KR20130129428A - Heat exchanger and air conditioner - Google Patents

Abstract

A plurality of flat pipes (33) and fins (36) are provided in the heat exchanger (30). The plate-like fins 36 are arranged at regular intervals from each other in the direction in which the flat tubes 33 extend. The flat tube 33 is inserted into the tube insertion portion 46 of the pin 36. [ In the pin 36, the portion between the vertically adjoining flat tubes 33 becomes the heat transfer portion 70. In the heat transfer portion 70, bulging portions 81 to 83 and louvers 50 and 60 are formed. The bulged portions 81 to 83 are disposed on the wind side of the heat transfer portion 70 and are formed by bulging the heat transfer portion 70 in a mountain shape. The louvers 50 and 60 are disposed at the windward side portion of the heat transfer portion 70 and are formed by cutting the heat transfer portion 70 up.

Description

Heat exchanger and air conditioner {HEAT EXCHANGER AND AIR CONDITIONER}

The present invention relates to a heat exchanger having a flat tube and a fin and for heat-exchanging fluid flowing in the flat tube with air.

Conventionally, a heat exchanger provided with a flat tube and a fin 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 vertically with a predetermined interval therebetween, and the pins in the form of a plate are elongated ) Direction. In the heat exchangers disclosed in Patent Documents 2 and 3, a plurality of flat tubes extending in the left-right direction are vertically arranged at a predetermined interval, and corrugate fins are arranged between adjoining flat tubes Respectively. In these heat exchangers, air flowing in contact with the fins performs heat exchange with the fluid flowing in the flat tubes.

Normally, a louver for promoting heat transfer is formed in this kind of heat exchanger fins. For example, as shown in Fig. 4 of Patent Document 3, in the conventional heat exchanger fins, a plurality of louvers having the same cut height are arranged in the air passing direction.

Japanese Patent Publication No. 2003-262485 Japanese Patent Application Laid-Open No. 2010-002138 Japanese Patent Laid-open No. 11-294984

The refrigerant circuit of the air conditioner is provided with an outdoor heat exchanger for exchanging the refrigerant with the 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 is lower than 0 °, the moisture in the air becomes frost (that is, ice) and attached to the outdoor heat exchanger. Therefore, during the heating operation in a state in which the outside air temperature is low, a defrosting operation for melting the frost attached to the outdoor heat exchanger is performed, for example, every 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 melted by the refrigerant. During the defrosting operation, since the refrigerant discharged from the compressor is supplied to the outdoor heat exchanger instead of the indoor heat exchanger, inflow of warm air into the room is stopped.

On the other hand, a heat exchanger having a flat pipe and a fin can be used as an outdoor heat exchanger of an air conditioner. However, conventionally, in this type of heat exchanger, a louver is formed in the vicinity of the leading edge of the fin and the vicinity of the trailing edge thereof. Therefore, in the outdoor heat exchanger constituted by this type of heat exchanger, the frost is concentrated on the wind side portion of the fin, and the air flow is impeded by the frost attached. As a result, although the frost is hardly adhered to the wind side portion of the fin, the flow rate of the air passing through the heat exchanger is reduced to reduce the amount of heat exchange between the refrigerant and the air, It falls out. Therefore, when this kind of heat exchanger is used as the outdoor heat exchanger of the air conditioner, the frequency of stopping the inflow of warm air into the room is increased by performing the defrosting operation and there is a fear that the heating capacity of the air conditioner is substantially lowered .

The object of the present invention is to provide a heat exchanger having a flat tube and a fin that can increase the time until the capacity of the heat exchanger falls to a limit due to the frost attached to the fin There is.

A first aspect of the present invention is a fuel cell system including a plurality of flat tubes (33) arranged vertically so as to face each other and having fluid passages (34) formed therein, and a plurality of ventilation passages And a plurality of fins (35) and (36) for partitioning the fins (35) and (36) into a plurality of the flat pipes (33) 40 having a plurality of heat transfer portions 70 constituting sidewalls. The heat transfer portions 70 of the fins 35 and 36 are provided with a plurality of louvers 50 and 60 formed by cutting and forming the heat transfer portion 70 and a plurality of louvers 50 and 60, And the bulging portions 81 to 83 are formed by expanding the heat transfer portion 70 so as to extend in a direction intersecting with the passing direction of the air.

In the first invention, a plurality of flat tubes (33) and fins (35, 36) are provided in the heat exchanger (30). Between the upper and lower flat tubes 33, the heat transfer portion 70 of the fins 36, 36 is disposed. In the heat exchanger 30, air passes through the air passage 40 between the vertically arranged flat pipes 33, and the air exchanges heat with the fluid flowing through the passage 34 in the flat tube 33.

The expansion portions 81 to 83 and the louvers 50 and 60 are formed in the respective heat transfer portions 70 of the fins 35 and 36 in the first invention. The swollen portions 81 to 83 are formed on the windward side portion of the heat transfer portion 70 with respect to the louvers 50 and 60. When the swelling portions 81 to 83 and the louvers 50 and 60 are formed in the heat transfer portion 70, the air flow of the ventilation path 40 is disturbed and the heat transfer between the air and the pin is promoted.

Generally, the effect of disturbing the airflow is larger than the bulging portions 81 to 83 formed by bulging the heat transfer portion 70, the louvers 50 and 60 formed by cutting and fixing the heat transfer portion 70. Therefore, the louvers 50 and 60 are generally larger than the bulging portions 81 to 83 in promoting heat transfer.

However, when the temperature of the fluid flowing in the flat pipe 33 is lower than 0 캜, moisture in the air becomes frosted and adheres to the surface of the heat transfer portion 70. On the other hand, in each of the heat transfer portions 70 of the fins 35 and 36 of the first invention, the convex portions 81 to 90 having a comparatively low heat transfer promoting effect are provided on the windward side portions of the louvers 50 and 60, 83 are formed. This reduces the amount of frost adhering to the airfoil portion of the heat transfer portion 70 compared to the case where the louvers 50 and 60 are formed over the entire heat transfer portion 70, The amount of frost adhering to the surface increases. Therefore, in the heat transfer portion 70 of the present invention, the difference between the frost amount attached to the windward side portion and the frost amount attached to the windward side portion becomes small.

The second invention is characterized in that in the first invention, at least the louvers (50, 60) formed on the respective heat transfer portions (70) of the fins (35, 36) The windward side cut edge 53 of the louver 50 protrudes in the bulge direction of the bulged portions 81 to 83. The bulging portion

The second invention is characterized in that in the respective heat transfer portions 70 of the fins 35 and 36, the part of the louver 50 located on the side of the bulging portions 81 to 83 has a cut- (81 to 83). That is, the part of the louver 50 located on the side of the bulging portions 81 to 83 is inclined in the direction opposite to the downstream portion of the bulging portions 81 to 83. The air flowing over the swollen portions 81 to 83 strikes the louvers 50 located on the swollen portions 81 to 83, and the flow direction thereof changes. Therefore, the flow of air over the bulged portions 81 to 83 is further disturbed by contact with the louvers 50 located on the bulged portions 81 to 83. [

The third and fourth aspects of the invention according to the first or second aspect of the present invention are characterized in that the cut end portions 53 and 63 of the louvers 50 and 60 are formed by the peripheral edges 54 and 64 and the upper ends of the peripheral edges 54 and 64 The upper ends of the louvers 50 and 60 extend from the upper ends of the ridges 50 and 60 to the upper edges 54 and 64 inclined with respect to the ridges 54 and 64, And is composed of lower side edge portions 56 and 66 which are inclined with respect to the peripheral edge portions 54 and 64. In each of the heat transfer portions 70 of the fins 35 and 36, The louvers 50 and 60 become asymmetric louvers whose inclination of the lower side edge portion 56 with respect to the peripheral edge portion 54 is gentler than the inclination of the upper side edge portion 55 with respect to the peripheral edge portion 54. [

The third invention is characterized in that the cut end portions 53 and 63 of the louvers 50 and 60 are constituted by the peripheral edge portions 54 and 64 and the upper side edge portions 55 and 65 and the lower side edge portions 56 and 66. At least one of the louvers 50 and 60 formed in the respective heat transfer portions 70 of the fins 35 and 36 is an asymmetric louver 50a. The inclination of the lower side edge portion 56 with respect to the peripheral edge portion 54 becomes gentler than the inclination with respect to the peripheral edge portion 54 of the upper side edge portion 55 in the asymmetric louver 50a. The clearance between the lower side edge portions 56 is made longer than the clearance between the upper side edge portions 55 between the cut end portions 35 of the asymmetric louvers 50a adjacent to the air passing direction.

On the surface of the heat exchanger (30) pins (35, 36) of the third invention, the moisture in the air condenses and the frost attached to the fins (35, 36) melts to generate drain water. The drain water generated on the surfaces of the fins 35 and 36 also enters between the cut-up ends 53 of the asymmetric louver 50a adjacent to the air passing direction. The drain water entered between the asymmetric louvers 50a is sucked into the gap between the elongated lower side edges 56 by the capillary phenomenon.

A fourth aspect of the present invention provides the fourth aspect of the present invention as set forth in the third aspect of the present invention, in which the louver (50) formed in a portion adjacent to the flat pipe (33) in each heat transfer portion (70) will be.

The louver 50 is formed at a portion adjacent to the flat tube 33 in each of the heat transfer portions 70 of the fins 35 and 36 and part or all of the louver 50 is asymmetric It becomes a louver.

The fifth aspect of the present invention is the fuel cell according to any one of the first to fourth inventions described above, wherein each of the heat transfer portions (70) of the fins (35, 36) has a downward windward end And the louver 60 is formed at the windward end portion 73 in each of the heat transfer portions 70 of the fins 35 and 36.

In the fifth invention, each of the heat transfer portions 70 of the fins 35 and 36 has the windward end portion 73. The windward end portion (73) of the heat transfer portion (70) protrudes downward from the flat pipe (33). In the heat transfer portion (70) of the present invention, the louver (60) is formed at the windward lower end portion (73). In the heat transfer portion 70 of the present invention, at least the louvers 50 and 60 may be formed on the downward wind-up end portion 73. [ That is, in the heat transfer portion 70 of the present invention, a plurality of louvers 50 and 60 may be formed over the windward side end portions 73 and the windward side end portions 73.

The sixth invention is characterized in that, in any one of the first to fifth inventions, a plurality of the bulging portions (81 to 83) are formed in the heat transfer portions (70) of the fins (35, 36) .

In the sixth invention, a plurality of swelling portions (81 to 83) are formed in each heat transfer portion (70) of the fins (35, 36). In each heat transfer portion 70, the plurality of swollen portions 81 to 83 are arranged in the direction of air passage. The airflow of the ventilation path (40) is scattered every time it passes over the plurality of swelling portions (81 to 83).

