in each heat-transfer part (70) of a fin (35, 36) inclines. The lower end of each bulging part (81-83) inclines so that it may become downward, so that the leeward side. For this reason, in each heat-transfer part (70) of a fin (35, 36), from the flat tube (33) adjacent to the lower side of the heat-transfer part (70) to the lower end of a bulging part (81-83) The distance gradually decreases toward the leeward side.

Here, during the defrost to melt the frost adhered to the fins (35, 36), the drain water generated by melting the frost is swelled along the surface of the heat transfer section (70) (81- 83) It flows down from the bottom. The drain water that has flowed down from the bulging part (81 to 83) accumulates on the flat tube (33) adjacent to the lower side of the heat transfer part (70). On the other hand, in the tenth invention, the distance from the flat tube (33) below the heat transfer section (70) to the lower end of the bulging section (81 to 83) gradually decreases toward the leeward side. For this reason, the drain water that has flowed down from the bulging portion (81 to 83) and accumulated on the flat tube (33) has a short distance from the flat tube (33) to the lower end of the bulging portion (81 to 83). It is drawn to the side by capillary action.

In an eleventh aspect based on any one of the first to tenth aspects, the fin (36) has a plate shape in which a plurality of notches (45) for inserting the flat tube (33) are provided. The flat tube (33) is disposed at a predetermined interval in the extending direction of the flat tube (33), the flat tube (33) is sandwiched by the periphery of the notch (45), and the fin (36) Then, the part between the notch parts (45) adjacent up and down comprises the said heat-transfer part (70).

In the eleventh aspect , the plurality of fins (36) formed in a plate shape are arranged at predetermined intervals in the extending direction of the flat tube (33). Each fin (36) is formed with a plurality of notches (45) for inserting the flat tube (33). As for each fin (36), the peripheral part of the notch (45) has pinched the flat tube (33). And in each fin (36), the part between the notch parts (45) adjacent up and down comprises a heat-transfer part (70).

In a twelfth aspect of the invention according to any one of the first to tenth aspects of the invention, the fin (35) is a corrugated fin meandering up and down disposed between the adjacent flat tubes (33). A plurality of the heat transfer portions (70) arranged in the extending direction of the flat tube (33) and a portion continuous to the upper end or the lower end of the adjacent heat transfer portion (70), the flat tube (33) And a plurality of intermediate plate portions (41) joined to each other.

In the twelfth invention, the fin (35) which is a corrugated fin is disposed between the adjacent flat tubes (33). Each fin (35) is provided with a plurality of heat transfer sections (70) arranged in the extending direction of the flat tube (33). Moreover, in each fin (35), the adjacent heat-transfer part (70) is connected to the intermediate plate part (41), and this intermediate plate part (41) is joined to the flat side surface of the flat tube (33). .

A thirteenth invention is directed to an air conditioner (10), and includes a refrigerant circuit (20) provided with the heat exchanger (30) of any one of the first to thirteenth inventions, and the refrigerant circuit In (20), the refrigerant is circulated to perform the refrigeration cycle.

In the third invention, the heat exchanger (30) of any one of the first to twelfth inventions is connected to the refrigerant circuit (20). In the heat exchanger (30), the refrigerant circulating in the refrigerant circuit (20) flows through the passage (34) of the flat tube (33) and exchanges heat with the air flowing through the ventilation path (40).

  In each heat transfer part (70) of the fins (35, 36) of the present invention, a bulging part (81-83) having a relatively low heat transfer promoting effect is provided on the windward side of the louver (50, 60). Is formed. For this reason, the difference between the amount of frost adhering to the windward side portion of the heat transfer section (70) and the amount of frost adhering to the leeward side portion becomes small. As a result, in the heat exchanger (30) of the present invention, frost adherence at the time when the decrease in heat exchange capacity reaches a limit as compared with the conventional heat exchanger in which frost concentrates on the windward portion of the fin. The amount increases. Therefore, according to the present invention, it is possible to extend the time until the capacity reduction of the heat exchanger (30) due to frost adhesion reaches the limit, and the frequency of defrosting can be reduced.

Further, in each heat transfer section (70) of the present invention , a part of the louvers (50) located closer to the bulge section (81 to 83) have a cut-and-raised end (53) on the leeward side of the bulge section (53). 81-83) projecting in the bulging direction. For this reason, the air flow that has passed over the bulging portions (81 to 83) is further disturbed by hitting the louvers (50) located closer to the bulging portions (81 to 83). Therefore, according to the present invention , heat transfer between the fins (35, 36) and the air can be surely promoted in the portion of the heat transfer section (70) where the louvers (50, 60) are formed. .

In the second aspect of the invention, at least a part of the louvers (50, 60) formed in the heat transfer portions (70) of the fins (35, 36) are asymmetric louvers (50a). In the asymmetric louver (50a), the inclination of the lower edge (56) relative to the main edge (54) is gentler than the inclination of the upper edge (55) relative to the main edge (54). For this reason, the drain water generated on the surface of the fins (35, 36) and entering between the cut-and-raised ends (53) of the asymmetric louvers (50a) adjacent to each other in the air passage direction is elongated by the capillary action. It is drawn into the gap between the edges (56). Therefore, according to the present invention, the drain water that has entered between the cut-and-raised ends (53) of the asymmetric louvers (50a) adjacent to each other in the air passage direction can flow downward not only by gravity but also by capillary action. The amount of drain water remaining on the surface of the heat transfer section (70) can be reduced.

In the fourth aspect of the invention, the louvers (50, 60) are provided at the wind lower ends (73) of the heat transfer sections (70) of the fins (35, 36). The temperature difference between the wind lower end portion (73) and the air flowing through the ventilation path (40) is smaller than the portion sandwiched between the upper and lower flat tubes (33). On the other hand, in this invention, the louver (60) is provided at the wind lower end (73) of the heat transfer section (70), and heat transfer between the wind lower end (73) and the air is promoted. Therefore, according to this invention, the wind lower end (73) of the heat transfer section (70) can be effectively used for heat exchange with air, and the performance of the heat exchanger (30) can be improved. it can.

In the fifth aspect of the present invention, a plurality of bulge portions (81 to 83) are provided in each heat transfer portion (70) of the fins (35, 36). For this reason, the air flow in the ventilation path (40) is disturbed every time it passes over the plurality of bulging portions (81 to 83). Therefore, according to this invention, the heat transfer between the part in which the bulging part (81-83) was provided among the heat transfer parts (70) and air can be accelerated | stimulated.

In the sixth aspect of the invention, in each heat transfer section (70) of the fins (35, 36), the width in the air passage direction of the bulge section (81) located on the most windward side is the remaining bulge section ( 82, 83) is wider than the width in the air passage direction. Moreover, in each heat-transfer part (70) of the said 7th invention fin (35,36), the height of the bulging direction of the bulging part (81) located most upwind is the remaining bulging part ( 82, 83) is lower than the height in the bulging direction.

That is, in each of the sixth and seventh inventions, in each heat transfer section (70) of the fins (35, 36), the temperature difference between the air flowing through the ventilation path (40) and the heat transfer section (70) is relatively large. A bulging portion (81) having a smaller heat transfer promoting effect than the remaining bulging portions (82, 83) is provided at a position closer to the windward side. Therefore, according to these inventions, it is possible to suppress the amount of frost that adheres to the windward portion of each heat transfer section (70) of the fins (35, 36), and the wind of the heat transfer section (70). The difference between the amount of frost adhering to the upper portion and the amount of frost adhering to the leeward portion can be reliably reduced.

In the tenth aspect of the invention, the lower ends of the bulging portions (81 to 83) provided in the heat transfer portions (70) of the fins (35, 36) are inclined so as to be lower toward the leeward side. For this reason, the drain water generated on the surface of the heat transfer section (70) and flowing down from the bulge section (81-83) is the distance from the flat tube (33) to the lower end of the bulge section (81-83). Is drawn toward the short leeward side by capillary action. Therefore, according to this invention, the movement of drain water generated on the surface of the heat transfer section (70) to the leeward side can be promoted, and the amount of drain water remaining in the heat exchanger (30) can be reduced.

