JP2008249299A - Fin tube type heat exchanger and air conditioner - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a fin tube type heat exchanger, preventing lowering of heat exchange performance in the fin tube type heat exchanger. <P>SOLUTION: This fin tube type heat exchanger includes: a heat transfer fin 6; and a heat transfer pipe 3. A plurality of heat transfer pipes have a first heat transfer pipe part 3a and a second heat transfer pipe part 3b. In the heat transfer fin, a first erected part 61a and a second erected part 65a are formed by erecting machining. The first erected part is disposed in a first heat transfer fin part 6a in the vicinity between the first heat transfer pipe part and the second heat transfer pipe part. The second erected part is disposed in a second heat transfer fin part 6c different from the first heat transfer fin part. A first projection angle β31 made by first straight lines L41a, L41b virtually connecting from the center of the heat transfer pipe to both ends of the first erected part, is larger than a second projection angle γ31 made by second straight lines L51a, L51b virtually connecting from the center of the heat transfer pipe to both ends of the second erected part. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a finned tube heat exchanger, in particular, heat transfer fins arranged in an air flow, and a plurality of heat transfer tubes inserted in the heat transfer fins and arranged in a direction substantially perpendicular to the flow direction of the air flow, The present invention relates to a finned-tube heat exchanger provided with an air conditioner having the finned-tube heat exchanger.

Conventionally, as a technique for improving the heat exchange efficiency of the finned tube heat exchanger, a method is known in which a cut-and-raised portion is arranged so as to guide the airflow to the rear side in the airflow direction of the heat transfer tube (see Patent Document 1).
JP 2007-10279 A

  In the heat exchanger as in the technique of Patent Document 1, when functioning as a condenser, the superheated gas refrigerant flows in the heat transfer tube in the vicinity of the refrigerant inlet, and in the heat transfer tube in the vicinity of the refrigerant outlet. In this state, the liquid refrigerant that has become supercooled flows. Then, when the refrigerant in the overheated state or the overcooled state exchanges heat with the air around the heat exchanger, it performs heat exchange by sensible heat transfer without accompanying latent heat transfer. Further, there is a temperature difference between the refrigerant in the overheated state or the supercooled state and the refrigerant in the gas-liquid two-phase state. For this reason, in the vicinity of the refrigerant inlet and in the vicinity of the refrigerant outlet, heat exchange is performed between refrigerants having different temperatures due to heat conduction in the heat transfer fins, resulting in poor heat exchange efficiency. The fact that the refrigerant in the overheated state and the overcooled state occupies a part of the heat exchanger causes the performance of the heat exchanger to deteriorate.

  An object of the present invention is to provide a finned tube heat exchanger that prevents deterioration in heat exchange performance in a finned tube heat exchanger.

  The finned tube heat exchanger according to the first invention includes a heat transfer fin and a plurality of heat transfer tubes. The heat transfer fin is disposed in the airflow. The plurality of heat transfer tubes are inserted into the heat transfer fins, and are arranged so as to form a heat transfer tube array in a direction crossing the airflow direction. The plurality of heat transfer tubes have a first heat transfer tube portion and a second heat transfer tube portion. A superheated gas refrigerant or a supercooled liquid refrigerant flows through the first heat transfer tube portion. A gas-liquid two-phase refrigerant flows through the second heat transfer tube portion. In the heat transfer fin, a first cut and raised portion and a second cut and raised portion are formed by cutting and raising processing. A 1st raising part is arrange | positioned along the flow direction of airflow in the 1st heat-transfer fin part of the vicinity between the 1st heat-transfer tube part and the 2nd heat-transfer tube part. A 2nd raising part is arrange | positioned along the flow direction of an airflow in the 2nd heat-transfer fin part different from a 1st heat-transfer fin part. The first cut-and-raised portion and the second cut-and-raised portion are configured to flow air currents on both sides in the row direction of the heat transfer tube rows of the heat transfer tubes so that the air flow in the vicinity of the heat transfer tubes is guided to the rear side in the flow direction of the heat transfer tubes. Inclined with respect to direction. The first projection angle is larger than the second projection angle. The first projection angle is an angle formed by a first straight line that virtually connects both ends of the first cut and raised portion from the center of the heat transfer tube. The second projection angle is an angle formed by a second straight line that virtually connects both ends of the second cut and raised portion from the center of the heat transfer tube.

  In the present invention, the first cut-and-raised portion and the second cut-and-raised portion are formed so that the first projection angle is larger than the second projection angle. That is, the heat conduction between the first heat transfer tube portion and the second heat transfer tube portion is more likely to occur in the row direction of the heat transfer tube row than the second heat transfer fin portion. A first cut-and-raised portion that is unlikely to occur is formed. Therefore, it is possible to reduce the occurrence of heat exchange between the refrigerants inside the heat transfer tubes, and it is possible to suppress a decrease in heat exchange performance.

  A finned tube heat exchanger according to a second aspect of the present invention is the finned tube heat exchanger according to the first aspect of the present invention, wherein the first cut-and-raised part is a rear side in the flow direction of the airflow of the heat transfer tube. Line up straight on the 3rd straight line as guided by

  In the present invention, the first cut-and-raised portions are arranged straight on the third straight line. Accordingly, the vertical vortex can be generated by the upstream portion of the first cut-and-raised portion in the airflow direction, and the dead water area formed on the further rear side of the downstream portion of the first cut-and-raised portion in the airflow direction. Can be reduced.

  A finned tube heat exchanger according to a third aspect of the present invention is the finned tube heat exchanger according to the first or second aspect of the present invention, wherein the second cut-and-raised portion is configured such that the airflow in the vicinity of the heat transfer tube is the airflow of the heat transfer tube. They are arranged straight on the fourth straight line so as to be guided rearward in the flow direction.

  In the present invention, the second cut-and-raised portions are aligned straight on the fourth straight line. Accordingly, the vertical vortex can be generated by the upstream portion of the second cut-and-raised portion in the airflow direction, and the dead water area formed on the further rear side of the downstream portion of the second cut-and-raised portion in the airflow direction. Can be reduced.