A seventh aspect of the present invention is the fuel supply device according to the sixth aspect of the present invention, wherein the plurality of the bulging portions (81-83) formed in the heat transfer portions (70) of the fins (35,36) The width of the air passage direction is the widest.

The larger the width of the swollen portions 81 to 83 in the air passing direction is, the less the change in the air flow direction flowing along the swollen portions 81 to 83 is. As a result, The promoting effect of heat transfer becomes small. On the other hand, the temperature difference between the air flowing through the ventilation path 40 and the heat transfer portion 70 becomes the largest at the inlet of the ventilation path 40, and becomes gradually smaller toward the wind direction.

The width of the bulged portion 81 located on the most windward side in the air passing direction of the heat transfer portions 70 of the fins 35 and 36 is smaller than the width of the air passing direction of the remaining bulged portions 82 and 83 The width becomes wider than the width of the direction. That is, in each of the heat transfer portions 70 of the fins 35 and 36, the difference in temperature between the air flowing in the air passage 40 and the heat transfer portion 70 is relatively large, The wide swelling portion 81 is formed. This makes it possible to suppress the amount of frost adhering to the air side portion where the swollen portion 81 having the widest width is formed in each of the heat transfer portions 70 of the fins 35 and 36

An eighth aspect of the present invention is the fuel supply system according to the sixth or seventh aspect of the present invention, wherein the plurality of bulging portions (81-83) formed in the respective heat transfer portions (70) of the fins (35,36) The height in the bulging direction of the base 81 is the lowest.

The lower the height of the bulged portions 81 to 83 in the bulging direction, the smaller the change in the direction of the air flow flowing along the bulged portions 81 to 83 is. As a result, The promoting effect is reduced. On the other hand, the temperature difference between the air flowing through the ventilation path 40 and the heat transfer portion 70 becomes the largest at the inlet of the ventilation path 40, and becomes gradually smaller toward the wind direction.

The height of the bulged portion 81 located on the most windward side in the bulging direction is larger than the height of the bulged portions 82 and 83 in the bulging direction in the heat transfer portion 70 of the fins 35 and 36, Lt; / RTI > That is, in each of the heat transfer portions 70 of the fins 35 and 36, the heat transfer promoting effect is relatively small at a position on the air side where the temperature difference between the air flowing in the air passage 40 and the heat transfer portion 70 is relatively large, The lowest swollen portion 81 is formed. As a result, the amount of frost adhered to the air side portion where the bulged portion 81 having the lowest height is formed can be suppressed in each of the heat transfer portions 70 of the fins 35 and 36.

The ninth invention is characterized in that in each of the heat transfer portions (70) of the fins (35) and (36), the heat transfer portion (70) A plurality of the bulging portions 81 to 83 are formed at a portion from the center of the portion 70 in the air passing direction to the windward lower position.

In the ninth invention, each of the heat transfer portions 70 of the fins 35 and 36 is provided with a plurality of bulged portions 81 to 83 in an area of at least half the length in the air flow direction.

The tenth aspect of the present invention is the tenth invention according to any one of the sixth to ninth inventions, wherein each of the heat transfer portions (70) of the fins (35, 36) has an airfoil end portion (72) And a plurality of the bulging portions 81 to 83 are formed in the respective heat transfer portions 70 of the fins 35 and 36 over the windward end portion 72 and the windward side portion of the windward end portion 72, .

In the tenth aspect of the invention, an airfoil end portion (72) is formed in each of the heat transfer portions (70) of the fins (35, 36). Each of the heat transfer portions 70 has a plurality of bulged portions 81 to 83 formed on both sides of the windward end portion 72 and a portion adjacent to the windward side of the windward end portion 72.

The eleventh invention is characterized in that, in any one of the sixth to tenth inventions, the lower end of each of the bulged portions (81-83) of the respective heat transfer portions (70) of the fins (35, 36) It is to be inclined as much as possible.

In the eleventh invention, the lower ends of the bulged portions 81 to 83 formed in the heat transfer portions 70 of the fins 35 and 36 are inclined. The lower ends of the respective swollen portions 81 to 83 are inclined so as to be downward by the windward side. The distance from the flat tube 33 adjacent to the lower side of the heat transfer portion 70 to the lower end of the bulged portions 81 to 83 is smaller than the distance .

During the defrosting process in which the frost attached to the fins 35 and 36 is melted, the generated drain water flows downward from the bulged portions 81 to 83 along the surface of the heat transfer portion 70. The drain water flowing down from the bulging portions 81 to 83 is stored on the flat tube 33 adjacent to the lower side of the heat transfer portion 70. On the other hand, in the eleventh invention, the distance from the flat pipe 33 under the heat transfer portion 70 to the lower ends of the bulged portions 81 to 83 gradually becomes shorter toward the downwind side. The drain water flowing down from the bulging portions 81 to 83 and stored on the flat pipe 33 is discharged to the downwind side where the distance from the flat pipe 33 to the lower ends of the bulging portions 81 to 83 is short, Sucked by.

The twelfth aspect of the present invention is the bimetal according to any one of the first to eleventh inventions, wherein the fin (36) is formed into a plate shape having a plurality of notch portions (45) for fitting the flat tube (33) And is disposed at a predetermined distance from each other in the extension direction of the flat tube 33 and sandwiches the flat tube 33 by the periphery of the notched portion 45, , The portion between the vertically adjacent notch portions 45 constitutes the heat transfer portion 70. As shown in Fig.

In the twelfth invention, a plurality of pins (36) formed in a plate shape are arranged at intervals from each other in the direction of extension of the flat tube (33). Each of the fins 36 is provided with a plurality of notches 45 for fitting the flat tube 33 therein. The periphery of the notch 45 of each fin 36 sandwiches the flattened pipe 33 therebetween. In each of the fins 36, a portion between the vertically adjacent notches 45 constitutes the heat transfer portion 70.

The thirteenth invention is characterized in that, in any one of the first to eleventh inventions, the fin (35) is a corrugated fin which is arranged between adjoining flat pipes (33) A plurality of the heat transfer portions 70 arranged in the extending direction of the flat pipe 33 and a plurality of intermediate plate portions 33 connected to the flat pipe 33 and connected to the upper or lower end of the adjacent heat transfer portion 70, (41).

In the thirteenth invention, the pin 35, which is a corrugated fin, is disposed between the adjacent flat tubes 33. On each of the fins 35, a plurality of heat transfer portions 70 arranged in the extending direction of the flat tube 33 are formed. Adjacent heat transfer portions 70 are connected to the intermediate plate portion 41 and the intermediate plate portion 41 is joined to the flat side surface of the flat pipe 33. [

The fourteenth invention is directed to an air conditioner (10), comprising a refrigerant circuit (20) provided with a heat exchanger (30) of any one of the first to thirteenth inventions, wherein the refrigerant circuit (20) The refrigeration cycle is performed by circulating the refrigerant.

In the fourteenth invention, the heat exchanger (30) of any one of the first to thirteenth 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 32 and exchanges heat with the air flowing through the air passage 40.

In each of the heat transfer portions 70 of the fins 35 and 36 according to the present invention, bulged portions 81 to 83 having a relatively low heat transfer promoting effect are formed on the windward side portion of the louvers 50 and 60. Thereby, the difference between the amount of frost adhering to the air-side portion of the heat transfer portion 70 and the amount of frost adhering to the downstream portion of the heat transfer portion 70 is reduced. As a result, in the heat exchanger (30) of the present invention, the adhesion amount of the frost increases when the heat exchange ability is lowered as compared with the conventional heat exchanger in which frost is concentrated on the windward side portion of the fin. Therefore, according to the present invention, it is possible to extend the time until the capability of the heat exchanger 30 is lowered due to the adherence of the frost to the limit, and the frequency of the defrosting can be lowered.

In the respective heat transfer portions 70 of the second aspect of the present invention, the partial louver 50 located on the side of the bulged portions 81 to 83 is formed so that the cut- And is projected in a bulging direction. As a result, the flow of air over the bulged portions 81 to 83 is further disturbed by colliding with the louver 50 located on the bulged portions 81 to 83. [ Therefore, according to the present invention, heat transfer between the fins (35, 36) and the air can be reliably promoted at the portion where the louvers (50, 60) are formed in the heat transfer portion (70).

In the third invention, at least a part of the louvers (50, 60) formed in the respective heat transfer portions (70) of the fins (35, 36) becomes an asymmetric louver (50a). The inclination of the lower side edge portion 56 with respect to the peripheral edge portion 54 becomes gentler than the inclination with respect to the peripheral edge portion 54 of the upper side edge portion 55 in the asymmetric louver 50a. The drain water that has been generated on the surfaces of the fins 35 and 36 and entered between the cut-up ends 53 of the asymmetric louver 50a adjacent to the direction of air passage is formed by the capillary phenomenon, ) Is sucked into the gap between. Therefore, according to the present invention, it is possible to let the drain water that has entered between the cut-up ends 53 of the asymmetric louver 50a adjacent to the air passing direction to flow downward by capillary phenomenon not by gravity alone, The amount of drain water remaining on the surface of the portion 70 can be reduced.

In the fifth invention, louvers (50, 60) are formed at the windward end portions (73) of the respective heat transfer portions (70) of the fins (35, 36). The lower end portion of the downwind end portion 73 has a smaller temperature difference from the air flowing through the ventilation path 40 as compared with a portion sandwiched between vertically adjacent flat pipes 33. [ On the other hand, in the present invention, the louver 60 is formed on the downwind end portion 73 of the heat transfer portion 70, and the heat transfer between the downwind end portion 73 and the air is promoted. Therefore, according to the present invention, the windward end portion 73 of the heat transfer portion 70 can be effectively used for heat exchange with air, and the performance of the heat exchanger 30 can be improved.

In the sixth invention, a plurality of bulging portions (81 to 83) are formed in each heat transfer portion (70) of the fins (35, 36). As a result, the airflow in the ventilation path (40) is scattered every time it passes over the plurality of bulging portions (81 to 83). Therefore, according to the present invention, the heat transfer between the portion of the heat transfer portion 70 where the bulging portions 81 to 83 are formed and the air can be promoted.

The width of the bulged portion 81 located on the most windward side in the air flow direction is larger than the width of the remaining bulged portions 82 and 83 in the heat transfer portion 70 of the fins 35 and 36 Wider than the width of the passing direction. In the heat transfer portions 70 of the fins 35 and 36 according to the eighth aspect of the present invention, the height of the bulging portion 81 located on the most windward side in the bulging direction is smaller than the height of the bulging portions 82 and 83 in the bulging direction Lower than the height.