FIG. 1 is a refrigerant circuit diagram illustrating a schematic configuration of an air conditioner including the heat exchanger according to the first embodiment. FIG. 2 is a schematic perspective view of the heat exchanger according to the first embodiment. FIG. 3 is a partial cross-sectional view illustrating the front of the heat exchanger according to the first embodiment. FIG. 4 is a cross-sectional view of the heat exchanger showing a part of the AA cross section of FIG. 3. 5A and 5B are views showing main parts of the fins of the heat exchanger according to the first embodiment, wherein FIG. 5A is a front view of the fins, and FIG. 5B is a cross-sectional view showing a BB cross section of FIG. It is. 6A and 6B are cross-sectional views of fins provided in the heat exchanger according to the first embodiment, in which FIG. 6A shows a CC cross section of FIG. 5 and FIG. 6B shows a DD cross section of FIG. (C) shows the EE cross section of FIG. FIG. 7 is a view showing a heat transfer portion of a plurality of fins provided in the heat exchanger of Embodiment 1, and is a cross-sectional view corresponding to FIG. FIG. 8 is a cross-sectional view of the fin showing the FF cross section of FIG. 5. FIG. 9 is a schematic perspective view of the heat exchanger according to the second embodiment. FIG. 10 is a partial cross-sectional view illustrating the front of the heat exchanger according to the second embodiment. FIG. 11 is a cross-sectional view of the heat exchanger showing a part of the GG cross section of FIG. 10. FIG. 12 is a schematic perspective view of fins provided in the heat exchanger of the second embodiment. FIG. 13 is a cross-sectional view corresponding to FIG. 4 of the heat exchanger according to the third embodiment. FIG. 14: is a figure which shows the principal part of the fin of the heat exchanger of Embodiment 3, Comprising: (A) is a front view of a fin, (B) is sectional drawing which shows the HH cross section of (A). It is. FIG. 15 is a front view of a fin showing a first modification of the other embodiment applied to the fin of the first embodiment, and corresponds to FIG. 4. FIG. 16 is a front view of a fin showing a second modification of the other embodiment applied to the fin of the first embodiment, and corresponds to FIG. 4. Figure 17 is a sectional view corresponding to the view of full fin 5 (B), (A) shows the an application of the third modified example of the other embodiment to the fin embodiment 1, (B ) Shows the reference technique applied to the fin of the first embodiment.

  Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.

Embodiment 1 of the Invention
A first embodiment of the present invention will be described. The heat exchanger (30) of Embodiment 1 comprises the outdoor heat exchanger (23) of the air conditioner (10) mentioned later.

-Air conditioner-
The air conditioner (10) provided with the heat exchanger (30) of the present embodiment will be described with reference to FIG.

<Configuration of air conditioner>
The air conditioner (10) includes an outdoor unit (11) and an indoor unit (12). The outdoor unit (11) and the indoor unit (12) are connected to each other via a liquid side connecting pipe (13) and a gas side connecting pipe (14). In the air conditioner (10), the refrigerant circuit (20) is formed by the outdoor unit (11), the indoor unit (12), the liquid side communication pipe (13), and the gas side communication pipe (14).

  The refrigerant circuit (20) is provided with a compressor (21), a four-way switching valve (22), an outdoor heat exchanger (23), an expansion valve (24), and an indoor heat exchanger (25). ing. The compressor (21), the four-way switching valve (22), the outdoor heat exchanger (23), and the expansion valve (24) are accommodated in the outdoor unit (11). The outdoor unit (11) is provided with an outdoor fan (15) for supplying outdoor air to the outdoor heat exchanger (23). On the other hand, the indoor heat exchanger (25) is accommodated in the indoor unit (12). The indoor unit (12) is provided with an indoor fan (16) for supplying room air to the indoor heat exchanger (25).

  The refrigerant circuit (20) is a closed circuit filled with a refrigerant. In the refrigerant circuit (20), the compressor (21) has its discharge side connected to the first port of the four-way switching valve (22) and its suction side connected to the second port of the four-way switching valve (22). Yes. In the refrigerant circuit (20), the outdoor heat exchanger (23), the expansion valve (24), and the indoor heat exchanger are sequentially arranged from the third port to the fourth port of the four-way switching valve (22). (25) and are arranged.

  The compressor (21) is a scroll type or rotary type hermetic compressor. The four-way switching valve (22) has a first state (state indicated by a broken line in FIG. 1) in which the first port communicates with the third port and the second port communicates with the fourth port, The port is switched to a second state (state indicated by a solid line in FIG. 1) in which the port communicates with the fourth port and the second port communicates with the third port. The expansion valve (24) is a so-called electronic expansion valve.

  The outdoor heat exchanger (23) exchanges heat between the outdoor air and the refrigerant. The outdoor heat exchanger (23) is configured by the heat exchanger (30) of the present embodiment. On the other hand, the indoor heat exchanger (25) exchanges heat between the indoor air and the refrigerant. The indoor heat exchanger (25) is constituted by a so-called cross fin type fin-and-tube heat exchanger provided with a heat transfer tube which is a circular tube.

<Cooling operation>
The air conditioner (10) performs a cooling operation. During the cooling operation, the four-way switching valve (22) is set to the first state. During the cooling operation, the outdoor fan (15) and the indoor fan (16) are operated.

  In the refrigerant circuit (20), a refrigeration cycle is performed. Specifically, the refrigerant discharged from the compressor (21) flows into the outdoor heat exchanger (23) through the four-way switching valve (22), dissipates heat to the outdoor air, and is condensed. The refrigerant flowing out of the outdoor heat exchanger (23) expands when passing through the expansion valve (24), then flows into the indoor heat exchanger (25), absorbs heat from the indoor air, and evaporates. The refrigerant that has flowed out of the indoor heat exchanger (25) passes through the four-way switching valve (22) and then is sucked into the compressor (21) and compressed. The indoor unit (12) supplies the air cooled in the indoor heat exchanger (25) to the room.

<Heating operation>
The air conditioner (10) performs heating operation. During the heating operation, the four-way selector valve (22) is set to the second state. During the heating operation, the outdoor fan (15) and the indoor fan (16) are operated.

  In the refrigerant circuit (20), a refrigeration cycle is performed. Specifically, the refrigerant discharged from the compressor (21) flows into the indoor heat exchanger (25) through the four-way switching valve (22), dissipates heat to the indoor air, and condenses. The refrigerant flowing out of the indoor heat exchanger (25) expands when passing through the expansion valve (24), then flows into the outdoor heat exchanger (23), absorbs heat from the outdoor air, and evaporates. The refrigerant that has flowed out of the outdoor heat exchanger (23) passes through the four-way switching valve (22) and then is sucked into the compressor (21) and compressed. The indoor unit (12) supplies the air heated in the indoor heat exchanger (25) to the room.

<Defrosting operation>
As described above, the outdoor heat exchanger (23) functions as an evaporator during the heating operation. Under operating conditions where the outside air temperature is low, the evaporation temperature of the refrigerant in the outdoor heat exchanger (23) may be lower than 0 ° C. In this case, the moisture in the outdoor air becomes frost and the outdoor heat exchanger (23 ). Therefore, the air conditioner (10) performs the defrosting operation every time the duration time of the heating operation reaches a predetermined value (for example, several tens of minutes).

  When starting the defrosting operation, the four-way switching valve (22) is switched from the second state to the first state, and the outdoor fan (15) and the indoor fan (16) are stopped. In the refrigerant circuit (20) during the defrosting operation, the high-temperature refrigerant discharged from the compressor (21) is supplied to the outdoor heat exchanger (23). In the outdoor heat exchanger (23), the frost adhering to the surface is heated and melted by the refrigerant. The refrigerant that has radiated heat in the outdoor heat exchanger (23) sequentially passes through the expansion valve (24) and the indoor heat exchanger (25), and is then sucked into the compressor (21) and compressed. When the defrosting operation is completed, the heating operation is resumed. That is, the four-way switching valve (22) is switched from the first state to the second state, and the operation of the outdoor fan (15) and the indoor fan (16) is resumed.

-Heat exchanger of Embodiment 1-
The heat exchanger (30) of the present embodiment constituting the outdoor heat exchanger (23) of the air conditioner (10) will be described with reference to FIGS.

<Overall configuration of heat exchanger>
As shown in FIGS. 2 and 3, the heat exchanger (30) of the present embodiment includes one first header collecting pipe (31), one second header collecting pipe (32), and many flat tubes. (33) and a large number of fins (36). The first header collecting pipe (31), the second header collecting pipe (32), the flat pipe (33), and the fin (36) are all made of an aluminum alloy and are joined to each other by brazing. .

  Each of the first header collecting pipe (31) and the second header collecting pipe (32) is formed in an elongated hollow cylindrical shape whose both ends are closed. In FIG. 3, the first header collecting pipe (31) is arranged at the left end of the heat exchanger (30), and the second header collecting pipe (32) is arranged at the right end of the heat exchanger (30). Has been. That is, the first header collecting pipe (31) and the second header collecting pipe (32) are installed in such a posture that their respective axial directions are in the vertical direction.

  As shown in FIG. 4, the flat tube (33) is a heat transfer tube whose cross-sectional shape is a flat oval or a rounded rectangle. In the heat exchanger (30), the plurality of flat tubes (33) are arranged in a posture in which the extending direction is the left-right direction and the flat side surfaces face each other. In addition, the plurality of flat tubes (33) are arranged side by side at regular intervals. Each flat tube (33) has one end inserted into the first header collecting tube (31) and the other end inserted into the second header collecting tube (32).

  The fins (36) are plate-like fins and are arranged at regular intervals in the extending direction of the flat tube (33). That is, the fin (36) is disposed so as to be substantially orthogonal to the extending direction of the flat tube (33). Although mentioned later in detail, in each fin (36), the part located between the flat pipes (33) adjacent up and down comprises the heat-transfer part (70).

  As shown in FIG. 3, in the heat exchanger (30), the space between the flat tubes (33) adjacent to each other in the vertical direction is divided into a plurality of ventilation paths (40) by the heat transfer section (70) of the fin (36). Partitioned. The heat exchanger (30) exchanges heat between the refrigerant flowing through the fluid passage (34) of the flat tube (33) and the air flowing through the ventilation passage (40).