  A finned tube heat exchanger according to a fourth aspect of the present invention includes a heat transfer fin and a plurality of heat transfer tubes. The heat transfer fin is disposed in the airflow. The plurality of heat transfer tubes are inserted into the heat transfer fins, and are arranged so as to form a heat transfer tube array in a direction crossing the airflow direction. The plurality of heat transfer tubes have a first heat transfer tube portion and a second heat transfer tube portion. A superheated gas refrigerant or a supercooled liquid refrigerant flows through the first heat transfer tube portion. A gas-liquid two-phase refrigerant flows through the second heat transfer tube portion. In the heat transfer fin, a plurality of first cut and raised portions and a plurality of second cut and raised portions are formed by cutting and raising. The plurality of first cut-and-raised portions are arranged along the airflow direction in the first heat transfer fin portion in the vicinity between the first heat transfer tube portion and the second heat transfer tube portion. The plurality of second cut-and-raised portions are arranged along the airflow direction in the second heat transfer fin portion different from the first heat transfer fin portion. The plurality of first cut-and-raised portions and the plurality of second cut-and-raised portions are arranged on both sides in the row direction of the heat transfer tube rows of the heat transfer tubes so that the air flow in the vicinity of the heat transfer tubes is guided to the rear side in the flow direction of the heat flow of the heat transfer tubes. In the direction of the air flow. The sum of the first projection angles is larger than the sum of the second projection angles. The first projection angle is an angle formed by a first straight line that virtually connects both ends of each first cut and raised portion from the center of the heat transfer tube. The second projection angle is an angle formed by a second straight line that virtually connects both ends of each second raised portion from the center of the heat transfer tube.

  In the present invention, when there are a plurality of first cut-and-raised portions and second cut-and-raised portions, the total sum of the first projection angles formed by the first straight line that virtually connects both ends of each first cut-and-raised portion is The sum of the second projection angles formed by the second straight line that virtually connects both ends of the two cut and raised portions is larger. That is, the heat conduction between the first heat transfer tube portion and the second heat transfer tube portion is more likely to occur in the row direction of the heat transfer tube row than the second heat transfer fin portion. A first cut-and-raised portion that is unlikely to occur is formed. Therefore, it is possible to reduce the occurrence of heat exchange between the refrigerants inside the heat transfer tubes, and it is possible to suppress a decrease in heat exchange performance.

  A finned tube heat exchanger according to a fifth aspect of the present invention is the finned tube heat exchanger according to the fourth aspect of the present invention, wherein the plurality of first cut-and-raised parts are such that the airflow in the vicinity of the heat transfer tube is the flow direction of the airflow of the heat transfer tube. Line up straight on the 3rd straight line so as to be guided to the rear side.

  In the present invention, the plurality of first cut and raised portions are aligned straight on the third straight line. Therefore, the vertical vortex can be generated by the first cut-and-raised portion arranged on the upstream side in the flow direction of the airflow, and is formed further on the rear side of the first cut-and-raised portion arranged on the downstream side in the flow direction of the airflow. The dead water area can be reduced.

  A finned tube heat exchanger according to a sixth aspect of the present invention is the finned tube heat exchanger according to the fourth or fifth aspect of the present invention, wherein the plurality of second cut-and-raised portions are arranged such that the airflow in the vicinity of the heat transfer tube is a heat transfer tube. They are arranged straight on the fourth straight line so as to be guided to the rear side in the airflow direction.

  In the present invention, the plurality of second cut and raised portions are aligned straight on the fourth straight line. Accordingly, the vertical vortex can be generated by the second cut-and-raised portion arranged on the upstream side in the airflow direction, and is formed further on the rear side of the second cut-and-raised portion arranged on the downstream side in the airflow direction. The dead water area can be reduced.

  In the finned tube heat exchanger according to the first invention, it is possible to reduce the heat exchange between the refrigerants inside the heat transfer tubes, and to suppress a decrease in the heat exchange performance.

  In the finned tube heat exchanger according to the second aspect of the invention, the vertical vortex can be generated by the upstream portion of the first cut-and-raised portion in the airflow direction, and the downstream portion of the first cut-and-raised portion in the airflow direction. It is possible to reduce the dead water area formed on the further rear side of the.

  In the finned tube heat exchanger according to the third aspect of the present invention, the vertical vortex can be generated by the upstream portion of the second cut-and-raised portion in the airflow direction, and the downstream portion of the second cut-and-raised portion in the airflow direction. It is possible to reduce the dead water area formed on the further rear side of the.

  In the finned tube heat exchanger according to the fourth aspect of the present invention, it is possible to reduce the heat exchange between the refrigerants inside the heat transfer tubes, and it is possible to suppress the deterioration of the heat exchange performance.

  In the finned tube heat exchanger according to the fifth aspect of the present invention, the vertical vortex can be generated by the first cut and raised portion arranged on the upstream side in the flow direction of the airflow, and the first arranged on the downstream side in the flow direction of the airflow. The dead water area formed on the further rear side of the one cut-and-raised portion can be reduced.

  In the finned tube heat exchanger according to the sixth aspect of the present invention, the vertical vortex can be generated by the second cut and raised portion arranged on the upstream side in the airflow direction, and the second vortex arranged on the downstream side in the airflow direction. The dead water area formed on the further rear side of the two cut-and-raised portions can be reduced.

  Hereinafter, an embodiment of an air-conditioning apparatus according to the present invention will be described with reference to the drawings.

  FIG. 1 is a perspective view of an air conditioner according to an embodiment of the present invention. FIG. 2 is a side sectional view showing the internal structure near the center in the horizontal direction of FIG.

(1) Wall-mounted indoor unit FIG. 1 is a perspective view of an air conditioner 10 according to an embodiment of the present invention. In addition, in the following description, when showing the direction and position regarding the air conditioning apparatus 10, the state with which the air conditioning apparatus 10 was mounted | worn on the indoor wall surface shall be shown as a reference | standard. And the part with which the wall surface of the air conditioning apparatus 10 is mounted | worn is made into the back surface of the air conditioning apparatus 10 (namely, indoor unit casing 11), the surface which opposes a back surface and protrudes indoors is made into the front surface (or front surface), The lateral side of the back is the side (more specifically, the right side is the right side when viewed from the front, the left side is the left side when viewed from the front), and the upper side of the front and back is the top side. The lower surface of the front surface and the back surface is the bottom surface.

  The air conditioner 10 is a wall-mounted indoor unit that is attached to the upper part of an indoor wall surface, and has a function of performing indoor heating and cooling. The air conditioner 10 mainly includes a finned tube heat exchanger 1, a blower fan 4, and an indoor unit casing 11 that houses the finned tube heat exchanger 1 and the blower fan 4.

  The indoor unit casing 11 has a rectangular parallelepiped shape that is long in the horizontal direction when viewed from the front, and mainly accommodates the blower fan 4 and the finned tube heat exchanger 1 as shown in FIG. The indoor unit casing 11 is provided with an inlet 12 and an outlet 13. Here, FIG. 2 is a side sectional view showing the internal structure of the air conditioner 10 near the center in the horizontal direction. The air outlet 13 is an opening through which air blown out from the indoor unit casing 11 into the room passes, and is provided in a front portion of the bottom surface of the indoor unit casing 11. The suction port 12 is an opening through which air taken from the room into the indoor unit casing 11 passes, and is provided on the top surface of the indoor unit casing 11.