That is, in each of the heat transfer portions 70 of the fins 35 and 36, the temperature difference between the air flowing through the air passage 40 and the heat transfer portion 70 is relatively large on the windward side in the seventh and eighth inventions And the bulged portion 81 having a smaller heat transfer promoting effect than the remaining bulged portions 82 and 83 is formed. Therefore, according to the present invention, it is possible to suppress the amount of frost adhering to the airfoil portion of each of the heat transfer portions 70 of the fins 35 and 36, and the amount of frost attached to the airfoil portion of the heat transfer portion 70, It is possible to surely reduce the difference in frost amount adhering to the downstream portion.

In the eleventh invention, the lower ends of the bulged portions (81 to 83) formed in the respective heat transfer portions (70) of the fins (35, 36) are inclined downward by the windward side. Thereby, the drainage water generated on the surface of the heat transfer portion 70 and flowing downward from the bulging portions 81 to 83 flows toward the downwind side where the distance from the flat tube 33 to the lower ends of the bulging portions 81 to 83 is short Sucked in by the capillary phenomenon. Therefore, according to the present invention, the movement of the drain water generated on the surface of the heat transfer portion 70 toward the downwind side can be promoted, and the amount of drain water remaining in the heat exchanger 30 can be reduced.

1 is a refrigerant circuit diagram showing a schematic configuration of an air conditioner provided with a heat exchanger of the first embodiment.
2 is a schematic perspective view of the heat exchanger of the first embodiment.
3 is a partial cross-sectional view showing the front face of the heat exchanger of the first embodiment.
4 is a cross-sectional view of a heat exchanger showing a part of the AA cross section of FIG. 3.
Fig. 5 is a view showing a main part of a fin of a heat exchanger according to the first embodiment. Fig. 5 (A) is a front view of a fin, and Fig.
Fig. 6 is a cross-sectional view of a fin provided in the heat exchanger of the first embodiment, Fig. 6 (A) is a cross-sectional view taken along line CC in Fig. 5, .
Fig. 7 is a cross-sectional view corresponding to Fig. 5 (B) showing a heat transfer portion of a plurality of fins provided in the heat exchanger of the first embodiment. Fig.
8 is a cross-sectional view of the pin showing the FF section in Fig.
9 is a schematic perspective view of the heat exchanger of the second embodiment.
10 is a partial cross-sectional view showing the front face of the heat exchanger of the second embodiment.
11 is a cross-sectional view of a heat exchanger showing a part of the cross section of Fig. 10GG.
12 is a schematic perspective view of a fin provided in the heat exchanger of the second embodiment.
Fig. 13 is a cross-sectional view corresponding to Fig. 4 of the heat exchanger of the third embodiment. Fig.
Fig. 14 is a view showing a main part of a fin of a heat exchanger according to a third embodiment, wherein (A) is a front view of a fin, and Fig. 14 (B) is a cross-sectional view taken along the line HH in Fig.
Fig. 15 is a front view of a pin showing a first modification of the other embodiment applied to the pin of the first embodiment, and corresponds to Fig. 4; Fig.
Fig. 16 is a front view of the pin showing the application of the second modification of the other embodiment to the pin of the first embodiment, and corresponds to Fig. 4. Fig.
Fig. 17 is a cross-sectional view corresponding to Fig. 5 (B) of another embodiment of the pin, Fig. 17 (A) shows application of the third modification to the pin of the first embodiment, This example is applied to the pin of the first embodiment.

BEST MODE FOR CARRYING OUT THE INVENTION Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.

≪ First Embodiment >

A first embodiment of the present invention will be described. The heat exchanger (30) of the first embodiment constitutes an outdoor heat exchanger (23) of the air conditioner (10) to be described later.

Air conditioner

The air conditioner 10 provided with the heat exchanger 30 of this embodiment is demonstrated, referring FIG.

<Configuration of the 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 connection pipe 13 and a gas side connection 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 connection pipe 13, and the gas side connection pipe 14.

The refrigerant circuit 20 includes a compressor 21, a four-way switching valve 22, an outdoor heat exchanger 23, an expansion valve 24, and an indoor heat exchanger 25. The compressor 21, the four-way switching valve 22, the outdoor heat exchanger 23, and the expansion valve 24 are housed 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 housed in the indoor unit 12. The indoor unit 12 is provided with an indoor fan 16 for supplying indoor air to the indoor heat exchanger 25.

The coolant circuit 20 is a closed circuit in which a coolant is charged. In the refrigerant circuit 20, the discharge side of the compressor 21 is connected to the first port of the four-way switching valve 22 and the suction side thereof is connected to the second port of the four-way switching valve 22, respectively. In the refrigerant circuit 20, the outdoor heat exchanger 23, the expansion valve 24, and the indoor heat exchanger 25 are arranged in order from the third port to the fourth port of the four-way switching valve 22 do.

The compressor (21) is a compressor (21) of a scroll type or a rotary type. The four-way switching valve 22 has a first state in which the first port communicates with the third port, and a second port communicates with the fourth port (the state indicated by broken lines in FIG. 1), and the first port is fourth In addition, the port communicates with the second port and the second port communicates with the third port (the state indicated by a solid line in FIG. 1). The expansion valve 24 is what is called an electromagnetic expansion valve.

The outdoor heat exchanger 23 heats the outdoor air with the refrigerant. The outdoor heat exchanger 23 is comprised by the heat exchanger 30 of this embodiment. On the other hand, the indoor heat exchanger 25 heats the indoor air with the refrigerant. The indoor heat exchanger 25 is constituted by a so-called cross-fin type pin-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. In addition, during the cooling operation, the outdoor fan 15 and the indoor fan 16 are driven.

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 to radiate and condense the outdoor air. The refrigerant flowing out of the outdoor heat exchanger (23) expands when passing through the expansion valve (24), and then flows into the indoor heat exchanger (25), absorbs heat from the indoor air, and evaporates. The refrigerant flowing out of the indoor heat exchanger 25 is sucked into the compressor 21 and compressed after passing through the four-way switching valve 22. The indoor unit 12 supplies the air cooled by the indoor heat exchanger 25 to the room.

<Heating operation>

The air conditioner 10 performs heating operation. During the heating operation, the four-way switching valve 22 is set to the second state. In addition, during the heating operation, the outdoor fan 15 and the indoor fan 16 are driven.

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, radiates heat to the indoor air, and condenses it. The refrigerant flowing out from the indoor heat exchanger (25) expands when passing through the expansion valve (24), and then flows into the outdoor heat exchanger (23), absorbs heat from the outdoor air, and evaporates. The refrigerant flowing out of the outdoor heat exchanger 23 is sucked into the compressor 21 and compressed after passing through the four-way switching valve 22. The indoor unit 12 supplies the air heated by the indoor heat exchanger 25 to the room.

<Defrost action>

As described above, during the heating operation, the outdoor heat exchanger 23 functions as an evaporator. The evaporation temperature of the refrigerant in the outdoor heat exchanger 23 may be lower than 0 占 폚 under the low ambient temperature condition. In this case, the moisture in the outdoor air is frosted and adhered to the outdoor heat exchanger 23. Thus, the air conditioner 10 performs the defrost operation each time, for example, when the duration of the heating operation reaches a predetermined value (for example, several tens of minutes).

At the start of the defrost operation, the four-way switching valve 22 switches from the second state to the first state, and the outdoor fan 15 and the indoor fan 16 stop. In the refrigerant circuit 20 during the defrost operation, the high temperature refrigerant discharged from the compressor 15 is supplied to the outdoor heat exchanger 23. In the outdoor heat exchanger 23, frost attached to the surface of the outdoor heat exchanger 23 is warmed by the refrigerant to melt. The refrigerant discharged from the outdoor heat exchanger 23 sequentially passes through the expansion valve 24 and the indoor heat exchanger 25 and then sucked into the compressor 21 and compressed. When the defrost operation ends, 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 1st embodiment-

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. 2 to 8. FIG.

<Overall Configuration of Heat Exchanger>

2 and 3, the heat exchanger 30 of the present embodiment includes one first header collecting tube 31, one second header collecting tube 32, a plurality of flat tubes 33, , And a plurality of pins (36). The first header assembly tube 31, the second header assembly tube 32, the flat tube 33, and the pin 36 are all made of an aluminum alloy and are joined to each other by brazing.

Both the 1st header assembly pipe | tube 31 and the 2nd header assembly pipe | tube 32 are formed in the elongate hollow cylinder in which the both ends were closed | closed. 3, a first header collecting tube 31 is disposed at the left end of the heat exchanger 30 and a second header collecting tube 32 is disposed at the right end of the heat exchanger 30 in an upright position. That is, the 1st header assembly pipe | tube 31 and the 2nd header assembly pipe | tube 32 are provided in the attitude | position that each axial direction becomes an up-down direction.

As also shown in FIG. 4, the flat tube 33 is a heat exchanger tube which became a rectangle or rounded rectangle with a flat cross-sectional shape. In the heat exchanger 30, the plurality of flat tubes 33 are arranged in a posture in which the extending direction thereof is in the left-right direction, and the flat side faces thereof face each other. In addition, the plurality of flat tubes 33 are vertically arranged with a predetermined interval therebetween. One end of each of the flat tubes 33 is inserted into the first header assembly tube 31, and the other end thereof is inserted into the second header assembly tube 32.

The pins 36 are plate-shaped pins and are arranged at regular intervals in the extending direction of the flat tube 33. That is, the pin 36 is arrange | positioned so that it may become substantially orthogonal to the direction of extension of the flat tube 33. The details of this will be described later. In each of the fins 36, the portion located between the vertically adjacent flat pipes 33 constitutes the heat transfer portion 70.

3, in the heat exchanger 30, a space between the vertically adjacent flat pipes 33 is partitioned into a plurality of ventilation paths 40 by the heat transfer portion 70 of the fins 36. [ The heat exchanger 30 heat-exchanges the refrigerant flowing through the fluid passage 34 of the flat tube 33 with 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 as to face flat sides, and a plate-like heat transfer section 70 extending from one side of the adjacent flat tubes 33 to the other side And has a plurality of pins (36). A plurality of heat transfer portions 70 are arranged in the extending direction of the flat tubes 33 between the adjacent flat tubes 33. In this heat exchanger (30), the air flowing between the adjacent heat transfer portions (70) exchanges heat with the fluid flowing in each flat pipe (33).

<Configuration of the pin>

As shown in Fig. 4, the pin 36 is a vertically long plate-like pin 36 formed by pressing a metal plate. The thickness of the pin 36 is approximately 0.1 mm.