  As described above, the heat exchanger (30) includes a plurality of flat tubes (33) arranged vertically so that the flat side faces each other, and a plate-like shape extending from one to the other of the adjacent flat tubes (33). A plurality of fins (36) having a heat transfer section (70). Between the adjacent flat tubes (33), a plurality of heat transfer portions (70) are arranged in the extending direction of the flat tubes (33). And in this heat exchanger (30), the air which flows between adjacent heat-transfer parts (70) heat-exchanges with the fluid which flows through the inside of each flat tube (33).

<Fin configuration>
As shown in FIG. 4, the fin (36) is a vertically long plate-like fin formed by pressing a metal plate. The thickness of the fin (36) is approximately 0.1 mm.

  The fin (36) is formed with a number of elongated notches (45) extending from the front edge (38) of the fin (36) in the width direction of the fin (36) (that is, the air passage direction). In the fin (36), a large number of notches (45) are formed at regular intervals in the longitudinal direction (vertical direction) of the fin (36). The notch (45) is a notch for inserting the flat tube (33). The portion closer to the lee of the notch (45) constitutes the tube insertion portion (46). The tube insertion portion (46) has a vertical width substantially equal to the thickness of the flat tube (33) and a length substantially equal to the width of the flat tube (33).

  The flat tube (33) is inserted into the tube insertion portion (46) of the fin (36) and joined to the peripheral portion of the tube insertion portion (46) by brazing. That is, the flat tube (33) is sandwiched between the peripheral portions of the tube insertion portion (46) which is a part of the notch (45).

  In the fin (36), the portion between the upper and lower cutouts (45) constitutes the heat transfer section (70). That is, the single fin (36) includes a plurality of heat transfer portions (70) that are adjacent to each other vertically with the flat tube (33) interposed therebetween. In the heat exchanger (30) of the present embodiment, the heat transfer section (70) of the fin (36) is disposed between the flat tubes (33) arranged vertically.

  Each heat transfer section (70) of the fin (36) includes an intermediate section (71), a wind upper end section (72), and a wind lower end section (73). In each heat transfer section (70), a portion overlapping with the upper and lower flat tubes (33) (that is, a portion located directly above or below the upper and lower flat tubes (33)) is an intermediate portion (71 ). Moreover, in each heat transfer part (70), the part located on the windward side than the intermediate part (71) (that is, the part protruding to the windward side from the flat tube (33)) is the wind upper end part (72), A portion located on the leeward side from the intermediate portion (71) (that is, a portion protruding to the leeward side from the flat tube (33)) is the leeward end portion (73).

  In the fin (36), the wind lower ends (73) of the heat transfer portions (70) adjacent to each other in the vertical direction are connected to each other via the connecting plate portion (75). The fin (36) is formed with a water guiding rib (49). The water guiding rib (49) is a long and narrow groove extending vertically along the rear edge (39) of the fin (36). The water guiding rib (49) is formed from the upper end to the lower end of the fin (36).

  As shown in FIG. 5, each heat transfer part (70) of the fin (36) is provided with a plurality of bulge parts (81 to 83) and a plurality of louvers (50, 60). In each heat transfer part (70), the bulging part (81-83) is provided near the leeward side, and the louvers (50, 60) are provided near the leeward side. That is, in each heat transfer section (70), the louver (50, 60) is provided only in the part closer to the leeward side, and the bulging part (81-83) is provided in the part on the windward side than all the louvers (50, 60) Is provided. The numbers of the bulging portions (81 to 83) and louvers (50, 60) shown below are merely examples.

  In each heat transfer part (70) of the fin (36), three bulging parts (81 to 83) are provided in a portion extending from the wind upper end part (72) to the windward side of the intermediate part (71). ing. The three bulging portions (81 to 83) are arranged in the air passage direction (that is, the direction from the front edge (38) to the rear edge (39) of the fin (36)). Each bulge part (81-83) is formed in the mountain shape by making the heat-transfer part (70) bulge toward a ventilation path (40). Details of the bulging portions (81 to 83) will be described later.

  In each heat transfer section (70) of the fin (36), a plurality of louvers (50, 60) extending in the vertical direction are provided on the leeward part and the lee end part (73) of the intermediate part (71). ing. Moreover, in each heat-transfer part (70), several louvers (50,60) are located in a line with the passage direction of air. Details of the louvers (50, 60) will be described later.

  The fin (36) is formed with a tab (48) for maintaining a distance from the adjacent fin (36). As shown in FIG. 5B, the tab (48) is a rectangular piece formed by cutting and raising the fin (36). As shown in FIG. 7, the tabs (48) hold the gap between the fins (36) by the protrusions coming into contact with the adjacent fins (36). As shown in FIG. 5 (A), one tab (48) is provided on each of the upper edge and the lower edge of the windward end (72) of the heat transfer section (70). One tab (48) is also provided on each connecting plate (75).

<Arrangement and shape of bulges>
The arrangement and shape of the bulging portions (81 to 83) formed on the fin (36) will be described in detail. Note that “right” and “left” used in this description mean directions when the fin (36) is viewed from the windward side (that is, the front side of the heat exchanger (30)).

  As shown in FIG. 5, each heat transfer part (70) of the fin (36) has a first bulge part (81), a second bulge part (82), and a third bulge part (83). Is provided. Each bulging part (81-83) is formed by plastically deforming the heat transfer part (70) of the fin (36) by pressing or the like, and bulges to the right side of the heat transfer part (70). (See FIG. 6 (A)). Note that the bulging direction of the heat transfer section (70) shown here is merely an example. That is, each bulge part (81-83) may bulge to the left side of the heat-transfer part (70).

  Each bulge part (81-83) is extended in the direction which cross | intersects the passage direction of the air in a ventilation path (40). Specifically, each bulging part (81-83) is formed in a mountain shape in which the ridgeline (81a, 82a, 83a) is substantially parallel to the front edge (38) of the fin (36). That is, the ridgelines (81a, 82a, 83a) of the bulging portions (81 to 83) intersect with the air passage direction. In each bulging part (81-83), from the front end (namely, end part on the windward side) to the inclined part from the ridgeline (81a, 82a, 83a) and the rear end (namely, end part on the leeward side) Each of the inclined portions over the ridgelines (81a, 82a, 83a) is a slope portion (81b, 82b, 83b). Moreover, in each bulging part (81-83), the part from the upper end (81d, 82d, 83d) to the upper end of the slope part (81b, 82b, 83b), and the slope from the lower end (81e, 82e, 83e) Each of the parts extending to the lower ends of the parts (81b, 82b, 83b) is a side part (81c, 82c, 83c).

  In each heat transfer part (70) of the fin (36), the first bulge part (81), the second bulge part (82), and the third bulge part (83) are in the air passage direction (that is, The fins (36) are arranged in order from the front edge (38) to the rear edge (39). In each heat transfer section (70), the three bulging sections (81 to 83) are provided across the windward end of the windward end section (72) and the intermediate section (71). Specifically, the front end of the first bulging portion (81) is close to the front edge (38) of the fin (36). The rear end of the first bulge portion (81) continues to the front end of the second bulge portion (82), and the rear end of the second bulge portion (82) continues to the front end of the third bulge portion (83). doing. The rear end of the third bulge portion (83) is located on the leeward side of the center of the heat transfer portion (70) in the air passage direction. That is, the distance L1 from the front edge (38) of the fin (36) to the rear end of the third bulge portion (83) is the distance L from the front edge (38) of the fin (36) to the rear edge (39). Longer than half (L1> L / 2).

  As shown in FIG. 5A, the width W1 in the air passage direction of the first bulge portion (81) is equal to the width W2 of the second bulge portion (82) in the air passage direction and the third bulge portion. The width of the part (83) is wider than either of the widths W3 in the air passing direction. The width W2 of the second bulge portion (82) is equal to the width W3 of the third bulge portion (83). That is, the relationship between the widths of the bulging portions (81 to 83) is W1> W2 = W3. On the other hand, as shown in FIG. 5B, the height H1 of the first bulging portion (81) in the bulging direction is lower than the height H2 of the second bulging portion (82) in the bulging direction. The height H2 of the bulging part (82) in the bulging direction is lower than the height H3 of the third bulging part (83) in the bulging direction (H1 <H2 <H3).

  The upper end (81d) of the first bulge portion (81) is inclined so that the leeward side is upward. On the other hand, the upper end (82d) of the second bulge portion (82) and the upper end (83d) of the third bulge portion (83) are substantially orthogonal to the front edge (38) of the fin (36). . In each heat transfer section (70), the distance from the upper end of the heat transfer section (70) to the upper end (83d) of the third bulge section (83) is the distance from the upper end of the heat transfer section (70). 2 It is shorter than the distance to the upper end (82d) of the bulging portion (82).

  The lower end (81e, 82e, 83e) of each bulging part (81-83) is inclined so that the leeward side is downward. Further, the lower ends (81e, 82e, 83e) of the three bulging portions (81 to 83) are arranged on one straight line inclined so as to be lower toward the leeward side. Accordingly, in each heat transfer section (70), the distance D2 from the lower end of the heat transfer section (70) to the leeward end of the lower end (83e) of the third bulge section (83) is the heat transfer section. It is shorter than the distance D1 from the lower end of (70) to the windward end of the lower end (81e) of the first bulge portion (81). Moreover, in each heat-transfer part (70), the distance from the lower end of the heat-transfer part (70) to the lower end (81e, 82e, 83e) of a bulging part (81-83) becomes short gradually as it goes to the leeward side. It has become.