  The blower fan 4 is a cross-flow fan that is configured in a cylindrical shape that is elongated in the horizontal direction and has a central axis that is parallel to the horizontal direction. A plurality of blades are provided on the peripheral surface of the blower fan 4. The blower fan 4 is rotationally driven around a central axis by a fan motor (not shown), takes indoor air into the indoor unit casing 11 through the inlet 12, passes the fin tube heat exchanger 1, and then passes through the indoor unit casing. A flow of air blown out from the inside of the room 11 is generated from the air outlet 13. The blower fan 4 is disposed substantially at the center of the indoor unit casing 11 in a side view.

  In this embodiment, the finned tube heat exchanger 1 is a cross finned tube type heat exchanger formed by arranging a plurality of heat transfer tubes 3 in an inverted V shape, and is arranged so as to surround the blower fan 4 from above. Is done. Here, the several heat exchanger tube 3 forms the 1st heat exchanger tube group G1 in the front side in the indoor unit casing 11, and forms the 2nd heat exchanger tube group G2 in the back side. The first heat transfer tube group G1 and the second heat transfer tube group G2 are each formed by two rows of heat transfer tube rows. And the finned tube type heat exchanger 1 is connected to the outdoor unit installed outdoors etc. via refrigerant | coolant piping. The finned tube heat exchanger 1 can function as a refrigerant evaporator flowing inside during cooling operation, and as a refrigerant condenser flowing inside during heating operation. Thereby, the fin tube type heat exchanger 1 performs heat exchange with the air sucked into the indoor unit casing 11 through the suction port 12 by the blower fan 4, and cools the air during the cooling operation, and cools the air during the heating operation. Can be heated.

  Further, the fin tube heat exchanger 1 includes two refrigerant inlet pipes 31a and 31b (two in this embodiment) on the blower fan 4 side near the center in the row direction (second direction D2) in which the first heat transfer pipe groups G1 are arranged. Of the first heat transfer tube group G1 and the two refrigerant outlet tubes 32a and 32b on the upper front side in the second direction D2 of the first heat transfer tube group G1 (in the present embodiment, the two heat transfer tubes 3). ) Is flowing out the refrigerant after heat exchange. Here, in the finned tube heat exchanger 1 in the present embodiment, the refrigerant flows through two refrigerant paths, so-called paths 91 and 92. In the path 91, the refrigerant flows in from the refrigerant inlet pipe 31a, flows through the heat transfer pipe 3 and the second heat transfer pipe group G2 above the first heat transfer pipe group G1, and flows out from the refrigerant outlet pipe 32a. In the path 92, the refrigerant flows in from the refrigerant inlet pipe 31b, flows through the heat transfer pipe 3 below the first heat transfer pipe group G1, and flows out from the refrigerant outlet pipe 32b. In FIG. 2, the solid line drawn so as to connect adjacent heat transfer tubes 3 is connected to the front side in FIG. 2 (that is, the right end side in the front view of the finned tube heat exchanger 1). The broken lines drawn so as to connect the adjacent heat transfer tubes 3 are connected to the rear side in FIG. 2 (that is, the left end side in the front view of the finned tube heat exchanger 1). Is shown. Here, when the heat transfer tube 3 of the finned tube heat exchanger 1 functions as a condenser, the superheated gas refrigerant in which the refrigerant inlet tubes 31a and 31b and the vicinity thereof are overheated flows. The supercooled liquid refrigerant in the supercooled state flows in the outlet pipes 32a and 32b and the vicinity thereof, and a gas-liquid two-phase state is established between the refrigerant inlet pipes 31a and 31b and the vicinity thereof and the refrigerant outlet pipes 32a and 32b. Flowing two-phase refrigerant. That is, according to the state of the refrigerant flowing through the heat transfer tube 3 of the finned tube heat exchanger 1, the heat transfer tube 3 is in a gas-liquid two-phase state with the superheated gas refrigerant passage portion 3a through which the superheated gas refrigerant flows. The refrigerant can be classified into a two-phase refrigerant passage portion 3b through which the phase refrigerant flows and a supercooled liquid refrigerant passage portion 3c through which the supercooled refrigerant in a supercooled state flows (see the hatched portion in FIG. 2). The heat transfer fin 2 includes a first heat transfer fin portion 2a between the superheated gas refrigerant passage portion 3a and the two-phase refrigerant passage portion 3b, a supercooled liquid refrigerant passage portion 3c, and a two-phase refrigerant passage portion 3b. It can classify | categorize into the 2nd heat-transfer fin part 2b in between, and the 3rd heat-transfer fin part 2c other than the 1st heat-transfer fin part 2a and the 2nd heat-transfer fin part.

(2) Basic configuration of finned tube heat exchanger FIGS. 3 to 5 show the main part of the finned tube heat exchanger 1. Here, FIG. 3 is a cross-sectional view of the finned tube heat exchanger 1 in the region Z1 of FIG. The “region Z1” here is a region in the vicinity of the superheated gas refrigerant passage portion 3a and the two-phase refrigerant passage portion 3b in the heat transfer tube 3 (see FIG. 2), and the region Z1 shown in FIG. The upper one of the two regions Z1. FIG. 4 is a sectional view of the fin tube type heat exchanger 1 taken along the line IV-IV. 5 is a cross-sectional view taken along the line VV in FIG.

  The fin tube type heat exchanger 1 is a cross fin and tube type heat exchanger, and mainly includes a plurality of plate-shaped heat transfer fins 2 and a plurality of heat transfer tubes 3. The heat transfer fins 2 are arranged side by side in the plate thickness direction in a state in which the plane direction is generally along the flow direction of the airflow such as air. A plurality of through holes 27 are formed in the heat transfer fin 2 at intervals in a direction substantially orthogonal to the airflow direction. A peripheral portion of the through hole 27 is an annular collar portion 23 that protrudes to one side in the plate thickness direction of the heat transfer fin 2. The collar portion 23 is in contact with a surface opposite to the surface on which the collar portion 23 of the heat transfer fins 2 adjacent in the plate thickness direction is formed, and a predetermined interval H is provided between the plate thickness directions of the heat transfer fins 2. Secured. The heat transfer tube 3 is a tube member through which a heat medium such as a refrigerant flows. The heat transfer tube 3 is inserted into the plurality of heat transfer fins 2 arranged side by side in the plate thickness direction, and in a direction substantially orthogonal to the airflow direction. Has been placed. Specifically, the heat transfer tube 3 passes through the through holes 27 formed in the heat transfer fins 2, and is in close contact with the inner surface of the collar portion 23 by tube expansion work when the fin tube heat exchanger 1 is assembled. ing.