A plurality of elongated notched portions 45 extending in the width direction (i.e., the direction of air passage) of the fins 36 are formed in the fins 36 at the front edge 38 of the fins 36 . In the pin 36, many notch parts 45 are formed in the longitudinal direction (up-down direction) of the pin 36 by a fixed space | interval. The notch portion 45 is a notch for fitting the flat tube 33 therein. The windward portion of the notch 45 constitutes a tube insertion portion 46. The pipe insertion portion 46 has a width in the vertical direction 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 pipe 33 is fitted into the pipe insertion portion 46 of the pin 36 and is joined to the peripheral edge portion of the pipe insertion portion 46 by soldering. 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 portion 45.

In the pin 36, the portion between the vertically adjacent notches 45 constitutes the heat transfer portion 70. That is, one fin 36 has a plurality of heat transfer portions 70 sandwiched between the flat tubes 33 and vertically adjacent to each other. In the heat exchanger 30 of the present embodiment, the heat transfer portions 70 of the fins 36 are disposed between the flat tubes 33 arranged in the vertical direction.

Each heat transfer portion 70 of the pin 36 has an intermediate portion 71, a windward end portion 72 and a windward end portion 73. Each of the heat transfer portions 70 is provided with an intermediate portion 71 which overlaps with the flat pipe 33 adjacent to the upper and lower portions (that is, a portion located directly above or below the flat pipe 33 vertically adjacent thereto) . In the respective heat transfer portions 70, the portion located on the windward side from the intermediate portion 71 (that is, the portion projecting to the windward side from the flat pipe 33) becomes the airfoil end portion 72, and the intermediate portion 71 (That is, a portion protruding downward from the flattening pipe 33) becomes a downward windward end portion 73. The windward end portion 73 is a portion of the windward end portion 73 which is located lower than the flattening pipe 33.

In the pin 36, the windward end portions 73 of the upper and lower adjacent heat transfer portions 70 are connected to each other via the connecting plate portion 75. In addition, the fin 36 has a water-like rib 49 formed thereon. The diaphragm ribs 49 are elongated concave grooves extending upward and downward along the trailing edge 39 of the pin 36. The diaphragm ribs 49 are formed from the upper end of the pin 36 to the lower end thereof.

As shown in Fig. 5, a plurality of swelling portions 81 to 83 and louvers 50 and 60 are formed in each heat transfer portion 70 of the pin 36. As shown in Fig. In the respective heat transfer portions 70, bulging portions 81 to 83 are formed on the windward side and louvers 50 and 60 are formed on the windward side. That is, in each heat transfer portion 70, the louvers 50 and 60 are formed only in the downwind portion, and the swelling portions 81 to 83 are formed in the airfoil portion of all the louvers 50 and 60. Incidentally, the numbers of the bulging portions 81 to 83 and the louvers 50 and 60 shown below are all merely one example.

Three bulging portions 81 to 83 are formed in a portion extending from the windward end portion 72 to the windward side region of the intermediate portion 71 in each heat transfer portion 70 of the pin 36. [ The three bulging portions 81 to 83 are arranged in the air passing direction (i.e., the direction from the leading edge 38 to the trailing edge 39 of the pin 36). Each of the bulged portions 81 to 83 is formed in a mountain shape by causing the heat transfer portion 70 to bulge toward the ventilation path 40. The details of the bulging portions 81 to 83 will be described later.

Each of the heat transfer portions 70 of the pin 36 has a plurality of louvers 50 and 60 extending in the vertical direction on each of the downwind portion and the downwind end portion 73 of the intermediate portion 71. In each of the heat transfer portions 70, a plurality of louvers 50 and 60 are arranged in the air passing direction. Details of the louvers 50 and 60 will be described later.

A tab 48 is formed in the pin 36 to maintain a gap with the side fin 36. As shown in Fig. 5B, the tab 48 is a small rectangular piece formed by cutting and raising the pin 36. As shown in Fig. As shown in Fig. 7, the projecting end of the tab 48 comes into contact with the side fins 36, so that the spacing between the fins 36 is maintained. As shown in Fig. 5 (A), the tabs 48 are formed one by one on the upper edge and the lower edge of the windward end portion 72 of the heat transfer portion 70, respectively. Also, the tabs 48 are formed one by one on each connecting plate portion 75 as well.

<Arrangement and Shape of Expansion Portion>

The arrangement and shape of the bulged portions 81 to 83 formed on the pin 36 will be described in detail. "Right" and "left" used in this description mean the direction when the fin 36 is viewed from the air side (that is, the front side of the heat exchanger 30).

5, the first swelling portion 81, the second swelling portion 82, and the third swelling portion 83 are formed in the respective heat transfer portions 70 of the pin 36. As shown in Fig. Each of the bulged portions 81 to 83 is formed by plastic deformation of the heat transfer portion 70 of the pin 36 by press working or the like and bulges to the right side of the heat transfer portion 70 ). The expansion direction of the heat transfer portion 70 shown here is merely an example. That is, each of the bulged portions 81 to 83 may bulge to the left side of the heat transfer portion 70. [

Each of the bulged portions 81 to 83 extends in a direction intersecting the air passage direction in the ventilation path (40). Specifically, each of the bulged portions 81 to 83 is formed in a mountain shape in which the ridgelines 81a, 82a, and 83a are substantially parallel to the leading edge 38 of the pin 36. [ That is, the ridgelines 81a, 82a, and 83a of the respective swollen portions 81 to 83 intersect with the air passing direction. In each of the bulging portions 81 to 83, the inclined portion extending from the front end (that is, the end on the windward side) to the ridgelines 81a, 82a and 83a and the inclined portion extending from the rear end 82a, and 83a are sloped portions 81b, 82b, and 83b, respectively. The swelling portions 81 to 83 are provided with the portions extending from the upper ends 81d, 82d and 83d to the upper ends of the slope portions 81b, 82b and 83b and the portions extending from the lower ends 81e, 82e and 83e to the slope portions 81b and 82b And 83b are the side portions 81c, 82c, and 83c, respectively.

The first swollen portion 81, the second swollen portion 82 and the third swollen portion 83 in the respective heat transfer portions 70 of the pin 36 move in the air passing direction (that is, In the direction from the leading edge 38 to the trailing edge 39). The three bulging portions 81 to 83 are formed in the respective heat transfer portions 70 over the windward end portions 72 and the windward portions of the intermediate portion 71. [ Specifically, the front end of the first bulging portion 81 is close to the leading edge 38 of the pin 36. [ The rear end of the first bulging portion 81 continues to the front end of the second bulging portion 82 and the rear end of the second bulging portion 82 continues to the front end of the third bulging portion 83. The rear end of the third bulging portion 83 is located on the downstream side of the center of the heat transfer portion 70 in the air passing direction. The distance L1 from the leading edge 38 of the pin 36 to the trailing edge of the third bulging portion 83 is longer than half the distance L from the leading edge 38 to the trailing edge 39 of the pin 36 L1 &gt; L / 2).

5A, the width W1 of the first swollen portion 81 in the air passing direction is the same as the width W2 of the second swollen portion 82 in the air passing direction and the width W2 of the third swollen portion 83 And the width W3 in the direction of air passage. The width W2 of the second swollen portion 82 is equal to the width W3 of the third swollen portion 83. [ That is, the relationship between the widths of the respective bulged portions 81 to 83 is W1> W2 = W3. 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, and the height of the second bulging portion 82, (H1 &lt; H2 &lt; H3) of the third swelled portion 83 is smaller than the height H3 of the third swelled portion 83 in the swelling direction.

The upper end 81d of the first swollen portion 81 is inclined such that the windward side is upward. The upper end 82d of the second bulging portion 82 and the upper end 83d of the third bulging portion 83 are substantially orthogonal to the leading edge 38 of the pin 36. [ The distance from the upper end of the heat transfer portion 70 to the upper end 83d of the third swollen portion 83 in each heat transfer portion 70 is larger than the distance from the upper end of the heat transfer portion 70 to the second swollen portion 82 The upper end 82d of the upper portion 82a.

The lower ends 81e, 82e and 83e of the respective swelling portions 81 to 83 are inclined so that the windward side is downward. The lower ends 81e, 82e and 83e of the three bulging portions 81 to 83 are arranged on one straight line inclined downward by the windward side. The distance D2 from the lower end of the heat transfer portion 70 to the windward side end portion of the lower end 83e of the third bulging portion 83 is smaller than the distance D2 from the lower end of the heat transfer portion 70 Is shorter than the distance D1 to the windward side end portion of the lower end 81e of the one bulging portion 81. In each heat transfer portion 70, the distance from the lower end of the heat transfer portion 70 to the lower ends 81e, 82e, 83e of the bulged portions 81 to 83 becomes gradually shorter toward the downwind side.

&Lt; Arrangement and shape of louver &

The arrangement and shape of the louvers 50 and 60 formed on the pin 36 will be described in detail. "Right" and "left" used in this explanation mean the direction when the fin 36 is viewed from the air side (that is, the front side of the heat exchanger 30).

As shown in Fig. 5, a plurality of louvers 50 and 60 are arranged in the heat transfer portion 70 of the fin 36 in the air passing direction. A group of louvers formed in the intermediate portion 71 constitute the airfoil side louver 50 and a group of louvers formed on the airfoil end portion 73 constitute the downwind side louver 60 do.

Each of the louvers 50 and 60 is formed by forming a plurality of slits in the heat transfer portion 70 and plastic-deforming portions between adjacent slits to twist. The longitudinal direction of each of the louvers 50 and 60 is substantially parallel to the leading edge 38 of the heat transfer portion 70 (i.e., up and down direction). That is, the longitudinal direction of each of the louvers 50 and 60 is a direction intersecting with the passing direction of air. The lengths of the louvers 50 and 60 are equal to each other.

The distance from the lower end of the heat transfer portion 70 to the lower end of each of the louvers 50 and 60 in the respective heat transfer portions 70 is set such that the distance from the lower end of the heat transfer portion 70 to the lower end of the third swollen portion 83 The distance D2 to the windward side end portion of the windward side portion. The distance from the upper end of the heat transfer portion 70 to the upper end of each of the louvers 50 and 60 in each heat transfer portion 70 is set so that the distance from the upper end of the heat transfer portion 70 to the upper end of the third swollen portion 83 And is substantially equal to the distance to the upper end 83d.

As shown in Fig. 5 (B), each of the louvers 50, 60 is inclined with respect to the flat portion around the louvers 50, 60. The windward side louver 50 and the windward side louver 60 are inclined in directions opposite to each other. In the louver 50 on the windward side, the cut-up stand 53 on the windward side is bulged to the left, and the cut-up stand 53 on the windward side is bulged to the right. That is, the wind-up side louver 50 is projected in the same direction as the bulging direction of the third bulging portion 83, On the other hand, in the downward windward side louver 60, the cut end 63 on the windward side is bulged to the right, and the cut end 63 on the windward side is bulged to the left.