<Arrangement and shape of louvers>
The arrangement and shape of the louvers (50, 60) formed on the fin (36) will be described in detail. Note that “right” and “left” used in this description mean directions when the fin (36) is viewed from the windward side (that is, the front side of the heat exchanger (30)).

  As shown in FIG. 5, a plurality of louvers (50, 60) are provided side by side in the air passage direction in each heat transfer section (70) of the fin (36). In the heat transfer section (70), the group of louvers provided in the intermediate section (71) constitutes the windward louver (50), and the group of louvers provided in the leeward end section (73) is the leeward louver (60). ).

  Each louver (50, 60) is formed by making a plurality of slit-like cuts in the heat transfer section (70) and plastically deforming so as to twist a portion between adjacent cuts. The longitudinal direction of each louver (50, 60) is substantially parallel to the front edge (38) of the heat transfer section (70) (that is, the vertical direction). That is, the longitudinal direction of each louver (50, 60) is a direction intersecting with the air passing direction. Each louver (50, 60) has the same length.

  In each heat transfer section (70), the distance from the lower end of the heat transfer section (70) to the lower end of each louver (50, 60) is the third bulging section (83 from the lower end of the heat transfer section (70). ) Is substantially equal to the distance D2 to the leeward end of the lower end (83e). In each heat transfer section (70), the distance from the upper end of the heat transfer section (70) to the upper end of each louver (50, 60) is the third bulge section from the upper end of the heat transfer section (70). It is substantially equal to the distance to the upper end (83d) of (83).

  As shown in FIG. 5B, each louver (50, 60) is inclined with respect to a flat portion around the louver. Further, the leeward louver (50) and the leeward louver (60) are inclined in directions opposite to each other. The windward louver (50) has a cut-and-raised end (53) on the windward side bulging to the left and a cut-and-raised end (53) on the leeward side to the right. That is, in the windward louver (50), the cut-and-raised end (53) on the leeward side protrudes in the same direction as the bulging direction of the third bulging portion (83). On the other hand, the leeward louver (60) has a cut-and-raised end (63) on the leeward side that bulges to the right and a leeward-side cut and raised end (63) that bulges to the left.

  As shown in FIGS. 6B and 6C, the cut-and-raised ends (53, 63) of the windward louver (50) and the leeward louver (60) are the main edge (54, 64) and the upper edge. It is comprised by the part (55,65) and the lower side edge part (56,66). The extending direction of the main edges (54, 64) is substantially parallel to the extending direction of the front edge (38) of the heat transfer section (70). The upper edge portion (55, 65) extends from the upper end of the main edge portion (54, 64) to the upper end of the louver (50, 60), and is inclined with respect to the main edge portion (54, 64). Yes. The lower edge portion (56,66) extends from the lower end of the main edge portion (54,64) to the lower end of the louver (50,60), and is inclined with respect to the main edge portion (54,64). ing.

  As shown in FIG. 6B, in the windward louver (50), the inclination angle of the upper edge (55) with respect to the main edge (54) is θ1, and the main edge of the lower edge (56). The inclination angle with respect to (54) is θ2. As shown in FIG. 5A, in some upwind louvers (50a) located closer to the windward, the inclination angle θ2 of the lower edge (56) is more than the inclination angle θ1 of the upper edge (55). Is also small (θ2 <θ1). Therefore, in this windward louver (50a), the lower edge (56) is longer than the upper edge (55). This windward louver (50a) is an asymmetric louver in which the shape of the cut-and-raised end (53) is asymmetric in the vertical direction. On the other hand, in some upwind louvers (50b) located closer to the lee, the inclination angle θ2 of the lower edge (56) is equal to the inclination angle θ1 of the upper edge (55). This windward louver (50b) is a symmetric louver in which the shape of the cut and raised end (53) is vertically symmetrical.

  As shown in FIG. 6C, in the leeward louver (60), the inclination angle of the upper edge (65) with respect to the main edge (64) is θ3, and the main edge of the lower edge (66) The inclination angle with respect to (64) is θ4. As shown in FIG. 5A, in all leeward louvers (60), the inclination angle θ4 of the lower edge (66) is equal to the inclination angle θ3 of the upper edge (65). This leeward louver (60) is a symmetrical louver in which the shape of the cut and raised end (63) is vertically symmetrical.

-Air flow in heat exchanger-
The flow of air passing through the heat exchanger (30) will be described with reference to FIG.

  In the heat exchanger (30), the ventilation path (40) is formed between the heat transfer parts (70) adjacent to each other in the extending direction of the flat tube (33), and air flows through the ventilation path (40). On the other hand, the heat transfer part (70) of each fin (36) has a bulge part (in this embodiment, a right side when viewed from the front edge (38) side of the fin (36)) ( 81-83) are formed. Therefore, the part which faces the bulging part (81-83) of a heat-transfer part (70) among ventilation paths (40) becomes a shape meandering along a bulging part (81-83).

  The air flowing into the ventilation path (40) from the front edge (38) side of the fin (36) flows while the meandering portion of the ventilation path (40) hits the bulging portion (81-83). For this reason, the air flow in the ventilation path (40) hits the bulging portion (81 to 83) and is disturbed by changing its direction. As a result, the heat transfer between the air flowing through the ventilation path (40) and the heat transfer section (70) is promoted as compared to the case where the heat transfer section (70) is a flat plate without unevenness.

  The air that has flown over the bulging portions (81 to 83) in the ventilation path (40) hits the windward louver (50). In that case, the air which got over the ridgeline (83a) of the 3rd bulge part (83) flows along the slope part (83b) of a leeward side, and hits an upwind louver (50) after that. The windward louver (50) has a cut-and-raised end (53) on the leeward side protruding in the bulging direction of the third bulging portion (83). Therefore, when the air flowing along the leeward slope part (83b) of the third bulge part (83) hits the windward louver (50), the flow direction is changed by the windward louver (50). Is done. For this reason, the flow of air in the ventilation path (40) is disturbed, and heat transfer between the air and the heat transfer section (70) is promoted.

  As described above, the louvers (50, 60) are formed by cutting up the heat transfer section (70). For this reason, in the heat exchanger (30), air is exchanged between the adjacent ventilation paths (40) across the heat transfer section (70), and the air flow in the ventilation path (40) is greatly disturbed. As a result, compared with the case where the heat transfer part (70) is a flat plate without unevenness, or when only the bulging part is formed on the heat transfer part (70), the air flowing through the ventilation path (40) Heat transfer between the heat section (70) is promoted.

-State of frost and drain water in fins-
As described above, the heat exchanger (30) of the present embodiment constitutes the outdoor heat exchanger (23) of the air conditioner (10). The air conditioner (10) performs a heating operation. However, in an operation state where the evaporation temperature of the refrigerant in the outdoor heat exchanger (23) is lower than 0 ° C., moisture in the outdoor air becomes frost and the outdoor heat exchanger (23 ). For this reason, the air conditioner (10) performs a defrosting operation for melting frost attached to the outdoor heat exchanger (23). During the defrosting operation, drain water is generated by melting of the frost.

<Frost adhesion to fins>
The process in which frost adheres to the heat exchanger (30) constituting the outdoor heat exchanger (23) will be described. The air flowing into the ventilation path (40) of the heat exchanger (30) exchanges heat with the refrigerant flowing through the fluid passage (34) of the flat tube (33) via the heat transfer section (70) of the fin (36). . And in the state in which the surface temperature of the heat-transfer part (70) is less than 0 degreeC, the water | moisture content in air freezes and becomes frost and adheres to the surface of a heat-transfer part (70).

  In general, the effect of disturbing the flow of air is that the louver (50, 60) formed by cutting and raising the heat transfer section (70) is expanded without cutting the heat transfer section (70). It is larger than the bulging part (81-83). Therefore, normally, the louver (50, 60) is also larger than the bulging portion (81-83) in terms of the heat transfer promoting effect.

  On the other hand, in each heat transfer section (70) of the fin (36), a louver (50, 60) having a relatively high heat transfer promoting effect is formed on the leeward side, which is located on the leeward side of the louver (50, 60). The bulging part (81-83) with a comparatively low heat transfer promotion effect is formed in the part. For this reason, compared with the case where louvers are formed over the entire heat transfer section (70), the amount of frost adhering to the windward portion of the heat transfer section (70) is reduced, and the heat transfer section The amount of frost attached to the leeward part of (70) increases. Accordingly, in each heat transfer section (70) of the fin (36), the difference between the amount of frost adhering to the leeward portion and the amount of frost adhering to the leeward portion is reduced.

  In the state where the surface temperature of the heat transfer section (70) is less than 0 ° C., moisture in the air flowing through the ventilation path (40) gradually becomes frost and adheres to the heat transfer section (70). For this reason, the absolute humidity of the air flowing through the ventilation path (40) gradually decreases toward the leeward side. The air that has reached the louver (50, 60), which has a relatively high heat transfer promoting effect, has a relatively low absolute humidity. For this reason, in each heat-transfer part (70) of a fin (36), the quantity of the frost which adheres to the part in which the louver (50,60) was provided does not increase too much.