  Moreover, the finned-tube heat exchanger 1 of this embodiment is used in the state installed so that the sequence direction of the several heat exchanger tube 3 may become a substantially up-down direction. For this reason, the airflow flows across the finned tube heat exchanger 1 in a direction crossing the vertical direction. In the following description, when the terms “upper”, “upper”, “lower”, and “lower” are used, the arrangement direction of the heat transfer tubes 3 is indicated.

(3) Detailed shape of heat transfer fin Next, the detailed shape of the heat transfer fin 2 used in the finned tube heat exchanger 1 of the present embodiment will be described. In addition, the detailed shape of the heat transfer fin 2 demonstrated here is a detailed shape of the heat transfer fin 2 in the area | region Z1 shown in FIG.

  The heat transfer fins 2 in the region Z1 are connected to the first heat transfer fin portions 2a and the third heat transfer fin portions 2c on both sides in the vertical direction of the heat transfer tubes 3 (that is, the lower side and the upper side of the heat transfer tubes 3). A plurality of cut-and-raised portions 21a to 21f and 25a to 25f (three in the lower side and three in the upper side) arranged in a straight line from the upstream side to the downstream side in the airflow direction are cut and raised. Thus, the heat transfer fin surface 28 is formed (see FIG. 3). Here, the lower cut-and-raised portion is referred to as first cut-and-raised portions 21a to 21c and 25a to 25c, and the upper cut-and-raised portion is referred to as second cut and raised portions 21d to 21f and 25d to 25f. In addition, the direction in which the heat transfer tubes 3 are arranged in the region Z1 is the second direction inclined by the first angle θ1 clockwise from the vertical direction (first direction D1), and the airflow is in the vertical direction (first direction D1). ) In the counterclockwise direction (the third direction) inclined by the second angle θ2. The first straight line L1 that virtually connects the first cut-and-raised portions 21a to 21c and 25a to 25c is located on the rear side of the air flow in the vicinity of the heat transfer tube 3 in the air flow direction (third direction D3) in the heat transfer tube 3. It is inclined with respect to the third straight line L3 parallel to the third direction D3 so as to be guided. The second straight line L2 that virtually connects the second cut and raised portions 21d to 21f and 25d to 25f guides the airflow in the vicinity of the heat transfer tube 3 to the rear side in the flow direction of the airflow in the heat transfer tube 3 (third direction D3). In this way, it is inclined with respect to the fourth straight line L4 parallel to the third direction D3. Here, the angle of attack α1 of the first straight line L1 with respect to the third straight line L3 and the angle of attack α2 of the second straight line L2 with respect to the fourth straight line L4 are set to be within a range of 10 ° to 30 °. .

  Thus, the 1st cut-and-raised part 21a-21c, 25a-25c and the 2nd cut-and-raised part 21d-21f, 25d-25f are near the heat exchanger tube 3 in the 1st heat-transfer fin part 2a and the 3rd heat-transfer fin part 2c. Is inclined with respect to the third direction D3 so as to be guided to the rear side in the flow direction (third direction D3) of the air flow in the heat transfer tube 3. Therefore, mainly by the first cut and raised portions 21a and 25a and the second cut and raised portions 21d and 25d arranged on the front side in the air flow direction D4 of the heat transfer fin 2 among the cut and raised portions 21a to 21f and 25a to 25f. The effect of updating the boundary layer can be obtained with certainty. Moreover, in the 1st heat-transfer fin part 2a and the 3rd heat-transfer fin part 2c, the 1st cut-and-raised part 21c, 25c arrange | positioned in the flow direction (3rd direction D3) back of the airflow of the heat-transfer fin 2 and The dead water area formed in the rear part of the flow direction (third direction D3) of the air flow in the heat transfer tube 3 is reduced by the flow direction (third direction D3) of the heat transfer tube 3 by the second cut and raised portions 21f and 25f. Effect can be obtained.

  Moreover, each cut-and-raised part 21a-21f and 25a-25f are formed so that height may increase gradually toward the flow direction downstream. In the present embodiment, each cut-and-raised portion 21a to 21f, 25a to 25f has a substantially trapezoidal shape or a substantially triangular shape (see FIG. 5, FIG. 5 shows the second cut-and-raised portions 21d to 21f. The first cut-and-raised portions 21a to 21c have the same shape, and the cut-and-raised portions 25a to 25f in the third heat transfer fin portion 2c are different only in their bending lengths. The height is gradually increased in the same manner as the cut and raised portions 21a to 21f in the fin portion 2a), and the maximum height h is lower than the height H of the collar portion 23 (FIGS. 4 and 4). 5).

  Thus, each of the cut-and-raised portions 21a to 21f and 25a to 25f formed on both sides in the vertical direction of each heat transfer tube 3 has a plurality (in the present embodiment, the first heat transfer) from the upstream side to the downstream side in the airflow direction. The first cut-and-raised portions 21a to 21c, 25a to 25c, and the second cut-and-raised portions of the fin portion 2a, the second heat transfer fin portion 2b, and the third heat transfer fin portion 2c (three each in the vertical direction) It is divided into 21d-21f and 25d-25f. For this reason, when water droplets, such as condensed water, generate | occur | produce in the heat-transfer fin 2, a water drop is the clearance gap between 1st cut-and-raised part 21a-21c, 25a-25c, and the clearance gap between 2nd cut-raised part 21d-21f, 25d-25f. Can be easily discharged from. Thereby, the heat transfer promotion effect by the cut-and-raised portions 21a to 21f and 25a to 25f can be obtained without being affected by water droplets generated in the heat transfer fins 2.

  Moreover, when the cut-and-raised portions 21a to 21f and 25a to 25f are cut and raised, the slit holes 22a to 22f and 26a to 26f formed in the heat transfer fin 2 are located above the cut and raised portions 21a to 21f and 25a to 25f. Placed in. Further, the heat transfer fin 2 is provided with a concave portion 24 concentric with the collar portion 23 around the collar portion 23. As shown in FIG. 3, the recess 24 is formed by recessing the heat transfer fin 2 in a direction opposite to the collar portion 23 at a position where the cross section circumscribes the collar portion 23.