The cut end portions 53 and 63 of the windward side louver 50 and the windward side louver 60 are formed by the peripheral edges 54 and 64 and the upper edge portions 55 and 55 as shown in Figures 6 (B) and 6 (C) , 65, and lower side edges 56, 66, respectively. The extension directions of the peripheral portions 54 and 64 are substantially parallel to the extension direction of the leading edge 38 of the heat transfer portion 70. [ The upper side edges 55 and 65 extend from the upper ends of the peripheral edges 54 and 64 to the upper ends of the louvers 50 and 60 and are inclined with respect to the peripheral edges 54 and 64. The lower side edges 56 and 66 extend from the lower ends of the peripheral edges 54 and 64 to the lower edges of the louvers 50 and 60 and are inclined with respect to the peripheral edges 54 and 64.

The inclination angle of the upper side edge portion 55 to the peripheral edge portion 54 is θ1 and the inclination angle of the lower side edge portion 56 to the peripheral edge portion 54 is θ2 to be. 5A, the inclined angle? 2 of the lower side edge portion 56 is smaller than the inclined angle? 1 of the upper side edge portion 55 (? 2 &lt;? 1). Therefore, in this airfoil side louver 50a, the lower side edge portion 56 is longer than the upper side edge portion 55. This air-side louver 50a is an asymmetric louver in which the shape of the cut-up end 53 is vertically asymmetric. On the other hand, the inclined angle [theta] 2 of the lower side edge portion 56 is equal to the inclined angle [theta] 1 of the upper side edge portion 55 in some of the windward side louvers 50b located on the downwind side. This air-side louver 50b is a symmetrical louver in which the shape of the cut-up end 53 is vertically symmetrical.

The inclined angle with respect to the peripheral edge portion 64 of the upper side edge portion 65 is? 3 and the inclined angle with respect to the peripheral edge portion 64 of the lower side edge portion 66 is? 4 to be. The inclination angle? 4 of the lower side edge portion 66 of all the downwind side louvers 60 is equal to the inclination angle? 3 of the upper side edge portion 65 as shown in FIG. 5 (A). This windward side louver 60 is a symmetrical louver in which the shape of the cut-up 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), a ventilation passage (40) is formed between the heat transfer portions (70) adjacent to the flattening pipe (33) in the extending direction, and air flows through the ventilation passage (40). On the other hand, in the heat transfer portion 70 of each fin 36, bulging portions 81 to 83 bulging out in a predetermined direction (in this embodiment, the right side as viewed from the leading edge 38 side of the fin 36) are formed . Therefore, the portion of the ventilation path 40 which comes into contact with the bulging portions 81 to 83 of the heat transfer portion 70 becomes a shape that meanders along the bulging portions 81 to 83.

The air flowing into the ventilation path 40 from the side of the leading edge 38 of the pin 36 flows while hitting the meandering portion of the ventilation path 40 against the bulging portions 81 to 83. As a result, the airflow in the ventilation path (40) is disturbed by colliding with the bulging portions (81 to 83) and changing its direction. As a result, the heat transfer between the air flowing through the ventilation path 40 and the heat transfer portion 70 is promoted, as compared with the case where the heat transfer portion 70 is a flat plate having no unevenness.

Air flowing while passing over the bulging portions (81 to 83) in the ventilation path (40) strikes the windward side louver (50). At this time, the air over the ridge 83a of the third bulging portion 83 flows along the slope 83b on the downwind side, and then comes into contact with the louver 50 on the windward side. In the airfoil side louver 50, the cut-up end 53 on the downwind side protrudes in the direction in which the third swollen portion 83 extends. Thereby, when the air flowing along the downhill slope portion 83b of the third swollen portion 83 hits the airfoil side louver 50, the flow direction thereof is changed by the airfoil side louver 50. Thereby, the air flow in the ventilation path (40) is disturbed, and the heat transfer between the air and the heat transfer portion (70) is promoted.

As described above, the louvers 50 and 60 are formed by cutting up the heat transfer portion 70. Thus, in the heat exchanger 30, the air is exchanged between the adjacent ventilation paths 40 while sandwiching the heat transfer portion 70, and the air flow in the ventilation path 40 is greatly disturbed. As a result, compared to the case where the heat transfer portion 70 is a flat plate having no unevenness and the case where only the swelled portion is formed in the heat transfer portion 70, the heat transfer between the air flowing in the air passage 40 and the heat transfer portion 70 .

- Frost and drain water conditions at the pins -

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 the heating operation and in the operating state in which the evaporation temperature of the refrigerant in the outdoor heat exchanger 23 is lower than 0 ° C, the moisture in the outdoor air is frosted and is supplied to the outdoor heat exchanger 23 Respectively. Thereby, the air conditioner (10) performs the defrosting operation for melting the frost attached to the outdoor heat exchanger (23). During the defrosting operation, the frost melts to generate the drain water.

<Frost attachment to pin>

A process of adhering frost to the heat exchanger 30 constituting the outdoor heat exchanger 23 will be described. The air that has flown 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 portion 70 of the fin 36. In the state where the surface temperature of the heat transfer portion 70 is lower than 0 占 폚, moisture in the air is frozen, frosted, and attached to the surface of the heat transfer portion 70.

Generally, the effect of disturbing the airflow is that the louvers 50 and 60 formed by cutting and forming the heat transfer portion 70 are provided with the swelling portions 81 to 83 which merely cause the heat transfer portion 70 to bulge without being cut, Lt; / RTI &gt; Therefore, normally, the promoting effect of heat transfer is larger in the louvers 50, 60 than in the bulged portions 81 to 83.

On the other hand, in each of the heat transfer portions 70 of the fin 36, louvers 50 and 60 having relatively high heat transfer promoting effect are formed on the downwind side portion, and a heat transfer promoting effect Relatively low swelling portions 81 to 83 are formed. The amount of the frost adhering to the air bearing portion of the heat transfer portion 70 is reduced and the amount of the frost attached to the windward portion of the heat transfer portion 70 is smaller than that of the case where the louver is formed over the entire heat transfer portion 70 The amount increases. Therefore, in each heat transfer portion 70 of the fin 36, the difference between the amount of frost attached to the windward side portion and the amount of frost attached to the windward side portion becomes small.

The moisture in the air flowing through the ventilation path 41 is gradually frosted and attached to the heat transfer portion 70 in a state where the surface temperature of the heat transfer portion 70 is less than 0 占 폚. Accordingly, the absolute humidity of the air flowing through the ventilation path (40) decreases gradually toward the downwind side. The air having reached the louvers 50 and 60 having relatively high heat transfer promoting effect has a relatively low absolute humidity. Thereby, the amount of the frost adhering to the portions where the louvers 50 and 60 are formed in each heat transfer portion 70 of the fin 36 is not excessively increased.

The ventilation path 40 formed by the heat transfer portion 70 in which the bulging portions 81 to 83 are formed becomes a meander along the bulging portions 81 to 83 as described above. If the height of the bulge portion in the bulging direction is the same, the larger the width of the bulge portion in the air passing direction, the smaller the change in the air flow direction flowing along the bulge portion is. When the air flow direction of the bulged portion is the same, the lower the height in the bulging direction of the bulged portion, the smaller the change in the air flow direction flowing along the bulged portion is. When the change in the direction of the airflow flowing along the bulge portion is small, the effect of accelerating the bulging due to the bulging portion is reduced. On the other hand, the temperature difference between the air flowing through the ventilation path 40 and the heat transfer portion 70 becomes the largest at the inlet of the ventilation path 40, and becomes gradually smaller toward the wind direction.

The width W1 of the first bulging portion 81 is wider than the width W2 of the second bulging portion 82 and the width W3 of the third bulging portion 83 in each heat transfer portion 70 of the present embodiment. In each heat transfer portion 70, the height H1 of the first bulging portion 81 is lower than the height H2 of the second bulging portion 82 and the height H3 of the third bulging portion 83. [ That is, each of the heat transfer portions 70 of the fin 36 is provided with a first bulging portion (hereinafter, referred to as &quot; first bulging portion &quot;) having a comparatively small heat transfer promoting effect at a position on the windward side where the temperature difference between the air flowing through the airflow path 40 and the heat transfer portion 70 is relatively large 81 are formed. As a result, the amount of frost adhered to the airfoil portion is reliably suppressed in each heat transfer portion 70 of the fin 36. [

As described above, in the heat exchanger 30 of the present embodiment, the frost is attached not only to the windward side portion of the fin 36, but also to the windward side portion thereof. Therefore, the amount of the frost attached to the heat exchanger 30 at the time when it is necessary to perform the defrosting operation is smaller than that of the conventional heat exchanger in which the heat exchanger 30 according to the present embodiment has the louver on the entire heat transfer portion More. Therefore, in the air conditioner 10 having the outdoor heat exchanger 23 constituted by the heat exchanger 30 of the present embodiment, compared with the air conditioner having the outdoor heat exchanger constructed of the conventional heat exchanger, The time interval until the defrosting operation is started becomes longer, and as a result, the duration of the heating operation becomes longer.

<Frost and drain water conditions during defrosting operation>

The state of the 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 and drained, and the generated drain water is discharged from the heat exchanger (30).

In the heat transfer portion 70 of the fin 36, when the frost attached to the heat transfer portion 70 is melted, the generated drain water flows downward. At this time, the frost attached to the windward end portion 72 of the heat transfer portion 70 is drained and falls downward from the windward end portion 72. On the other hand, the frost attached to the intermediate portion 71 of the heat transfer portion 70 is drained and stored on the flat side of the flat pipe 33.

The lower ends 81e, 82e and 83e of the respective bulged portions 81 to 83 are inclined in the respective heat transfer portions 70 of the pins 36. The lower ends 81e to 83e of the bulged portions 81 to 83 are inclined from the lower end of the heat transfer portion 70, (81e, 82e, 83e) is gradually shortened toward the downwind side. The distance from the flattened pipe 33 located below each of the heat transfer portions 70 to the lower ends 81e, 82e and 83e of the bulged portions 81 to 83 gradually narrows toward the downwind side . The drain water flowing down from the bulged portions 81 to 83 and stored on the flat pipe 33 is discharged from the flat pipe 33 to the lower ends 81e, 82e, 83e of the bulged portions 81 to 83 Is sucked by the capillary phenomenon to the short downwind side. That is, during the defrosting operation, the outdoor fan (15) is stopped and the drain number is shifted downwindly, although the upper surface of the flat pipe (33) is in a substantially horizontal plane.

