WO2013161240A1

WO2013161240A1 - Finned tube heat exchanger

Info

Publication number: WO2013161240A1
Application number: PCT/JP2013/002660
Authority: WO
Inventors: 明広重田; 横山　昭一; 由樹山岡
Original assignee: パナソニック株式会社
Priority date: 2012-04-23
Filing date: 2013-04-19
Publication date: 2013-10-31
Also published as: CN104246409B; JP5974276B2; CN104246409A; JP2013224800A

Abstract

The finned tube heat exchanger of the present invention is provided with a plurality of fins (1) and a plurality of heat transfer tubes (2) that pass through the plurality of fins (1) and have a fluid flowing therethrough. The fins (1) comprise a tube periphery section (4) that is formed on the periphery of the heat transfer tubes (2) and a convex section (5) that is formed so as to surround the tube periphery section (4). The convex section (5) is configured so as to comprise fluid paths (9, 9a, 9b, 10) that connect the front and the back of the fins (1).

Description

Finned tube heat exchanger

The present invention relates to a finned tube heat exchanger used for heat exchange of a refrigerant.

Conventionally, as this kind of finned tube heat exchanger, for example, one described in Patent Document 1 (Japanese Patent Laid-Open No. 9-203593) is known. FIG. 14A is a partial plan view of a fin included in a conventional fin tube heat exchanger. 14B is a cross-sectional view taken along line AA in FIG. 14A. 14C is a cross-sectional view taken along line BB of FIG. 14A. FIG. 14D is a partially enlarged view of a region C surrounded by a broken line in FIG. 14A and shows how air flows.

A conventional fin tube heat exchanger includes a plurality of fins 101 shown in FIG. 14A. The plurality of fins 101 are arranged in parallel at regular intervals so that air flows between them. Each fin 101 is provided with a plurality of heat transfer tubes 102 penetrating in the thickness direction of the fin 101. Inside each heat transfer tube 102, a refrigerant for performing heat exchange with air flowing between the plurality of fins 101 flows.

Also, the fin 101 is formed with a plurality of cylindrical fin collars 103 into which the heat transfer tubes 102 are inserted. A flat tube peripheral portion 104 is formed around the fin collar 103. A substantially annular convex portion 105 is formed around the tube peripheral portion 104. The convex portion 105 has a first inclined surface 105a and a second inclined surface 105b, and functions as a guide for the air flow S. As shown in FIG. 14D, the convex portion 105 reduces the dead water area D by attracting the air flows Sa and Sb that wrap around the downstream portion of the heat transfer tube 102. The first inclined surface 105a is inclined from the ridge line of the convex portion 105 toward the heat transfer tube 2 side. The second inclined surface 105 b is inclined from the ridge line of the convex portion 5 toward the side opposite to the heat transfer tube 2. Further, as shown in FIG. 14A, a flat portion 106 is provided in a part below the convex portion 105 with respect to the gravity direction G.

For example, when a conventional fin tube heat exchanger is used as an evaporator, condensed water 120 in which moisture in the air is condensed is generated around the heat transfer tube 102 on the surface side of the fin 101 as shown in FIG. 15A. To do. Since the flat part 106 is formed in a part below the convex part 105, the condensed water 120 is drained through the flat part 106 as shown in FIG. 15B. In the conventional fin tube heat exchanger, the drainage property of the water generated on the surface of the fin 101 is improved by such a configuration.

JP-A-9-203593

However, in the conventional configuration, as indicated by a broken line arrow in FIG. 14D, an air flow Sc leaking from the flat portion 106 is generated, and it is difficult to increase the air volume at the downstream portion of the heat transfer tube 102. For this reason, there exists a subject that the heat-transfer performance of the downstream part of the heat exchanger tube 102 falls.

Further, in the conventional configuration, there is a problem that the heat transfer area is reduced and the heat transfer performance is lowered by providing the flat portion 106.

The present invention solves the above-described conventional problems, and can improve the heat transfer performance of the downstream portion of the heat transfer tube without reducing the drainage of water generated on the surface of the fin. The purpose is to provide an exchanger.

In order to solve the conventional problem, a finned tube heat exchanger according to the present invention includes a plurality of fins and a plurality of heat transfer tubes that pass through the plurality of fins and in which a fluid flows. A pipe peripheral part formed around the heat transfer pipe and a convex part formed so as to surround the pipe peripheral part, and a fluid path communicating the front and back of the fin is provided in the convex part. It is configured.