  As described above, the cut-and-raised portions 21a to 21f and 25a to 25f are formed by cutting and raising the heat transfer fins 2 from the upper part to the lower part. For this reason, in the 1st heat-transfer fin part 2a, the 1st slit hole 22a-22c will be formed between the heat-transfer tube 3 and the 1st cut-and-raised part 21a-21c which a water drop tends to stay especially, and is transmitted. Water droplets are less likely to stay between the heat tube 3 and the first cut and raised portions 21a to 21c. Further, in the third heat transfer fin portion 2c, similarly to the first heat transfer fin portion 2a, the first slit holes 26a to 26a are particularly formed between the heat transfer tube 3 in which water droplets tend to stay and the first cut and raised portions 25a to 25c. 26c is formed, and it becomes difficult for water droplets to stay between the heat transfer tube 3 and the first cut and raised portions 25a to 25c. For this reason, water droplets are easily discharged from the heat transfer fins 2. Further, a recess 24 is formed in the entire periphery of the heat transfer tube 3 in the heat transfer fin 2. Accordingly, water droplets temporarily stay in the recess 24, and flow down and be discharged after a predetermined amount or more of water droplets remain. For this reason, a water droplet can be discharged | emitted, without making a water droplet retain so much between the 1st cut-and-raised part 21a-21c, 25a-25c, and the heat exchanger tube 3. FIG.

  The first cut and raised portions 21a to 21c and the second cut and raised portions 21d to 21f are formed on the first heat transfer fin portion 2a of the heat transfer fin 2, and the first cut and raised portions 25a to 25c and the second cut and raised portions are formed. The raising portions 25d to 25f are formed in the third heat transfer fin portion 2c (see FIG. 3). And the 1st bending length a1 (refer FIG. 6) of the bending part of each raising part 21a-21f formed in the 1st heat-transfer fin part 2a is each cut formed in the 3rd heat-transfer fin part 2c. It is longer than the second bending length a2 (see FIG. 7) of the bent portions of the raising portions 25a to 25f. That is, in each cut-and-raised portion 21a to 21f formed in the first heat transfer fin portion 2a, both ends of each cut-and-raised portion 21a to 21f from the center of the heat transfer tube 3 are connected to virtual lines L11a, L11b, L12a, L12b, L13a The total sum of the first angles β11 to β16 formed by connecting L13b, L14a, L14b, L15a, L15b, L16a, and L16b is a heat transfer tube in each cut-and-raised portion 25a to 25f formed in the third heat transfer fin portion 2c. The second angles γ11 to γ16 that can be formed by connecting both ends of the cut and raised portions 25a to 25f from the center of the line 3 with virtual lines L21a, L21b, L22a, L22b, L23a, L23b, L24a, L24b, L25a, L25b, L26a, and L26b. Cut and raised portions 21a to 21f, 2 so as to be larger than the sum of a~25f is formed. Here, FIG. 6 is an enlarged view of the first heat transfer fin portion 2a in the first heat transfer tube group G1, and FIG. 7 is an enlarged view of the third heat transfer fin portion 2c in the first heat transfer tube group G1. .

  By the way, since the 1st heat transfer fin part 2a is an area | region between the superheated gas refrigerant passage part 3a and the two-phase refrigerant passage part 3b in the heat transfer fin 2, the superheated gas refrigerant passage part 3a and the two-phase refrigerant passage A temperature difference is generated between the portion 3b and the heat transfer fin 2 is a region where heat exchange by heat conduction is easily performed. When heat exchange by this heat conduction is performed, heat exchange is not performed between the refrigerant and the air but heat exchange between the refrigerants, so that the heat exchange efficiency is lowered. Therefore, as described above, the cut-and-raised portions 21a to 21f formed in the first heat transfer fin portion 2a are cut and raised in the sum of the first angles β11 to β16 formed in the third heat-transfer fin portion 2c. By forming it to be larger than the sum of the second angles γ11 to γ16 in 25a to 25f, the thermal conductivity in the first heat transfer fin portion 2a by the superheated gas refrigerant passage portion 3a and the two-phase refrigerant passage portion 3b is increased. It can be made small, and a decrease in heat exchange efficiency can be prevented. Further, the cut-and-raised portion (not shown) formed in the second heat transfer fin portion 2b has the same shape as the cut-and-raised portions 21a to 21f formed in the first heat transfer fin portion 2a. It is formed so as to make the thermal conductivity between the heat transfer tubes 3 smaller than the cut and raised portions 25a to 25f formed in the heat fin portion 2c.

  Further, the first cut-and-raised portions 21a to 21c and 25a to 25c are arranged in a straight line on the first straight line L1 from the upstream side to the downstream side in the airflow direction (third direction D3). 21c and 25a to 25c, the first cut-and-raised portions 21c and 25c arranged on the downstream side in the airflow direction (third direction D3) of the heat transfer fin 2 are upstream in the airflow direction (third direction D3). Have the same inclination as the first cut-and-raised portions 21a and 25a. Further, the second cut-and-raised portions 21d to 21f and 25d to 25f are arranged straight on the second straight line L2 from the upstream side to the downstream side in the airflow direction (third direction D3). 21f and 25d to 25f, the second cut and raised portions 21f and 25f arranged on the downstream side in the airflow direction (third direction D3) of the heat transfer fin 2 are upstream in the airflow direction (third direction D3). Have the same inclination as the second cut and raised portions 21d and 25d. For this reason, not only the dead water area formed in the rear portion of the heat transfer tube 3 in the flow direction of the airflow is reduced, but a new rear portion is provided behind the first cut and raised portions 21c and 25c and the second cut and raised portions 21f and 25f. It is possible to prevent the formation of dead water areas.

  Here, only the portion of the region Z1 in FIG. 2 has been described with reference to FIG. 3, but the heat transfer fin in the region where the airflow flows in a direction different from the third direction D3 (for example, the region of the second heat transfer tube group G2). In the detailed shape of 2, the raised portion is inclined so that the airflow in the vicinity of the heat transfer tube 3 is guided to the rear side in the flow direction of the heat transfer tube 3 in that region. In such a region, the inclination at which the cut-and-raised portion is formed is only different from the detailed shape of the heat transfer fin in FIG. 3 (for example, in the fourth direction (not shown) in which the airflow direction is different from the third direction D3). The first cut-and-raised part tilts at the angle of attack α1 and the second cut-and-raised part tilts at the angle of attack α2 with respect to the fourth direction D4), and the shape of the cut-and-raised part itself is the third transmission in FIG. It has the same shape as the cut and raised portions 25a to 25f of the heat fin portion 2c. Moreover, the collar part 23 and the recessed part 24 which are formed in the heat-transfer fin 2 are the same shape in all the areas.