Thus, in the heat exchanger 30 of the present embodiment, the drain water generated during the defrosting operation is reliably discharged downwind. Thereby, the amount of drain water remaining on the surface of the heat transfer portion 70 at the end of the defrosting operation is reduced. If the drainage water remains on the surface of the heat transfer portion 70, the remaining drainage amount after the heating operation is resumed is frozen, and the time until it becomes necessary to perform the defreeging operation again becomes shorter. Therefore, in the air conditioner 10 having the outdoor heat exchanger 23 constituted by the heat exchanger 30 of the present embodiment, compared with the air conditioner having the outdoor heat exchanger constructed in the conventional heat exchanger, at the end of the defrosting operation The elapsed time until the start of the next defrosting operation (i.e., the duration of the heating operation) becomes longer.

Incidentally, as described above, in the heat exchanger 30 of the present embodiment, a part of the windward side louvers 50a is an asymmetric louver. That is, in this airfoil side louver 50a, the inclination angle [theta] 2 of the lower side edge portion 56 becomes smaller than the inclination angle [theta] 1 of this upper side edge portion 55 (see FIG. 8, gaps formed between the respective lower side edge portions 56 between the air side louvers 50a adjacent to the air passage direction are formed between the respective upper side edge portions 55 It becomes thinner and longer than the gap formed.

Generally, a relatively large capillary force acts on a liquid present in a relatively narrow gap. Further, the capillary force acting on the liquid becomes larger as the gap becomes narrower. On the other hand, as shown in Fig. 8, the lower side edge portions 56 contacting the lower end of the drain water in the state in which the drainage water enters between the cut-up end portions 53 of the air side louver 50a adjacent to the air passage direction Is narrower than the interval between the peripheral edge portions (54) contacting the upper end of the drain water. Therefore, the downward capillary force acting on the drain water is larger than the upward capillary force, and the drain water is sucked to the lower side edge 6 (i.e., the lower side).

In addition, the lower side edge portion 56 of the air side louver 50a, which is an asymmetric louver, is relatively long. As a result, between the airfoil side louvers 50a adjacent to the air passage direction, the narrowed area between the cut-up ends 53 is widened. As a result, the area where the downward capillary force acting on the drain water is larger than the upward capillary force is enlarged, and the possibility that the drain water moves downward by the capillary force increases.

As described above, the drain water that has entered between the cut-up ends 53 of the airfoil side louvers 50a adjacent to the air passing direction has a narrow narrow gap between the lower side edge portions 56, Sucked by. That is, this drain number flows downward not only by gravity but also by capillary phenomenon. Therefore, the drain water generated in the vicinity of the louver 50a during the defrosting operation is quickly discharged downward and held between the cut-up ends 53 of the louver 50a adjacent to the air flow direction .

Each of the heat transfer portions 70 of the pin 36 is formed in the intermediate portion 71 close to the flat pipe 33 as compared with the windward side louver 60 formed on the downwind end portion 73 remote from the flat pipe 33. [ The amount of frost to be adhered to the windward side louver 50 increases. Among the louvers 50 on the windward side, the amount of frost adhering to the windward side louver 50a located on the windward side is larger than that on the windward side louver 50b located on the downwind side. As a result, the amount of drain water generated during the defrosting operation becomes greater as the windward side louver 50 is located on the windward side.

On the other hand, in each of the heat transfer portions 70 of the fin 36 of the present embodiment, a part of the air side louvers 50a located on the air side is an asymmetric louver. That is, in each heat transfer portion 70, the windward side louver 50a on the windward side where the amount of drain water generated during the defrosting operation is increased becomes an asymmetric louver which is difficult to maintain the drain water. Therefore, the amount of drain water remaining on the surface of the heat transfer portion 70 at the end of the defrosting operation is also reduced by using some of the louvers 50a as the asymmetric louvers.

- Effect of the first embodiment -

As described above, according to the heat exchanger 30 of the present embodiment, during the heating operation of the air conditioner 10, frost is attached to not only the windward portion but also the windward portion of the heat transfer portion 70 of the pin 36 . Therefore, by configuring the outdoor heat exchanger 23 of the air conditioner 10 with the heat exchanger 30 of this embodiment, the duration of the heating operation can be prolonged.

According to the heat exchanger 30 of the present embodiment, the amount of drain water remaining on the surface of the heat transfer portion 70 at the end of the defrosting operation can be reduced. The drain water remaining on the surface of the heat transfer portion 70 is frozen after resumption of heating operation. As a result, if the number of drains remaining on the surface of the heat transfer portion 70 decreases, the time until the next defrosting operation becomes necessary becomes longer. Therefore, by configuring the outdoor heat exchanger 23 of the air conditioner 10 with the heat exchanger 30 of this embodiment, the duration of the heating operation can be prolonged.

As described above, by configuring the outdoor heat exchanger 23 of the air conditioner 10 as the heat exchanger 30 of the present embodiment, the duration of the heating operation can be extended and the time required for the defrosting operation can be shortened . Therefore, when the outdoor heat exchanger 23 of the air conditioner 10 is configured by the heat exchanger 30 of the present embodiment, the time average value of the heating capacity of the air conditioner 10 (that is, The actual heating capacity of the heater can be increased.

`` Second Embodiment ''

A second embodiment of the present invention will be described. The heat exchanger 30 of the second embodiment constitutes the outdoor heat exchanger 23 of the air conditioner 10 in the same manner as the heat exchanger 30 of the first embodiment. Hereinafter, the heat exchanger 30 of the present embodiment will be described with reference to FIGS. 9 to 12 as appropriate.

<Overall Configuration of Heat Exchanger>

9 and 10, the heat exchanger 30 of the present embodiment includes one first header collecting tube 31, one second header collecting tube 32, a plurality of flat tubes 33, , And a plurality of pins (35). The first header collecting tube 31, the second header collecting tube 32, the flat tube 33 and the fins 35 are both made of aluminum alloy and are joined to each other by brazing.

The construction and arrangement of the first header collecting tube 31, the second header collecting tube 32 and the flat tube 33 are the same as those of the heat exchanger 30 of the first embodiment. That is, the first header collecting tube 31 and the second header collecting tube 32 are all formed into a vertically elongated cylindrical shape, one of which is located at the left end of the heat exchanger 30, the other is located at the right side of the heat exchanger 30 Respectively. On the other hand, the flat pipe 33 is a heat transfer pipe having a flat cross-sectional shape, and each of the flat side surfaces is arranged vertically in a facing posture. A plurality of fluid passages (34) are formed in each flat pipe (33). One end of the flat pipe 33 is inserted into the first header collecting tube 31 and the other end of the flat tube 33 is inserted into the second header collecting tube 32.

The pin 35 is a corrugated fin which meanders upward and downward, and is disposed between the vertically adjoining flat pipes 33. The fin 35 is provided with a plurality of heat transfer portions 70 and intermediate plate portions 41 in detail. Each of the fins 35 is joined to the flat pipe 33 by soldering the middle plate portion 41.

10, in the heat exchanger 30, the spaces between the vertically adjacent flat tubes 33 are partitioned into the plurality of ventilation paths 40 by the heat transfer portions 70 of the fins 35. As shown in Fig. The heat exchanger 30 heat-exchanges the refrigerant flowing through the fluid passage 34 of the flat tube 33 with the air flowing through the ventilation passage 40.

As described above, the heat exchanger 30 has a plurality of flat tubes 33 arranged vertically so as to face flat sides, and a plate-like heat transfer section 70 extending from one side of the adjacent flat tubes 33 to the other side And has a plurality of pins (35). A plurality of heat transfer portions 70 are arranged in the extending direction of the flat tubes 33 between the adjacent flat tubes 33. In this heat exchanger (30), the air flowing between the adjacent heat transfer portions (70) exchanges heat with the fluid flowing in each flat pipe (33).

<Configuration of the pin>

As shown in Fig. 12, the pin 35 is a corrugated fin formed by bending a metal plate having a constant width, and has a shape that meanders vertically. The heat transfer portion 70 and the intermediate plate portion 41 are alternately formed in the pin 35 along the extending direction of the flat tube 33. That is, a plurality of heat transfer portions 70, which are arranged between adjacent flat pipes 33 and arranged in the extending direction of the flat pipe 33, are formed on the fins 35. In addition, the projecting plate portion 42 is formed on the pin 35. 12, illustration of later-described swelling portions 81 to 83 and louvers 50 and 60 is omitted.

The heat transfer portion 70 is a plate-shaped portion extending from one side to the other side of the vertically adjacent flat pipe 33. In the heat transfer portion 70, the end on the windward side becomes the leading edge 38, and the edge on the downward side becomes the trailing edge 39. [ The intermediate plate portion 41 is a plate-shaped portion along the flat side surface of the flat tube 33 and is continuous to the upper ends or lower ends of the adjacent heat transfer portions 70. The angle formed by the heat transfer portion 70 and the intermediate plate portion 41 is substantially perpendicular.

11, each heat transfer portion 70 of the pin 35 has an intermediate portion 71, a windward end portion 72, and a windward end portion 73. [ Each of the heat transfer portions 70 is provided with an intermediate portion 71 which overlaps with the flat pipe 33 adjacent to the upper and lower portions (that is, a portion located directly above or below the flat pipe 33 vertically adjacent thereto) . In the respective heat transfer portions 70, the portion located on the windward side from the intermediate portion 71 (that is, the portion projecting to the windward side from the flat pipe 33) becomes the airfoil end portion 72, and the intermediate portion 71 (That is, a portion protruding downward from the flattening pipe 33) becomes a downward windward end portion 73. The windward end portion 73 is a portion of the windward end portion 73 which is located lower than the flattening pipe 33.

Two stone projecting portions 42 are formed in each heat transfer portion 70. The stone publishing section 42 is formed in a trapezoidal plate shape continuous with the windward lower end portion 73. One projecting portion 42 projects upward from the upper end of the windward lower end portion 73 and the other projected portion 42 projects downward from the lower end of the windward end portion 73 in each heat transfer portion 70 . In the heat exchanger (30), the projecting portions (42) of the upper and lower adjacent fins (35) sandwich the flat tube (33) therebetween.

11, each of the heat transfer portions 70 of the fin 35 is provided with a plurality of swelling portions 81 to 83 and louvers 50 and 60. As shown in Fig. As in the case of the pin 36 of the first embodiment, the heat transfer portions 70 are formed with swollen portions 81 to 83 on the windward side and louvers 50 and 60 on the windward side. That is, in each of the heat transfer portions 70, louvers 50 and 60 are formed only on the downwind portion, and the swelling portions 81 to 83 are formed on the windward side portions of all the louvers 50 and 60.