  As above-mentioned, the ventilation path (40) formed of the heat-transfer part (70) provided with the bulging part (81-83) becomes the shape meandered along the bulging part (81-83). . And if the height of the bulging part in the bulging direction is the same, the wider the width of the bulging part in the air passage direction, the less the change in the flow direction of the air flowing along the bulging part. Further, if the width of the bulging portion in the air passage direction is the same, the lower the height of the bulging portion in the bulging direction, the less the change in the flow direction of the air flowing along the bulging portion. When the change in the flow direction of the air flowing along the bulging portion decreases, the effect of promoting heat transfer by the bulging portion decreases. On the other hand, the temperature difference between the air flowing through the ventilation path (40) and the heat transfer section (70) is the largest at the inlet of the ventilation path (40) and gradually decreases toward the lee.

  In each heat transfer portion (70) of the present embodiment, the width W1 of the first bulge portion (81) is greater than the width W2 of the second bulge portion (82) and the width W3 of the third bulge portion (83). Is also getting wider. In each heat transfer section (70), the height H1 of the first bulge section (81) is the same as the height H2 of the second bulge section (82) and the height H3 of the third bulge section (83). Is lower than. That is, in each heat transfer part (70) of the fin (36), the heat transfer promoting effect is provided at a position on the windward side where the temperature difference between the air flowing through the ventilation path (40) and the heat transfer part (70) is relatively large. A relatively small first bulging portion (81) is provided. For this reason, in each heat-transfer part (70) of a fin (36), the quantity of the frost adhering to a windward near part is suppressed reliably.

  Thus, in the heat exchanger (30) of this embodiment, frost adheres not only to the windward portion of the fin (36) but also to the windward portion thereof. For this reason, the amount of frost adhering to the heat exchanger (30) at the time when it is necessary to perform the defrosting operation is greater in the heat exchanger (30) of the present embodiment than in the heat transfer section. More than the conventional heat exchanger provided with louvers as a whole. Therefore, compared with the air conditioner which has the outdoor heat exchanger comprised by the conventional heat exchanger, the air conditioner which has the outdoor heat exchanger (23) comprised by the heat exchanger (30) of this embodiment In (10), the time interval from the end of the defrosting operation to the start of the next defrosting operation becomes longer, and as a result, the duration of the heating operation becomes longer.

<State of frost and drain water during defrosting operation>
The state of frost and drain water in the heat exchanger (30) during the defrosting operation of the air conditioner (10) will be described. During the defrosting operation, the frost attached to the heat exchanger (30) is melted to become drain water, and the generated drain water is discharged from the heat exchanger (30).

  In each heat transfer section (70) of the fin (36), when the frost adhering to the heat transfer section (70) melts, the generated drain water flows downward. At that time, the frost adhering to the wind upper end portion (72) of the heat transfer section (70) becomes drain water and falls downward from the wind upper end portion (72). On the other hand, the frost adhering to the intermediate part (71) of the heat transfer part (70) becomes drain water and accumulates on the flat side surface of the flat tube (33).

  In each heat transfer part (70) of the fin (36), the lower end (81e, 82e, 83e) of each bulge part (81-83) is inclined, and the bulge part extends from the lower end of the heat transfer part (70). The distance to the lower ends (81e, 82e, 83e) of (81-83) is gradually shortened toward the leeward side. Accordingly, in each heat transfer section (70), the distance from the flat tube (33) positioned below to the lower end (81e, 82e, 83e) of the bulging section (81-83) gradually increases toward the leeward side. It gets narrower. For this reason, the drain water that has flowed down from the bulging portion (81 to 83) and accumulated on the flat tube (33) is removed from the flat tube (33) to the lower end (81e, 82e, 83e) of the bulging portion (81 to 83). To the leeward side where the distance to) is short. That is, during the defrosting operation, the outdoor fan (15) is stopped, and the drain water moves to the leeward side even though the upper surface of the flat tube (33) is substantially horizontal.

  Thus, in the heat exchanger (30) of the present embodiment, the drain water generated during the defrosting operation is surely discharged to the leeward side. For this reason, the amount of drain water remaining on the surface of the heat transfer section (70) at the end of the defrosting operation is reduced. If drain water remains on the surface of the heat transfer section (70), the drain water remaining after the resumption of heating operation is frozen, and the time until it is necessary to perform the defrosting operation again is shortened. . Therefore, compared with the air conditioner which has the outdoor heat exchanger comprised by the conventional heat exchanger, the air conditioner which has the outdoor heat exchanger (23) comprised by the heat exchanger (30) of this embodiment In (10), the elapsed time from the end of the defrosting operation to the start of the next defrosting operation (that is, the duration of the heating operation) becomes longer.

  By the way, as mentioned above, in the heat exchanger (30) of this embodiment, some windward louvers (50a) are asymmetric louvers. That is, in the windward louver (50a), the inclination angle θ2 of the lower edge (56) is smaller than the inclination angle θ1 of the upper edge (55) (see FIG. 6B). . For this reason, as shown in FIG. 8, between the windward louvers (50a) adjacent to each other in the air passage direction, gaps formed between the lower edge portions (56) are separated from each other on the upper edge. It becomes elongated compared to the gap formed between the portions (55).

  In general, a relatively large capillary force acts on a liquid present in a relatively narrow gap. Further, the capillary force acting on the liquid increases as the gap becomes narrower. On the other hand, as shown in FIG. 8, in a state in which drain water enters between the cut and raised ends (53) of the windward louvers (50a) adjacent in the air passage direction, the lower side in contact with the lower end of the drain water The interval between the edge portions (56) is narrower than the interval between the main edge portions (54) in contact with the upper end of the drain water. Accordingly, the downward capillary force acting on the drain water is stronger than the upward capillary force, and the drain water is drawn to the lower edge (56) side (ie, the lower side).

  The windward louver (50a), which is an asymmetric louver, has a relatively long lower edge (56). For this reason, the area | region where the space | interval of the cut-and-raised end (53) is narrow is expanded between the windward louvers (50a) adjacent in the air passage direction. As a result, the region where the downward capillary force acting on the drain water becomes stronger than the upward capillary force is expanded, and the possibility that the drain water moves downward due to capillary action is increased.

  In this way, the drain water that has entered between the cut-and-raised ends (53) of the windward louvers (50a) adjacent to each other in the air passage direction passes into the narrow and narrow gap between the lower edges (56). It is drawn by capillary action. That is, this drain water flows downward not only by the action of gravity but also by capillary action. Therefore, drain water generated in the vicinity of the windward louver (50a) during the defrosting operation is quickly discharged downward, and the cut-and-raised ends (53) of the windward louvers (50a) adjacent to each other in the air passing direction are It becomes difficult to be held in between.

  In each heat transfer part (70) of the fin (36), an intermediate part closer to the flat tube (33) than the leeward louver (60) provided at the lower wind end (73) far from the flat tube (33) The windward louver (50) provided in (71) has more frost attached. Further, among the windward louvers (50), the windward louver (50a) located on the windward side has a larger amount of frost attached than the windward louver (50b) located on the windward side. . For this reason, the amount of drain water generated during the defrosting operation increases as the windward louver (50) is located on the windward side.

  On the other hand, in each heat transfer section (70) of the fin (36) of the present embodiment, a part of the windward louvers (50a) located closer to the windward are asymmetric louvers. That is, in each heat transfer section (70), the windward louver (50a) closer to the windward, where the amount of drain water generated during the defrosting operation increases, is an asymmetric louver that hardly holds the drain water. Therefore, even if some upwind louvers (50a) are asymmetric louvers, the amount of drain water remaining on the surface of the heat transfer section (70) at the end of the defrosting operation is reduced.

-Effect of Embodiment 1-
As described above, according to the heat exchanger (30) of the present embodiment, during the heating operation of the air conditioner (10), only the portion near the windward side of the heat transfer section (70) of the fin (36). In addition, frost can be attached to the part closer to the lee. Therefore, if the outdoor heat exchanger (23) of the air conditioner (10) is configured by the heat exchanger (30) of this embodiment, the duration of the heating operation can be extended.

  Moreover, according to the heat exchanger (30) of this embodiment, the amount of drain water remaining on the surface of the heat transfer section (70) at the end of the defrosting operation can be reduced. The drain water remaining on the surface of the heat transfer section (70) freezes after resuming the heating operation. For this reason, if the drain water remaining on the surface of the heat transfer section (70) decreases, the time until the next defrosting operation becomes necessary becomes longer. Therefore, if the outdoor heat exchanger (23) of the air conditioner (10) is configured by the heat exchanger (30) of this embodiment, the duration of the heating operation can be extended.

  Thus, if the outdoor heat exchanger (23) of the air conditioner (10) is configured by the heat exchanger (30) of the present embodiment, the duration of the heating operation can be extended, and further, the defrosting operation is performed. Can be shortened. Therefore, if the outdoor heat exchanger (23) of the air conditioner (10) is configured by the heat exchanger (30) of the present embodiment, the temporal average value of the heating capacity of the air conditioner (10) (that is, The substantial heating capacity of the air conditioner (10) can be increased.