  As described above, in the finned tube heat exchanger 1 of the present embodiment, the heat transfer promotion effect by the cut-and-raised portions 21a to 21f and 25a to 25f is obtained without being significantly affected by the water droplets generated in the heat transfer fins 2. Since it can obtain, it can prevent that a new dead water area is formed behind the 1st cut and raised part 21c, the 2nd cut and raised part 21f, the 3rd cut and raised part 25c, and the 4th cut and raised part 25f. The heat transfer promotion effect by the cut and raised portions 21a to 21f and 25a to 25f and the drainage can be made compatible.

  Moreover, in this fin tube type heat exchanger 1, each cut-and-raised part is formed by making the shape of each cut-and-raised part 21a to 21f and 25a to 25f into a shape in which the height gradually increases toward the downstream side in the flow direction of the airflow. Since vertical vortices can be generated behind 21a to 21f and 25a to 25f, the effect of promoting heat transfer by the cut and raised portions 21a to 21f and 25a to 25f can be further enhanced.

<Features>
(1)
In the present invention, since the first heat transfer fin portion 2a is a region between the superheated gas refrigerant passage portion 3a and the two-phase refrigerant passage portion 3b in the heat transfer fin 2, the superheated gas refrigerant passage portion 3a and the two-phase There is a temperature difference between the refrigerant passage portion 3b and the heat transfer fin 2 is a region where heat exchange by heat conduction is easily performed. When heat exchange by this heat conduction is performed, heat exchange is not performed between the refrigerant and the air but heat exchange between the refrigerants, so that the heat exchange efficiency is lowered.

  Therefore, as described above, the cut-and-raised portions 21a to 21f formed in the first heat transfer fin portion 2a are cut and raised portions in which the sum of the first angles β11 to β16 is formed in the third heat-transfer fin portion 2c. By forming it to be larger than the sum of the second angles γ11 to γ16 in 25a to 25f, the thermal conductivity in the first heat transfer fin portion 2a by the superheated gas refrigerant passage portion 3a and the two-phase refrigerant passage portion 3b is increased. Therefore, the heat exchange efficiency can be improved.

(2)
In the present invention, the plurality of cut-and-raised portions 21a to 21f and 25a to 25f are arranged straight on the first straight line L1 and the second straight line L2. Therefore, the vertical vortex can be generated by the cut-and-raised parts 21a, 21d, 25a, and 25d arranged on the upstream side in the airflow direction, and the cut-and-raised parts 21c, 21f, 21f arranged on the downstream side in the airflow direction The dead water area formed on the further rear side of 25c and 25f can be reduced.

<Modification>
As mentioned above, although embodiment of this invention was described based on drawing, a specific structure is not restricted to these embodiment, It can change in the range which does not deviate from the summary of invention.

(1)
In the present embodiment, the finned tube heat exchanger 1 is employed in a wall-mounted indoor unit, but is not limited thereto, and may be employed in an outdoor unit, or an indoor unit other than the wall-mounted type (for example, Further, it may be a ceiling-embedded indoor unit, a ceiling-suspended indoor unit, a built-in indoor unit, or the like.

(2)
In the present embodiment, the first bending length a1 of the cut-and-raised portions 21a to 21f in the first heat transfer fin portion 2a is greater than the second bending length a2 of the raised portions 25a to 25f in the third heat-transfer fin portion 2c. Although the cut and raised portions 21a to 21f and 25a to 25f are formed so that the sum of the first angles β11 to β16 becomes larger than the sum of the second angles γ11 to γ16 by increasing the length, it is not limited thereto. First, the first distance from the cut-and-raised portion in the first heat transfer fin portion to the heat transfer tube is shorter than the second distance from the cut-and-raised portion in the third heat transfer fin portion to the heat transfer tube. The sum of one angle may be larger than the sum of the second angle.

  FIG. 8 shows an enlarged view of the cut-and-raised portions 51a to 51f in the first heat transfer fin portion 5a formed as described above where the first distance b1 is shorter than the second distance b2. In this case, the fin tube type heat exchanger 1a is different from the fin tube type heat exchanger 1 of the present embodiment only in the first heat transfer fin portion 5a as shown in FIG. In the same manner as the fin-tube heat exchanger 1 of the embodiment, the 2nd unit is replaced with the 5th unit and the 20th unit is replaced with the 50th unit. The first distance b1 from the cut and raised portions 51a to 51f in the first heat transfer fin portion 5a to the heat transfer tube 3 is greater than the second distance b2 from the cut and raised portions 55a to 55f to the heat transfer tube 3 in the third heat transfer fin portion 5c. The cut and raised portions 51a to 51f and 55a to 55f are formed so as to be shorter. That is, in each cut-and-raised portion 51a to 51f formed in the first heat transfer fin portion 5a, both ends of each cut-and-raised portion 51a to 51f from the center of the heat transfer tube 3 are connected to virtual lines L31a, L31b, L32a, L32b, L33a The total sum of the first angles β21 to β26 formed by tying with L33b, L34a, L34b, L35a, L35b, L36a, and L36b is the heat transfer tube in each cut-and-raised portion 55a to 55f formed in the third heat transfer fin portion 5c. The second angles γ11 to γ16 that can be formed by connecting both ends of the cut and raised portions 55a to 55f from the center of the line 3 with virtual lines L21a, L21b, L22a, L22b, L23a, L23b, L24a, L24b, L25a, L25b, L26a, and L26b. Each of the raised portions 51a to 51f, so as to be larger than the sum of 5a~55f will be formed. Here, the bending length a3 of the bent portions of the cut and raised portions 51a to 51f is equal to the bent length a2 of the bent portions of the cut and raised portions 55a to 55f in the third heat transfer fin portion 5c. In addition, although the modification of only the 1st heat-transfer fin part 5a is shown here, the same can be said also about the 2nd heat-transfer fin part 5b.

(3)
In the present embodiment, the cut-and-raised portions 21a to 21f and 25a to 25f are formed in plural on both sides in the row direction of the heat transfer tubes 3 (the second direction D2 in the present embodiment). One may be formed on both sides in the three column directions (second direction D2).

  9 and 10 are enlarged views of cut-and-raised portions 61a, 61b, 65a, and 65b formed one on each side in the row direction (second direction D2) of the heat transfer tubes 3 as described above. In this case, the fin tube type heat exchanger 1b is different from the fin tube type heat exchanger 1 of the present embodiment only in the shape of the cut and raised portions 61a, 61b, 65a, 65b, and the other shapes are the same as those of the present embodiment. In the same manner as the fin tube type heat exchanger 1, the 2nd series is replaced with the 6th series, and the 20th series is replaced with the 60th series. 9 is an enlarged view of the first heat transfer fin portion 6a of the heat transfer fin 6 of the fin tube type heat exchanger 1b, and FIG. 10 is an enlarged view of the third heat transfer fin portion 6c.