<Arrangement and Shape of Expansion Portion>

The arrangement and shape of the bulged portions 81 to 83 formed on the pin 35 will be described. "Right" and "left" used in this description mean the direction when the fin 35 is viewed from the windward side (that is, the front side of the heat exchanger 30).

11, the arrangement of the bulged portions 81 to 83 of each heat transfer portion 70 of the pin 35 and the shape of each of the bulged portions 81 to 83 are the same as those of the pin 36 of the first embodiment to be. It is also similar to the first embodiment in that the number of bulge portions 81 to 83 shown below and the bulge direction are only one example.

Specifically, each of the bulged portions 81 to 83 is formed by bulging the heat transfer portion 70 toward the ventilation path 40, and the ridgelines 81a, 82a, and 82a are formed by piling up the leading edge 38 of the pin 35 So that it becomes a substantially parallel mountain shape. Each of the bulged portions 81 to 83 bulges to the right side of the heat transfer portion 70.

Three swelling portions 81 to 83 are arranged in the air passing direction (that is, in the direction from the leading edge 38 to the trailing edge 39 of the pin 35) in each heat transfer portion 70. The three bulging portions 81 to 83 are formed in the respective heat transfer portions 70 over the windward end portions 72 and the windward portions of the intermediate portion 71. [

In each heat transfer portion 70, the width of the first swollen portion 81 in the air passing direction is widest among the three swollen portions 81 to 83. The widths of the second swollen portion 82 and the third swollen portion 83 in the air passing direction are equal. In each heat transfer portion 70, the height of the first bulging portion 81 in the bulging direction is the lowest among the three bulging portions 81 to 83. The height of the second bulging portion 82 in the bulging direction is lower than the bulge height direction of the third bulging portion 83.

The lower ends 81e, 82e and 83e of the respective swollen portions 81 to 83 are inclined such that the downwind side is downward. The distances from the lower end of the heat transfer portion 70 to the lower ends 81e, 82e and 83e of the bulged portions 81 to 83 are gradually shortened toward the windward side in each heat transfer portion 70.

&Lt; Arrangement and shape of louver &

The arrangement and shape of the louvers 50 and 60 formed on the pin 35 will be described. The "right" and "left" used in this description mean the direction when viewed from the windward side (that is, the front surface of the heat exchanger 30) of the fins 35.

11, the arrangement of the louvers 50, 60 of each heat transfer portion 70 of the pin 35 and the shape of each of the louvers 50, 60 are the same as those of the pin 36 of the first embodiment . In addition, the number of louvers 50 and 60 shown in the drawing is only one example, which is the same as the first embodiment.

Specifically, in each heat transfer portion 70 of the fin 35, a plurality of louvers 50 and 60 are provided in a portion extending from the downwind region of the intermediate portion 71 to the downwind end portion 73 in the air passing direction Respectively. A group of louvers arranged on the windward side constitute the windward side louver 50, and a group of louvers arranged on the windward side constitute the windward side louver 60. The lengths of the louvers 50 and 60 are equal to each other.

In each heat transfer portion 70 of the pin 35, the part of the airfoil side louver 50a located on the windward side is an asymmetric louver. In each of the heat transfer portions 70, a part of the windward side louver 50b and all of the downwind side louvers 60 located downwind are symmetrical louvers.

In each of the heat transfer portions 70 of the pin 35, the windward side louver 50 and the windward side louver 60 are inclined in opposite directions to each other. In the louver 50 on the windward side, the cut-up stand 53 on the windward side is bulged to the left, and the cut-up stand 53 on the windward side is bulged to the right. That is, the wind-up side louver 50 is projected in the same direction as the bulging direction of the third bulging portion 83, On the other hand, in the downward windward side louver 60, the cut-up end 63 on the downwind side bulges to the right and the cut-off end 63 on the downwind side bulges to the left.

Effects of the Second Embodiment

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 bulge portions 81 to 83 are formed on the airfoil side portions of the respective heat transfer portions 70 of the fins 35, Louvers 50 and 60 are respectively formed. In the heat exchanger 30 of the present embodiment, similarly to the first embodiment, the width of the first bulging portion 81 located at the most upstream side is the widest, and the height in the bulging direction is the lowest . Therefore, in each heat transfer portion 70 of the fin 35, the difference between the amount of frost attached to the windward side portion and the amount of frost attached to the windward side portion becomes small. As a result, the duration of the heating operation of the air conditioner (10) can be prolonged, and the substantial heating capability of the air conditioner (10) can be improved.

In the heat exchanger 30 of the present embodiment, the lower ends 81e, 82e and 83e of the bulging portions 81 to 83 are inclined and the upper side louvers 50a is an asymmetric louver. Therefore, the amount of drain water remaining on the surface of the heat transfer portion 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) .

`` Third embodiment ''

A third embodiment of the present invention will be described. The heat exchanger (30) of the third embodiment is a modification of the configuration of the fin (36) in the heat exchanger (30) of the first embodiment. Here, the pin 36 provided in the heat exchanger 30 of the present embodiment is different from the pin 36 provided in the heat exchanger 30 of the first embodiment.

13 and 14, the pin 36 of this embodiment is provided with the first bulging portion 81, the second bulging portion 82, and the second bulging portion 82, similarly to the pin 36 of the first embodiment. Three bulging portions 83, and an airfoil side louver 50 are formed. In addition, in the pin 36 of the present embodiment, a downwind side swollen portion 85 is formed instead of the downwind side louver 60. The auxiliary swelling portion 86, the upper horizontal rib 91, and the lower horizontal rib 92 are added to the pin 36 of the present embodiment. The pin 36 of the present embodiment differs from the pin 36 of the first embodiment in the arrangement of the tabs 81. [

The first bulging portion 81, the second bulging portion 82 and the third bulging portion 83 formed on the pin 36 of the present embodiment are different in shape and arrangement from the first embodiment . The point that the first bulging portion 81, the second bulging portion 82 and the third bulging portion 83 are arranged in order from the leading edge 38 of the fin 36 to the trailing edge 39, This is similar to the first embodiment.

Each of the heat transfer portions 70 of the pin 36 of the present embodiment has the first bulged portion 81 formed from the airfoil end portion 72 to the intermediate portion 71 and the second bulged portion 82 and the Three swelling portions 83 are formed in the intermediate portion 71. The upper ends 81d to 83d and the lower ends 81e to 83e of the respective bulged portions 81 to 83 are substantially orthogonal to the leading edge 38 of the pin 36. [ The length of the first bulging portion (81) is shorter than the length of the second bulging portion (82). The length of the second bulging portion (82) is equal to the length of the third bulging portion (83). The widths of the respective swollen portions 81 to 83 are widened in order of the third swollen portion 83, the first swollen portion 81 and the second swollen portion 82 (W3 <W1 <W2). The heights of the respective bulge portions 81 to 83 in the bulging direction are equal to each other (H1 = H2 = H3).

In the pin 36 of the present embodiment, as in the first embodiment, a plurality of louvers 50 are formed on the windward side of the third bulging portion 83. As in the first embodiment, a part of the louver 50a located on the windward side is an asymmetric louver, and the remaining louver 50b located on the windward side is a symmetrical louver. In the pin 36 of the present embodiment, similarly to the first embodiment, the cut-up end 53 on the downwind side of each louver 50 protrudes in the bulge direction of the third bulging portion 83 14 (B)).

The distance L1 between the upper ends of the second swollen portion 82 and the third swollen portion 83 to the upper end of the intermediate portion 71 and the distance L1 between the upper end of the second swollen portion 82 and the upper portion of the intermediate portion 71, The distance L2 from the lower end of the third bulging portion 83 to the lower end of the intermediate portion 71, the distance L3 from the upper end of the louvers 50a and 50b to the upper end of the intermediate portion 71, The distance L4 from the lower end of the intermediate portion 71 to the lower end of the intermediate portion 71 are equal to each other.

In the pin 36 of the present embodiment, the tab 48 is formed on the windward end portion 72 of the heat transfer portion 70 as in the first embodiment. In the heat transfer portion 70 of the present embodiment pin 36, however, one tab 48 is formed on the windward side portion of the windward end portion 72 on the windward side portion than the first bulging portion 81. The tab 48 is disposed in the vicinity of the center in the vertical direction of the windward end portion 72. The tab 48 is inclined with respect to the leading edge 38 of the pin 36.

An upper horizontal rib 91 and a lower horizontal rib 92 are formed in each heat transfer portion 70 of the pin 36. [ The upper horizontal rib 91 is formed on the upper side of the first swollen portion 81 and the lower horizontal rib 92 is formed on the lower side of the first swollen portion 81. Each of the horizontal ribs 91 and 92 has an elongated shape of a straight line extending from the leading edge 38 of the pin 36 to the second bulging portion 82. Each of the horizontal ribs 91 and 92 is formed by expanding the heat transfer portion 70 toward the ventilation path 40 in the same manner as the respective bulging portions 81, 82, 83 and 84. The direction in which the horizontal ribs 91 and 92 extend is the same as the direction in which the respective bulged portions 81 to 83 expand.

One auxiliary swelling portion 86 is formed in each of the heat transfer portions 70 of the pin 36. In each heat transfer portion 70, the auxiliary swollen portion 86 is disposed on the windward side of the louver 50. In each heat transfer portion 70, the auxiliary swollen portion 86 is formed from the intermediate portion 71 to the windward lower end portion 73.

The auxiliary swollen portion 86 is formed in a mountain shape by expanding the pin 36. [ The auxiliary swollen portion (86) extends in a direction intersecting with the air passing direction in the ventilation path (40). In the pin 36 of the present embodiment, the auxiliary swollen portions 86 are bulged to the right as seen from the leading edge 38 of the pin 36. [ The ridge 85a of the auxiliary swelling portion 86 is substantially parallel to the leading edge 38 of the pin 36. [ That is, the ridge line 85a of the auxiliary swollen portion 86 crosses the direction of the air flow in the ventilation path 40. The lower end of the auxiliary swollen portion 86 is inclined so as to be downward by the windward side.

The height H5 of the auxiliary swelling portion 86 in the swelling direction is lower than the height H3 of the third swelling portion 83 in the swelling direction (H5 < H3), as shown in Fig. 14B. 14A, the width W5 of the auxiliary swelling portion 86 in the air passing direction is narrower than the width W3 of the third swelling portion 83 in the air passing direction (W5 <W3).

The downstream-side bulged portions 85 are formed one by one on the downstream side of the notched portions 45. Each downwind-side bulged portion 85 is formed over a connecting plate portion 75, a downwind end portion 73 on the connecting plate portion 75, and a downwind end portion 73 below the connecting plate portion 75.