<< Embodiment 2 of the Invention >>
A second embodiment of the present invention will be described. Similarly to the heat exchanger (30) of the first embodiment, the heat exchanger (30) of the second embodiment constitutes an outdoor heat exchanger (23) of the air conditioner (10). Below, the heat exchanger (30) of this embodiment is demonstrated, referring FIGS. 9-12 suitably.

<Overall configuration of heat exchanger>
As shown in FIGS. 9 and 10, the heat exchanger (30) of the present embodiment includes one first header collecting pipe (31), one second header collecting pipe (32), and many flat tubes. (33) and a large number of fins (35). The first header collecting pipe (31), the second header collecting pipe (32), the flat pipe (33), and the fin (35) are all made of an aluminum alloy and are joined to each other by brazing. .

  The configuration and arrangement of the first header collecting pipe (31), the second header collecting pipe (32), and the flat pipe (33) are the same as those of the heat exchanger (30) of the first embodiment. That is, the first header collecting pipe (31) and the second header collecting pipe (32) are both formed in a vertically long cylindrical shape, one at the left end of the heat exchanger (30) and the other at the heat exchanger (30). 30) are arranged at the right end of each. On the other hand, the flat tube (33) is a heat transfer tube having a flat cross-sectional shape, and is arranged side by side in a posture in which the flat side surfaces face each other. Each flat tube (33) has a plurality of fluid passages (34). One end of each of the flat tubes (33) arranged in the vertical direction is inserted into the first header collecting pipe (31), and the other end is inserted into the second header collecting pipe (32).

  A fin (35) is a corrugated fin meandering up and down, and is arrange | positioned between the flat pipes (33) adjacent up and down. As will be described in detail later, a plurality of heat transfer sections (70) and intermediate plate sections (41) are formed on the fin (35). Each fin (35) has its intermediate plate (41) joined to the flat tube (33) by brazing.

  As shown in FIG. 10, in the heat exchanger (30), the space between the upper and lower flat tubes (33) is divided into a plurality of ventilation paths (40) by the heat transfer section (70) of the fin (35). Partitioned. The heat exchanger (30) exchanges heat between the refrigerant flowing through the fluid passage (34) of the flat tube (33) and the air flowing through the ventilation passage (40).

  As described above, the heat exchanger (30) includes a plurality of flat tubes (33) arranged vertically so that the flat side faces each other, and a plate-like shape extending from one to the other of the adjacent flat tubes (33). A plurality of fins (35) having a heat transfer section (70). Between the adjacent flat tubes (33), a plurality of heat transfer portions (70) are arranged in the extending direction of the flat tubes (33). And in this heat exchanger (30), the air which flows between adjacent heat-transfer parts (70) heat-exchanges with the fluid which flows through the inside of each flat tube (33).

<Fin configuration>
As shown in FIG. 12, the fin (35) is a corrugated fin formed by bending a metal plate having a constant width, and has a shape meandering up and down. In the fin (35), the heat transfer section (70) and the intermediate plate section (41) are alternately formed along the extending direction of the flat tube (33). That is, the fin (35) is provided with a plurality of heat transfer portions (70) arranged between adjacent flat tubes (33) and arranged in the extending direction of the flat tubes (33). The fin (35) is provided with a projecting plate portion (42). In addition, in FIG. 12, illustration of the bulging part (81-83) mentioned later and louvers (50,60) is abbreviate | omitted.

  The heat transfer portion (70) is a plate-like portion extending from one side of the flat tube (33) adjacent to the top to the bottom. In the heat transfer section (70), the end on the leeward side is the front edge (38), and the end on the leeward side is the rear edge (39). The intermediate plate portion (41) is a plate-like portion along the flat side surface of the flat tube (33) and is continuous with the upper ends or lower ends of the heat transfer portions (70) adjacent to the left and right. The angle formed by the heat transfer section (70) and the intermediate plate section (41) is substantially a right angle.

  As shown in FIG. 11, each heat transfer section (70) of the fin (35) includes an intermediate section (71), a wind upper end section (72), and a wind lower end section (73). In each heat transfer section (70), a portion overlapping with the upper and lower flat tubes (33) (that is, a portion located directly above or below the upper and lower flat tubes (33)) is an intermediate portion (71 ). Moreover, in each heat transfer part (70), the part located on the windward side than the intermediate part (71) (that is, the part protruding to the windward side from the flat tube (33)) is the wind upper end part (72), A portion located on the leeward side from the intermediate portion (71) (that is, a portion protruding to the leeward side from the flat tube (33)) is the leeward end portion (73).

  Two protruding plate portions (42) are provided in each heat transfer portion (70). The projecting plate portion (42) is formed in a trapezoidal plate shape that is continuous with the lower wind end portion (73). In each heat transfer section (70), one protruding plate (42) protrudes upward from the upper end of the wind lower end (73), and the other protruding plate (42) extends downward from the lower end of the wind lower end (73). Protruding to In the heat exchanger (30), the projecting plate portions (42) of the fins (35) that are adjacent vertically with the flat tube (33) in between are in contact with each other.

  As shown in FIG. 11, each heat transfer section (70) of the fin (35) is provided with a plurality of bulge sections (81 to 83) and a plurality of louvers (50, 60). As with the fins (36) of the first embodiment, each heat transfer section (70) is provided with a bulging section (81 to 83) on the leeward side and louvers (50, 60) on the leeward side. Yes. That is, in each heat transfer section (70), the louver (50, 60) is provided only in the part closer to the leeward side, and the bulging part (81-83) is provided in the part on the windward side than all the louvers (50, 60). Is provided.

<Arrangement and shape of bulges>
The arrangement and shape of the bulging portions (81 to 83) formed on the fin (35) will be described. Note that “right” and “left” used in this description mean directions when the fin (35) is viewed from the windward side (that is, the front side of the heat exchanger (30)).

  As shown in FIG. 11, the arrangement of the bulging portions (81 to 83) and the shapes of the bulging portions (81 to 83) in the heat transfer portions (70) of the fin (35) It is the same as 36). Further, the number of the bulging portions (81 to 83) and the bulging direction shown below are merely examples, which is the same as in the first embodiment.

  Specifically, each bulging part (81 to 83) is formed by causing the heat transfer part (70) to bulge toward the air passage (40), and the ridge lines (81a, 82a, 83a) are formed on the fins (35 ) In the shape of a mountain substantially parallel to the leading edge (38). Each bulge part (81-83) bulges to the right side of the heat transfer part (70).

  In each heat transfer section (70), the three bulging sections (81 to 83) are arranged in the air passage direction (that is, the direction from the front edge (38) to the rear edge (39) of the fin (35)). It is out. In each heat transfer section (70), the three bulging sections (81 to 83) are provided across the windward end of the windward end section (72) and the intermediate section (71).

  In each heat transfer section (70), the width of the first bulge section (81) in the air passage direction is the widest among the three bulge sections (81 to 83). The second bulging portion (82) and the third bulging portion (83) have the same width in the air passage direction. Moreover, in each heat-transfer part (70), the height of the bulging direction of the 1st bulging part (81) is the lowest among the three bulging parts (81-83). The height of the second bulge portion (82) in the bulge direction is lower than the height of the third bulge portion (83) in the bulge direction.

  The lower end (81e, 82e, 83e) of each bulging part (81-83) is inclined so that the leeward side is downward. In each heat transfer section (70), the distance from the lower end of the heat transfer section (70) to the lower ends (81e, 82e, 83e) of the bulging sections (81-83) becomes gradually shorter toward the leeward side.

<Arrangement and shape of louvers>
The arrangement and shape of the louvers (50, 60) formed on the fin (35) will be described. Note that “right” and “left” used in this description mean directions when the fin (35) is viewed from the windward side (that is, the front side of the heat exchanger (30)).

  As shown in FIG. 11, the arrangement of louvers (50, 60) and the shape of each louver (50, 60) in each heat transfer section (70) of the fin (35) are the same as those of the fin (36) of the first embodiment. It is. Also, the number of louvers (50, 60) shown in the figure is merely an example, as in the first embodiment.

  Specifically, in each heat transfer section (70) of the fin (35), a plurality of louvers (50, 60) are placed in the air from the leeward area of the intermediate section (71) to the leeward end section (73). Are arranged side by side in the passing direction. The group of louvers arranged closer to the windward constitutes the windward louver (50), and the group of louvers arranged closer to the leeward constitutes the leeward louver (60). Each louver (50, 60) has the same length.

  In each heat transfer section (70) of the fin (35), a part of the windward louver (50a) located closer to the windward is an asymmetric louver. In each heat transfer section (70), a part of the leeward louvers (50b) and all the leeward louvers (60) located closer to the leeward are symmetrical louvers.

  In each heat transfer section (70) of the fin (35), the windward louver (50) and the leeward louver (60) are inclined in opposite directions. The windward louver (50) has a cut-and-raised end (53) on the windward side bulging to the left and a cut-and-raised end (53) on the leeward side to the right. That is, in the windward louver (50), the cut-and-raised end (53) on the leeward side protrudes in the same direction as the bulging direction of the third bulging portion (83). On the other hand, the leeward louver (60) has a cut-and-raised end (63) on the leeward side that bulges to the right and a leeward-side cut and raised end (63) that bulges to the left.