  Here, the bending length c1 (see FIG. 9) of the bent portions of the cut and raised portions 61a and 61b formed in the first heat transfer fin portion 6a is the cut and raised portion 65a formed in the third heat transfer fin portion 6c. , 65b are formed so as to be longer than the bending length c2 (see FIG. 10) of the bent portions of the bent portions 61a, 61b, 65a, 65b. That is, in the first cut-and-raised portion 61a formed in the first heat transfer fin portion 6a, the first angle β31 that can be formed by connecting both ends of the first cut-and-raised portion 61a from the center of the heat transfer tube 3 with virtual lines L41a and L41b. However, in the first cut-and-raised portion 65a formed in the third heat transfer fin portion 6c, the second angle γ31 formed by connecting both ends of the first cut-and-raised portion 65a from the center of the heat transfer tube 3 with virtual lines L51a and L51b. The first cut-and-raised portions 61a and 65a are formed so as to be larger. Similarly, in the second cut-and-raised portion 61b formed in the first heat transfer fin portion 6a, the second cut-and-raised portion 61b is connected to both ends of the second cut-and-raised portion 61b from the center of the heat transfer tube 3 by virtual lines L42a and L42b. In the second cut-and-raised portion 65b formed in the third heat transfer fin portion 6c, the first angle β32 is formed by connecting both ends of the second cut-and-raised portion 65b from the center of the heat transfer tube 3 with virtual lines L52a and L52b. The first cut and raised portions 61b and 65b are formed so as to be larger than the two angles γ32. Accordingly, since the heat conduction distance from the superheated gas refrigerant passage portion 3a to the two-phase refrigerant passage portion 3b is increased, the heat through the heat transfer fins 6 between the superheated gas refrigerant passage portion 3a and the two-phase refrigerant passage portion 3b. Heat exchange by conduction is less likely to occur. Therefore, it can prevent that heat exchange efficiency falls by heat conduction. In addition, although the modification of only the 1st heat-transfer fin part 6a is shown here, the same can be said also about the 2nd heat-transfer fin part 6b.

(4)
In the modified example (3), the bending length c1 of the bent portions of the cut and raised portions 61a and 61b in the first heat transfer fin portion 6a is the bent length of the bent portions of the cut and raised portions 65a and 65b in the third heat transfer fin portion 6c. Although not limited to this, the first distance from the cut-and-raised portion in the first heat transfer fin portion to the heat transfer tube is the first distance from the cut-and-raised portion in the third heat transfer fin portion to the heat transfer tube. By making the distance shorter than two distances, the sum of the first angles may be larger than the sum of the second angles.

  FIG. 11 shows an enlarged view of the cut-and-raised portions 71a and 71b in the first heat transfer fin portion 7a. The fin tube type heat exchanger 1c in this case is different from the fin tube type heat exchanger 1b of the modification (3) only in the first heat transfer fin portion 7a as shown in FIG. Similar to the fin tube type heat exchanger 1b, the 6th series is replaced with the 7th series and the 60th series is replaced with the 70th series. The first distance d1 from the cut and raised portions 71a and 71b to the heat transfer tube 3 in the first heat transfer fin portion 7a is greater than the second distance d2 from the cut and raised portions 75a and 75b to the heat transfer tube 3 in the third heat transfer fin portion 7c. Each cut-and-raised portion 71a, 71b, 75a, 75b is formed so as to be shorter. That is, in the first cut-and-raised portion 71a formed in the first heat transfer fin portion 7a, the first angle β41 that can be obtained by connecting both ends of the first cut-and-raised portion 71a from the center of the heat transfer tube 3 with virtual lines L61a and L61b. However, in the first cut-and-raised portion 75a formed in the third heat transfer fin portion 7c, the second angle γ31 formed by connecting both ends of the first cut-and-raised portion 75a from the center of the heat transfer tube 3 with virtual lines L51a and L51b. The first cut-and-raised portions 71a and 75a are formed so as to be larger. Similarly, in the second cut-and-raised portion 71b formed in the first heat transfer fin portion 7a, the second cut-and-raised portion 71b is connected to the both ends of the second cut-and-raised portion 71b from the center of the heat transfer tube 3 by virtual lines L62a and L62b. In the second cut-and-raised portion 75b formed in the third heat transfer fin portion 7c, the first angle β42 is formed by connecting both ends of the second cut-and-raised portion 75b from the center of the heat transfer tube 3 with virtual lines L52a and L52b. The first cut-and-raised portions 71b and 75b are formed so as to be larger than the two angles γ32. Here, the bending length c3 of the bent portions of the cut and raised portions 71a and 71b is equal to the bent length c2 of the bent portions of the cut and raised portions 75a and 75b in the third heat transfer fin portion 7c. In addition, although the modification of only the 1st heat-transfer fin part 7a is shown here, the same can be said also about the 2nd heat-transfer fin part 7b.

  The finned tube heat exchanger according to the present invention can improve the heat exchanging performance, and is inserted into the finned tube heat exchanger, in particular, the heat transfer fins arranged in the airflow and the heat transfer fins. The present invention is useful as a finned tube heat exchanger having a plurality of heat transfer tubes arranged in a direction substantially orthogonal to the flow direction of the airflow, and an air conditioner having the finned tube heat exchanger.

1 is an external perspective view of an air conditioner according to an embodiment of the present invention. Side surface sectional drawing which shows the internal structure of the horizontal direction center vicinity of FIG. Sectional drawing of the area | region containing the 1st heat-transfer fin part of a finned-tube type heat exchanger. IV-IV sectional drawing of FIG. VV sectional drawing of FIG. The enlarged view of a 1st heat-transfer fin part. The enlarged view of a 3rd heat-transfer fin part. The enlarged view of the 1st heat-transfer fin part of the fin tube type heat exchanger of a modification (2). The enlarged view of the 1st heat-transfer fin part of the fin tube type heat exchanger of a modification (3). The enlarged view of the 3rd heat-transfer fin part of the fin tube type heat exchanger of a modification (3). The enlarged view of the 1st heat-transfer fin part of the fin tube type heat exchanger of a modification (4).