The downwind side bulged portion 85 is formed in a mountain shape by causing the pin 36 to bulge. The downwind side bulging portion 85 extends in a direction intersecting the air passage direction of the ventilation path 40. In the pin 36 of the present embodiment, each downwind-side swollen portion 85 is bulged to the right as seen from the leading edge 38 of the pin 36. [ The ridgeline 84a of the downwind side bulging portion 85 is substantially parallel to the leading edge 38 of the pin 36. [ That is, the ridgeline 84a of the downwind-side swollen portion 85 crosses the direction of air flow in the ventilation path 40.

As shown in Fig. 14B, the height H4 of the downwind side bulging portion 85 in the bulging direction is equal to the height H2 in the bulging direction of the second bulging portion 82 (H4 = H2). 14A, the width W4 of the downward swelling portion 85 in the air passing direction is equal to the width W2 of the second swelling portion 82 in the air passing direction (W4 = W2).

In the pin 36 of the present embodiment, one tab 48 is formed between adjacent downwind-side bulged portions 85. That is, in this pin 36, one tab 48 is formed at the windward end portion 73 of each heat transfer portion 70.

Effect of the third embodiment

According to the heat exchanger 30 of the present embodiment, the same effects as those of the heat exchanger 30 of the first embodiment can be obtained.

That is, in the heat exchanger 30 of the present embodiment, as in the first embodiment, the swelling portions 81 to 83 are formed on the air side portions of the respective heat transfer portions 70 of the fins 36, 81 to 83) The louver 50 is formed on the downwind side. Therefore, in each heat transfer portion 70 of the fin 36, the difference between the amount of frost attached to the windward side portion and the amount of frost attached to the windward side portion becomes small. As a result, the duration of the heating operation of the air conditioner 10 can be prolonged. The substantial heating capacity of the air conditioner 10 can be improved.

&Lt; Other Embodiments &gt;

Modifications of the heat exchanger 30 of the first and second embodiments will be described.

- Modified Example 1 -

All the windward side louvers 50 formed on the respective heat transfer portions 70 of the fins 35 and 36 may be asymmetric louvers.

15 shows the application of this modification to the fin 36 of the heat exchanger 30 of the first embodiment. All the windward side louvers 50 are asymmetric louvers and all the windward side louvers 60 are symmetrical louvers in each heat transfer portion 60 of the pin 36 shown in the same figure.

- Modified Example 2 -

Each of the heat transfer portions 70 of the fins 35 and 36 formed in the heat exchanger 30 of each of the above embodiments is provided with a plurality of bulging portions 81 and 82 over the whole of the windward end portion 72 and the intermediate portion 71 83, and 84 may be formed, and the louver 60 may be formed only at the windward end portion 73. [

16 shows the application of the present modification to the fin 36 of the heat exchanger 30 of the first embodiment. In the respective heat transfer portions 70 of the pin 36 shown in the same figure, the four bulging portions 81, 82, 83, and 84 are formed in the airflow end portion 72 and the intermediate portion 71, And are arranged in the passing direction. The fourth swollen portion 84 located at the most downstream side is formed adjacent to the third swollen portion 83. All of the louvers 60 formed on the windward end portion 73 are symmetrical louvers.

- Modified Example 3 -

The portions where the louvers 50 and 60 are formed may bulge toward the ventilation path 40 in the respective heat transfer portions 70 of the fins 35 and 36 formed in the heat exchanger 30 of the respective embodiments.

Fig. 17A shows the application of the present modification to the heat exchanger 30 pin 36 of the first embodiment. The portions where the louvers 50 and 60 are formed are bulged in the same direction as the bulged portions 81 to 83 in the respective heat transfer portions 70 of the pin 36 shown in the same figure. Specifically, a portion of each heat transfer portion 70 where the airfoil side louver 50 is formed is inclined in the same direction as the airfoil side slope portions 81b, 82b, 83b of the respective swollen portions 81 to 83. The portions where the downward wind direction louvers 60 are formed in each of the heat transfer portions 70 are inclined in the same direction as the slope portions 81b, 82b, 83b on the downstream side of the respective swollen portions 81 to 83. [

- Fourth Modification -

The inclined direction of each of the louvers 50 and 60 may be opposite to each other in each of the heat transfer portions 70 of the fins 35 and 36 formed in the heat exchanger 30 of the respective embodiments.

Fig. 17 (B) shows that this modification is applied to the fin 36 of the heat exchanger 30 of the first embodiment. In the respective heat transfer portions 70 of the pin 36 shown in the figure, the wind-up side louver 50 is formed such that the wind-up side end 63 is bulged to the right and the wind- To the left. That is, the windward side cut-and-raised end 53 of the airfoil side louver 50 protrudes in the same direction as the direction in which the third swollen portion 83 extends. On the other hand, in the downward windward side louver 60, the cut-up end 53 on the windward side is bulged to the left, and the cut-up end 53 on the windward side is bulged to the right. Here, "right" and "left" used in this description mean the direction when the fin 36 is viewed from the air side (that is, the front side of the heat exchanger 30).

It is to be understood that the above-described embodiments are essentially preferred examples and are not intended to limit the scope of the present invention, its application, or its use.

[Industry availability]

INDUSTRIAL APPLICABILITY As described above, the present invention is useful for a heat exchanger having a flat tube and a pin arranged up and down.

10: air conditioner 20: refrigerant circuit
30: heat exchanger 33: flat tube
34: fluid passage (passage) 35, 36: pin
38: leading edge 40: ventilation path
41: middle plate portion 45: notch portion
50: louver on the rising side (louver) 50a: louver on the rising side (asymmetric louver)
53, 63: cut-out stand 54, 64:
55, 65: upper edge 56, 66: lower edge
60: louver on the downwind side (louver) 70:
72: windward end portion 73: windward end portion
81: first bulging portion 82: second bulging portion
83: third bulging portion 84: fourth bulging portion

Claims (14)

A plurality of flat pipes 33 are arranged up and down so that side surfaces thereof face each other, and a fluid passage 34 is formed therein, and a plurality of ventilation paths 40 through which air flows between the adjacent flat pipes 33. With a plurality of pins 35, 36 to make,
The fins (35) and (36) are formed in a plate shape extending from one side of the adjacent flat pipe (33) to the other side, and have a plurality of heat transfer portions (70) constituting side walls of the ventilation path ,
In each heat transfer portion (70) of the fins (35, 36)
A plurality of louvers (50, 60) formed by cutting up the heat transfer portion (70)
The bulging parts 81-83 are formed in the wind up-side part rather than the louvers 50 and 60, and are formed by expanding the heat transfer part 70, and extending in the direction crossing the air passage direction. Heat exchanger, characterized in that. The method according to claim 1,
Some of the louvers 50 positioned on at least the bulging portions 81 to 83 of the louvers 50 and 60 formed on the heat transfer parts 70 of the fins 35 and 36 are winds down of the louvers 50. A heat exchanger characterized in that the side 53 cut off protrudes in the expansion direction of the bulges 81 to 83. The method according to claim 1 or 2,
The cut ends 53 and 63 of the louvers 50 and 60 are peripheral portions 54 and 64 and portions extending from the upper ends of the peripheral portions 54 and 64 to the upper ends of the louvers 50 and 60, Upper edge portions 55 and 65 inclined with respect to the peripheral edges 54 and 64 and portions extending from the lower edge of the peripheral edges 54 and 64 to the lower ends of the louvers 50 and 60, And a lower side edge portion (56, 66)
At least a part of the louvers 50 and 60 of each of the heat transfer portions 70 of the fins 35 and 36 are arranged such that the inclination of the lower side edge portion 56 with respect to the peripheral edge portion 54 is smaller than the inclination angle of the upper side edge portion 55, Is a gentle asymmetric louver than the slope of the circumferential portion (54) of the heat exchanger (54). The method according to claim 3,
Wherein the louver (50) formed in a portion adjacent to the flat pipe (33) in each heat transfer portion (70) of the fins (35, 36) is the asymmetric louver. The method according to claim 1,
Each of the heat transfer portions 70 of the fins 35 and 36 is provided with a downward windward end portion 73 located below the flattened pipe 33,
Wherein the louver (60) is formed on the windward end portion (73) of each heat transfer portion (70) of the fins (35, 36). The method according to claim 1,
Wherein each of the heat transfer portions (70) of the fins (35, 36) has a plurality of the bulged portions (81 to 83) arranged in the air flow direction. The method of claim 6,
The plurality of the bulging portions 81 to 83 formed in the respective heat transfer portions 70 of the fins 35 and 36 are arranged in such a manner that the width of the bulged portion 81 located on the most wind And wherein the heat exchanger is made wide. The method according to claim 6 or 7,
The plurality of the bulged portions 81 to 83 formed in the respective heat transfer portions 70 of the fins 35 and 36 are characterized in that the height of the bulged portion 81 located at the most air- Heat exchanger. The method of claim 6,
In each of the heat transfer portions 70 of the fins 35 and 36, a portion from the airfoil side end portion 38 of the heat transfer portion 70 to the position below the center in the air passing direction of the heat transfer portion 70, And a plurality of the bulging portions (81 to 83) are formed. The method of claim 6,
Each of the heat transfer portions 70 of the fins 35 and 36 has an airfoil end 72 located on the windward side of the flat pipe 33,
The plurality of the bulging portions 81 to 83 are formed in the respective heat transfer portions 70 of the fins 35 and 36 over the windward end portion 72 and the windward side portion of the windward end portion 72 Features a heat exchanger. The method of claim 6,
Wherein each of the heat transfer portions (70) of the fins (35, 36) is inclined such that the lower ends of the respective bulged portions (81 to 83) are downward by the windward side. The method according to claim 1,
The pin 36 is formed in a plate shape in which a plurality of notch portions 45 for fitting the flat tube 33 are formed and is arranged at a predetermined interval in the extending direction of the flat tube 33 And the flat pipe 33 is sandwiched by the periphery of the notch 45,
Wherein a portion of the pin (36) between the vertically adjacent notches (45) constitutes the heat transfer portion (70). The method according to claim 1,
The fin 35 is a meandering corrugated fin disposed between adjoining flat tubes 33. The plurality of heat transfer portions 70 arranged in the direction of extension of the flat tubes 33, , And a plurality of intermediate plate portions (41) joined to the flat tube (33), the portions continuing to the upper or lower end of the adjacent heat transfer portion (70). A refrigerant circuit (20) provided with a heat exchanger (30) according to claim 1,
And a refrigerating cycle by circulating the refrigerant in the refrigerant circuit (20).

Images