-Effect of Embodiment 2-
The effect obtained by the heat exchanger (30) of the present embodiment is the same as the effect obtained by the heat exchanger (30) of the first embodiment.

  That is, in the heat exchanger (30) of the present embodiment, as in the first embodiment, the bulging portions (81 to 83) are located on the windward side of the heat transfer portions (70) of the fins (35). Louvers (50, 60) are provided on the leeward side. Moreover, in the heat exchanger (30) of this embodiment, the width | variety of the 1st bulging part (81) located in the windward is the widest similarly to Embodiment 1, and the height of the bulging direction is the same. Is the lowest. Accordingly, in each heat transfer section (70) of the fin (35), the difference between the amount of frost adhering to the leeward portion and the amount of frost adhering to the leeward portion is reduced. As a result, the duration of the heating operation of the air conditioner (10) can be extended, and the substantial heating capacity of the air conditioner (10) can be improved.

  Further, in the heat exchanger (30) of the present embodiment, as in the first embodiment, the lower ends (81e, 82e, 83e) of the bulging portions (81 to 83) are inclined, and further, located closer to the windward side. The upwind louver (50a) is an asymmetric louver. For this reason, the amount of drain water remaining on the surface of the heat transfer section (70) at the end of the defrosting operation can be reduced. As a result, the time interval until the next defrosting operation (that is, the duration of the heating operation) is reduced. Can be extended.

<< Embodiment 3 of the Invention >>
Embodiment 3 of the present invention will be described. The heat exchanger (30) of the third embodiment is obtained by changing the configuration of the fins (36) in the heat exchanger (30) of the first embodiment. Here, the difference between the fin (36) provided in the heat exchanger (30) of the present embodiment and the fin (36) provided in the heat exchanger (30) of the first embodiment will be described.

  As shown in FIGS. 13 and 14, the fin (36) of the present embodiment has a first bulging portion (81) and a second bulging portion (82) as in the fin (36) of the first embodiment. ), A third bulge portion (83), and an upwind louver (50). Moreover, instead of the leeward louver (60), a leeward bulge portion (85) is formed in the fin (36) of the present embodiment. Moreover, the auxiliary bulging part (86), the upper horizontal rib (91), and the lower horizontal rib (92) are added to the fin (36) of this embodiment. Further, the fin (36) of the present embodiment is different from the fin (36) of the first embodiment in the arrangement of the tab (48).

  The first bulging portion (81), the second bulging portion (82), and the third bulging portion (83) formed on the fin (36) of the present embodiment are different in shape and arrangement from the embodiment. 1 and different. In addition, a 1st bulge part (81), a 2nd bulge part (82), and a 3rd bulge part (83) are in order toward the rear edge (39) from the front edge (38) of a fin (36). The arrangement is the same as in the first embodiment.

  In each heat transfer part (70) of the fin (36) of the present embodiment, the first bulge part (81) is formed from the wind upper end part (72) to the intermediate part (71), and the second bulge part. (82) and a third bulging portion (83) are formed in the intermediate portion (71). Each of these bulges (81-83) has its upper end (81d-83d) and lower end (81e-83e) substantially orthogonal to the front edge (38) of the fin (36). Yes. The length of the first bulge portion (81) is shorter than the length of the second bulge portion (82). The length of the second bulge portion (82) is equal to the length of the third bulge portion (83). The width of each bulging part (81-83) becomes wider in the order of the third bulging part (83), the first bulging part (81), and the second bulging part (82) (W3 <W1 <). W2). The heights of the bulging portions (81 to 83) in the bulging direction are equal to each other (H1 = H2 = H3).

  In the fin (36) of the present embodiment, as in the first embodiment, a plurality of louvers (50) are formed on the leeward side of the third bulge portion (83). Similarly to the first embodiment, a part of the louvers (50a) positioned closer to the leeward are asymmetric louvers, and the remaining louvers (50b) positioned closer to the leeward are symmetric louvers. Further, in the fin (36) of the present embodiment, as in the first embodiment, the cut-and-raised end (53) on the leeward side of each louver (50) protrudes in the bulging direction of the third bulging portion (83). (See FIG. 14B).

  As shown in FIG. 14A, the distance L1 from the upper ends of the second bulge portion (82) and the third bulge portion (83) to the upper end of the intermediate portion (71), and the second bulge portion (82 ) And the third bulge part (83), the distance L2 from the lower end of the intermediate part (71), the distance L3 from the upper end of the louver (50a, 50b) to the upper end of the intermediate part (71), The distance L4 from the lower end of 50a, 50b) to the lower end of the intermediate portion (71) is equal to each other.

  In the fin (36) of this embodiment, the tab (48) is formed in the wind upper end part (72) of the heat-transfer part (70) similarly to Embodiment 1. FIG. However, in each heat transfer part (70) of the fin (36) of the present embodiment, one tab (48) is provided on the windward side of the wind upper end part (72) from the first bulge part (81). Is formed. The tab (48) is disposed near the center in the up-down direction of the wind upper end (72). The tab (48) is inclined with respect to the front edge (38) of the fin (36).

  The upper horizontal rib (91) and the lower horizontal rib (92) are formed in each heat transfer section (70) of the fin (36). The upper horizontal rib (91) is formed above the first bulge portion (81), and the lower horizontal rib (92) is formed below the first bulge portion (81). The shape of each horizontal rib (91, 92) is a straight and elongated hook shape extending from the front edge (38) of the fin (36) to the second bulging portion (82). Each horizontal rib (91,92) is formed by bulging the heat transfer section (70) toward the ventilation path (40), like each bulging section (81,82,83,84). Yes. The bulge direction of each horizontal rib (91, 92) is the same as the bulge direction of each bulge part (81-83).

  One auxiliary bulging portion (86) is formed in each heat transfer portion (70) of the fin (36). In each heat transfer section (70), the auxiliary bulging section (86) is disposed on the leeward side of the louver (50). In each heat transfer section (70), the auxiliary bulging section (86) is formed from the intermediate section (71) to the wind lower end section (73).

  The auxiliary bulging portion (86) is formed in a mountain shape by bulging the fin (36). The auxiliary bulging portion (86) extends in a direction crossing the air passage direction in the ventilation path (40). In the fin (36) of the present embodiment, each auxiliary bulging portion (86) bulges to the right as viewed from the front edge (38) of the fin (36). Further, the ridge line (85a) of the auxiliary bulging portion (86) is substantially parallel to the front edge (38) of the fin (36). That is, the ridge line (85a) of the auxiliary bulging portion (86) intersects the air flow direction in the ventilation path (40). Moreover, the lower end of the auxiliary bulging portion (86) is inclined so as to be lower toward the leeward side.

  As shown in FIG. 14B, the height H5 of the auxiliary bulging portion (86) in the bulging direction is lower than the height H3 of the third bulging portion (83) in the bulging direction (H5 <H3). ). Further, as shown in FIG. 14A, the width W5 of the auxiliary bulge portion (86) in the air passage direction is narrower than the width W3 of the third bulge portion (83) in the air passage direction (W5). <W3).

  One leeward bulge portion (85) is formed on the leeward side of each notch portion (45). Each leeward bulge portion (85) includes a connecting plate portion (75), an upper lee end portion (73) on the upper side of the connecting plate portion (75), and a lower wind end on the lower side of the connecting plate portion (75). Part (73).

  The leeward bulge portion (85) is formed in a mountain shape by bulging the fin (36). The leeward side bulging portion (85) extends in a direction intersecting with the air passing direction in the ventilation path (40). In the fin (36) of the present embodiment, each leeward bulge portion (85) bulges to the right as viewed from the front edge (38) of the fin (36). Further, the ridge line (84a) of the leeward bulge portion (85) is substantially parallel to the front edge (38) of the fin (36). That is, the ridgeline (84a) of the leeward bulge portion (85) intersects the air flow direction in the ventilation path (40).

  As shown in FIG. 14B, the height H4 of the leeward bulge portion (85) in the bulge direction is equal to the height H2 of the second bulge portion (82) in the bulge direction (H4 = H2). ). Further, as shown in FIG. 14A, the width W4 of the leeward bulge portion (85) in the air passage direction is equal to the width W2 of the second bulge portion (82) in the air passage direction (W4). = W2).

  In the fin (36) of this embodiment, one tab (48) is formed between adjacent leeward bulges (85). That is, in this fin (36), one tab (48) is provided in the wind lower end part (73) of each heat-transfer part (70).

-Effect of Embodiment 3-
According to the heat exchanger (30) of this embodiment, the same effect as the heat exchanger (30) of Embodiment 1 is acquired.

  That is, in the heat exchanger (30) of the present embodiment, as in the first embodiment, the bulging portions (81 to 83) are provided in the windward side portions of the heat transfer portions (70) of the fins (36). The louver (50) is provided on the leeward side of the bulging portion (81-83). Accordingly, in each heat transfer section (70) of the fin (36), the difference between the amount of frost adhering to the leeward portion and the amount of frost adhering to the leeward portion is reduced. As a result, the duration of the heating operation of the air conditioner (10) can be extended, and the substantial heating capacity of the air conditioner (10) can be improved.