Explanation of symbols

1, 1a-1c Fin tube type heat exchangers 2, 5-7 Heat transfer fins 2a, 5a-7a First heat transfer fin portions 2b, 5b-7b Second heat transfer fin portions 2c, 5c-7c Third heat transfer Fin portion 3 Heat transfer tube 3a Superheated gas refrigerant passage portion (first heat transfer tube portion)
3b Two-phase refrigerant passage part (second heat transfer tube part)
3c Supercooled liquid refrigerant passage part (first heat transfer tube part)
21a-21c 1st raising part (1st raising part)
21d-21f 2nd raising part (1st raising part)
25a-25c 1st raising part (2nd raising part)
25d-25f 2nd raising part (2nd raising part)
51a-51c 1st raising part (1st raising part)
51d-51f 2nd raising part (1st raising part)
55a-55c 1st raising part (2nd raising part)
55d-55f 2nd raising part (2nd raising part)
61a-61c 1st raising part (1st raising part)
61d-61f 2nd raising part (1st raising part)
65a-65c 1st raising part (2nd raising part)
65d-65f 2nd raising part (2nd raising part)
71a-71c 1st raising part (1st raising part)
71d-71f 2nd raising part (1st raising part)
75a-75c 1st raising part (2nd raising part)
75d-75f 2nd raising part (2nd raising part)
D2 Second direction (row direction of heat transfer tube row)
D3 3rd direction (flow direction of airflow)
L11a to L16a, L11b to L16b Virtual line (first straight line)
L21a to L26a, L21b to L26b Virtual line (second straight line)
L31a to L36a, L31b to L36b Virtual line (first straight line)
L41a, L42a, L41b, L42b Virtual line (first straight line)
L51a, L52a, L51b, L52b Virtual line (second straight line)
L61a, L62a, L61b, L62b Virtual line (first straight line)
L1 1st straight line (3rd straight line)
L2 2nd straight line (4th straight line)
β11 to β16 first angle (first projection angle)
β21 to β26 First angle (first projection angle)
β31, β32 first angle (first projection angle)
β41, β42 First angle (first projection angle)
γ11 to γ16 second angle (second projection angle)
γ31, γ32 second angle (second projection angle)

Claims (6)

Heat transfer fins (6, 7) arranged in the airflow;
A plurality of heat transfer tubes (3) that are inserted into the heat transfer fins and arranged to form a heat transfer tube array in a direction intersecting the flow direction of the airflow;
With
The plurality of heat transfer tubes have a first heat transfer tube portion (3a, 3c) through which superheated gas refrigerant or supercooled liquid refrigerant flows, and a second heat transfer tube portion (3b) through which gas-liquid two-phase refrigerant flows,
The heat transfer fins are arranged along the flow direction of the airflow in the first heat transfer fin portions (6a, 6b, 7a, 7b) in the vicinity between the first heat transfer tube portion and the second heat transfer tube portion. The first cut-and-raised portion (61a, 61b, 71a, 71b) and the second heat transfer fin portion (6c, 7c) different from the first heat transfer fin portion are arranged along the flow direction of the air flow. The second cut and raised portions (65a, 65b, 75a, 75b) are formed by the cut and raised processing,
The first cut-and-raised part and the second cut-and-raised part are arranged so that the air flow in the vicinity of the heat transfer tube is guided to the rear side in the flow direction (D3) of the air flow of the heat transfer tube. Are inclined with respect to the air flow direction on both sides of the row direction (D2) of
First projection angles (β31, β32, β41, β42) are obtained from a second projection angle (γ31, γ32) formed by a second straight line (L51a, L51b, L52a, L52b) that virtually connects both ends of the second cut-and-raised portion from the center of the heat transfer tube. Is also big,
Fin tube heat exchanger (1b, 1c). The first cut-and-raised part is arranged straight on a third straight line so that the airflow in the vicinity of the heat transfer tube is guided to the rear side in the flow direction of the airflow of the heat transfer tube,
The finned tube heat exchanger (1b, 1c) according to claim 1. The second cut-and-raised part is arranged straight on the fourth straight line so that the airflow in the vicinity of the heat transfer tube is guided to the rear side in the flow direction of the airflow of the heat transfer tube,
The finned-tube heat exchanger (1b, 1c) according to claim 1 or 2. Heat transfer fins (2, 5) arranged in the airflow;
A plurality of heat transfer tubes (3) that are inserted into the heat transfer fins and arranged to form a heat transfer tube array in a direction intersecting the flow direction of the airflow;
With
The plurality of heat transfer tubes have a first heat transfer tube portion (3a, 3c) through which superheated gas refrigerant or supercooled liquid refrigerant flows, and a second heat transfer tube portion (3b) through which gas-liquid two-phase refrigerant flows,
The heat transfer fins are arranged along the airflow direction in the first heat transfer fin portions (2a, 2b, 5a, 5b) in the vicinity between the first heat transfer tube portion and the second heat transfer tube portion. A plurality of first cut-and-raised portions (21a to 21f, 51a to 51f) and second heat transfer fin portions (2c, 5c) different from the first heat transfer fin portions along the airflow direction. A plurality of second cut and raised portions (25a to 25f, 55a to 55f) to be arranged are formed by the cut and raised processing,
The plurality of first cut-and-raised portions and the plurality of second cut-and-raised portions of the heat transfer tubes are arranged so that the airflow in the vicinity of the heat transfer tubes is guided to the rear side in the flow direction (D3) of the airflow of the heat transfer tubes. Inclined with respect to the flow direction of the airflow on both sides in the row direction (D2) of the heat transfer tube row,
First straight lines (L11a, L11b, L12a, L12b, L13a, L13b, L14a, L14b, L15a, L15b, L16a, L16b, L31a, which virtually connect both ends of the first cut and raised portions from the center of the heat transfer tube. The sum of the first projection angles (β11 to β16, β21 to β26) formed by L31b, L32a, L32b, L33a, L33b, L34a, L34b, L35a, L35b, L36a, L36b is determined from the center of the heat transfer tube. Second projection angle (γ11 to γ16) formed by a second straight line (L21a, L21b, L22a, L22b, L23a, L23b, L24a, L24b, L25a, L25b, L26a, L26b) virtually connecting both ends of the two cut and raised portions Greater than the sum of
Fin tube heat exchanger (1, 1a). The plurality of first cut and raised portions are arranged straight on the third straight line (L1) so that the airflow in the vicinity of the heat transfer tube is guided to the rear side in the flow direction of the airflow of the heat transfer tube,
The finned-tube heat exchanger (1, 1a) according to claim 2. The plurality of second cut-and-raised parts are arranged straight on the fourth straight line (L2) so that the airflow in the vicinity of the heat transfer tube is guided to the rear side in the flow direction of the airflow of the heat transfer tube,
The finned-tube heat exchanger (1, 1a) according to claim 3.

Images