<< Other Embodiments >>
The modification of the heat exchanger (30) of Embodiment 1 and 2 is demonstrated.

-First modification-
In the heat exchanger (30) of each of the above embodiments, all the windward louvers (50) formed in the heat transfer sections (70) of the fins (35, 36) may be asymmetric louvers.

  FIG. 15 shows an application of this modification to the fins (36) of the heat exchanger (30) of the first embodiment. In each heat transfer section (70) of the fin (36) shown in the figure, all the leeward louvers (50) are asymmetric louvers, and all the leeward louvers (60) are symmetric louvers.

-Second modification-
In each heat transfer part (70) of the fins (35, 36) provided in the heat exchanger (30) of each of the embodiments described above, a plurality of the heat transfer parts (72) and the entire intermediate part (71) are provided. The bulging portion (81, 82, 83, 84) may be formed, and the louver (60) may be formed only in the wind lower end portion (73).

  FIG. 16 shows an application of this modification to the fins (36) of the heat exchanger (30) of the first embodiment. In each heat transfer section (70) of the fin (36) shown in the figure, there are four bulge sections (81, 82, 83, 84) are provided side by side in the air passage direction. The fourth bulging portion (84) located on the most leeward side is provided adjacent to the third bulging portion (83). All of the louvers (60) formed on the wind lower end (73) are symmetrical louvers.

-Third modification-
In each heat transfer part (70) of the fins (35, 36) provided in the heat exchanger (30) of each of the embodiments described above, the portion where the louvers (50, 60) are formed faces the ventilation path (40). May bulge out.

  FIG. 17A shows an application of this modification to the fins (36) of the heat exchanger (30) of the first embodiment. In each heat transfer section (70) of the fin (36) shown in the figure, the portion where the louvers (50, 60) are formed bulges in the same direction as the bulge sections (81-83). Specifically, the portion of each heat transfer portion (70) where the windward louver (50) is formed is the same as the slope portion (81b, 82b, 83b) on the windward side of each bulge portion (81-83). Inclined in the direction. Moreover, the part in which the leeward louver (60) was formed among each heat-transfer part (70) is the same direction as the slope part (81b, 82b, 83b) of the leeward side of each bulge part (81-83). Inclined.

《Reference technology》
Reference technology will be described. In this reference technique, in each heat transfer section (70) of the fins (35, 36) provided in the heat exchanger (30) of each of the above embodiments, the inclination direction of each louver (50, 60) is reversed . It is a thing .

FIG. 17B shows the application of this reference technique to the fin (36) of the heat exchanger (30) of the first embodiment. In each heat transfer section (70) of the fin (36) shown in the figure, the windward louver (50) has a cut-and-raised end (63) on the windward side, and a cut-and-raised end (63) on the leeward side. Bulges to the left. That is, in the windward louver (50), the cut-and-raised end (53) on the windward side protrudes in the same direction as the bulging direction of the third bulging portion (83). On the other hand, the leeward louver (60) has a cut-and-raised end (53) on the leeward side bulging to the left and a cut-and-raised end (53) on the leeward side to the right. Note that “right” and “left” used in this description mean directions when the fin (36) is viewed from the windward side (that is, the front side of the heat exchanger (30)).

  In addition, the above embodiment is an essentially preferable illustration, Comprising: It does not intend restrict | limiting the range of this invention, its application thing, or its use.

  As described above, the present invention is useful for a heat exchanger having flat tubes and fins arranged vertically.

10 Air conditioner
20 Refrigerant circuit
30 heat exchanger
33 Flat tube
34 Fluid passage (passage)
35 fins
36 fins
38 Leading edge
40 Ventilation path
41 Intermediate plate
45 Notch
50 Windward louver (louver)
50a Upwind louver (asymmetric louver)
53 Cut edge
54 Main edge
55 Upper edge
56 Lower edge
60 Downward louver (louver)
63 Cut end
64 Main edge
65 Upper edge
66 Lower edge
70 Heat transfer section
72 Wind top
73 Wind end
81 First bulge
82 Second bulge
83 Third bulge
84 Fourth bulge

Claims (13)

A plurality of flat tubes (33) that are arranged vertically so that the side faces are opposed to each other and in which a fluid passage (34) is formed, and a plurality of ventilation channels through which air flows between the adjacent flat tubes (33) A plurality of fins (35, 36) partitioned into (40),
The fins (35, 36) have a plurality of heat transfer portions (70) that are formed in a plate shape extending from one side of the adjacent flat tube (33) to the other and constitute the side wall of the ventilation path (40). A heat exchanger,
Each heat transfer part (70) of the fin (35, 36)
A plurality of louvers (50, 60) formed by cutting and raising the heat transfer section (70);
The bulging part (81-83) which is arrange | positioned in the part above the louver (50,60), and is formed by expanding the said heat-transfer part (70), and extends in the direction which cross | intersects the passage direction of air And
Lulu Ba be positioned in the louvers (50, 60) No Chi upper Symbol bulging portion provided on the heat transfer part (70) of the fin (35, 36) (81 through 83) closer (50) , bulging of projecting bulging direction of the wind under the side of the cut-and-raised end (53) is bulging portion (81 to 83), the windward side of the cut-and-raised end (53) is bulging portion (81 to 83) A heat exchanger that protrudes in the direction opposite to the direction . In claim 1 ,
The cut-and-raised end (53,63) of the louver (50,60) extends from the main edge (54,64) and the upper end of the main edge (54,64) to the upper end of the louver (50,60). An upper edge (55,65) that is an extended portion and is inclined with respect to the main edge (54,64), and a lower end of the louver (50,60) from a lower end of the main edge (54,64) A lower edge (56,66) inclined with respect to the main edge (54,64),
In each heat transfer part (70) of the fin (35, 36), at least a part of the louver (50, 60) has an inclination of the lower edge part (56) with respect to the main edge part (54). The heat exchanger is characterized in that the asymmetric louver is gentler than the inclination of the upper edge (55) with respect to the main edge (54). In claim 2 ,
In each heat transfer section (70) of the fin (35, 36), the louver (50) formed in a portion adjacent to the flat tube (33) is the asymmetric louver. vessel. In any one of Claims 1 thru | or 3 ,
Each heat transfer portion (70) of the fin (35, 36) includes a lee end portion (73) located leeward than the flat tube (33),
In each heat transfer section (70) of the fin (35, 36), the louver (60) is provided at the wind lower end (73). In any one of Claims 1 thru | or 4 ,
In each heat transfer section (70) of the fins (35, 36), a plurality of the bulging sections (81 to 83) are provided side by side in the air passage direction. In claim 5 ,
The plurality of bulging portions (81 to 83) formed in the heat transfer portions (70) of the fins (35, 36) are arranged in the air passage direction of the bulging portion (81) located on the most windward side. A heat exchanger characterized by its widest width. In claim 5 or 6 ,
The plurality of bulging portions (81 to 83) formed in each heat transfer portion (70) of the fin (35, 36) are the height in the bulging direction of the bulging portion (81) located on the most windward side. A heat exchanger characterized by having the lowest height. In any one of Claims 5 thru | or 7 ,
In each heat transfer section (70) of the fins (35, 36), from the windward end (38) of the heat transfer section (70) to the center of the heat transfer section (70) in the air passage direction. A heat exchanger characterized in that a plurality of the bulging portions (81 to 83) are provided in a portion up to the leeward position. In any one of claims 5 to 8 ,
Each heat transfer part (70) of the fins (35, 36) includes a wind upper end part (72) located on the windward side than the flat tube (33),
In each heat transfer section (70) of the fins (35, 36), a plurality of the bulge sections (81) extends across the leeward end section (72) and the leeward side portion of the leeward end section (72). ~ 83) are provided. In any one of Claims 5 thru | or 9 ,
In each heat-transfer part (70) of the said fin (35, 36), the lower end of each bulging part (81-83) inclines so that it may become below toward the leeward side, The heat exchanger characterized by the above-mentioned. In any one of Claims 1 thru | or 10 ,
The fin (36) is formed in a plate shape provided with a plurality of notches (45) for inserting the flat tube (33), and has a predetermined interval in the extending direction of the flat tube (33). Are arranged, sandwiching the flat tube (33) at the periphery of the notch (45),
In the fin (36), the heat exchanger (70) is characterized in that the portion between the vertically adjacent cutouts (45) constitutes the heat transfer section (70). In any one of Claims 1 thru | or 10 ,
The fin (35) is a corrugated fin meandering up and down disposed between the adjacent flat tubes (33), and a plurality of the heat transfer sections (lined in the extending direction of the flat tubes (33)) ( 70) and a plurality of intermediate plate portions (41) joined to the flat tube (33) that are continuous to the upper end or lower end of the adjacent heat transfer portions (70). Features heat exchanger. A refrigerant circuit (20) provided with the heat exchanger (30) according to any one of claims 1 to 12 ,
An air conditioner that performs a refrigeration cycle by circulating refrigerant in the refrigerant circuit (20).

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