According to the finned tube heat exchanger of the present invention, there is provided a finned tube heat exchanger that can improve the heat transfer performance of the downstream portion of the heat transfer tube without reducing the drainage of water generated on the surface of the fin. Can be provided.

These and other objects and features of the invention will become apparent from the following description taken in conjunction with the preferred embodiments with reference to the accompanying drawings. In this drawing,
FIG. 1 is a perspective view showing the configuration of the finned tube heat exchanger according to the first embodiment of the present invention. It is a partial top view of the fin with which the fin tube heat exchanger of FIG. 1 is provided, FIG. 2B is a cross-sectional view taken along line A1-A1 of FIG. 2A. FIG. 2B is a sectional view taken along line B1-B1 of FIG. 2A; FIG. 2B is an enlarged view of a region C1 surrounded by a broken line in FIG. 2A and shows how air flows; It is the elements on larger scale which show the state where condensed water occurred on the surface of the fin of Drawing 2A, It is the elements on larger scale which show a mode that the condensed water which occurred on the surface of the fin of Drawing 2A is drained on the back of a fin via notch, It is the elements on larger scale which show the state where most condensate generated on the surface of the fin of Drawing 2A was drained, It is the fragmentary top view which shows the modification which made the fin of FIG. 2A wave shape, FIG. 4B is a cross-sectional view taken along line A2-A2 when a plurality of the fins of FIG. 4A are stacked. FIG. 4B is a sectional view taken along line B2-B2 when a plurality of the fins of FIG. 4A are stacked; It is the elements on larger scale which show the state where condensed water occurred on the surface of the fin of Drawing 4A, It is the elements on larger scale which show a mode that the condensed water which occurred on the surface of the fin of Drawing 4A is drained on the back of a fin via notch, It is the elements on larger scale which show the state where most condensate generated on the surface of the fin of Drawing 4A was drained, It is a partial top view of the fin with which the finned-tube heat exchanger concerning 2nd Embodiment of this invention is provided, It is a partial top view which shows the modification which made the fin of FIG. 6 the waveform shape, It is a fragmentary top view of the fin with which the finned-tube heat exchanger concerning 3rd Embodiment of this invention is provided, It is the A3-A3 sectional view taken on the line of FIG. 8A, FIG. 8B is a sectional view taken along line B3-B3 of FIG. 8A; FIG. 8B is an enlarged view of a region C2 surrounded by a broken line in FIG. 8A and shows how air flows; It is the elements on larger scale which show the state where condensed water generate | occur | produced on the surface of the fin of FIG. 8A, It is the elements on larger scale which show a mode that the condensed water which generate | occur | produced on the surface of the fin of FIG. 8A is drained by the back surface of a fin through a notch | incision, It is the elements on larger scale which show the state where most of the condensed water which generate | occur | produced on the surface of the fin of FIG. 8A was drained, In the fin of FIG. 8A, it is an image figure which shows a mode that heat conduction spreads radially, It is the fragmentary top view which shows the modification which made the fin of FIG. 8A wave shape, FIG. 11B is a cross-sectional view taken along line A4-A4 when a plurality of the fins of FIG. 11A are stacked; FIG. 11B is a cross-sectional view taken along line B4-B4 when a plurality of the fins of FIG. 11A are stacked; It is the elements on larger scale which show the state where condensed water occurred on the surface of the fin of Drawing 10A, It is the elements on larger scale which show a mode that the condensed water which generate | occur | produced on the surface of the fin of FIG. 11A is drained by the back surface of a fin through a notch | incision, It is the elements on larger scale which show the state where most condensate generated on the surface of the fin of Drawing 11A was drained, It is a fragmentary top view which shows the modification of the notch | incision of the fin of FIG. 11A, It is the fragmentary top view of the fin of the conventional fin tube heat exchanger, FIG. 14B is a sectional view taken along line AA in FIG. 14A; FIG. 14B is a sectional view taken along line BB in FIG. 14A; FIG. 14B is an enlarged view of a region C surrounded by a broken line in FIG. 14A and shows how air flows; It is the elements on larger scale which show the state where condensed water occurred on the surface of the fin of Drawing 14A, It is the elements on larger scale which show a mode that the condensed water generated on the surface of the fin of Drawing 14A is drained on the back of a fin via a cut. It is the elements on larger scale which show the state from which the majority of the condensed water which generate | occur | produced on the surface of the fin of FIG. 14A was drained.

The finned tube heat exchanger according to the present invention includes a plurality of fins and a plurality of heat transfer tubes that pass through the plurality of fins and allow fluid to flow therein, and the fins are formed around the heat transfer tubes. It has a pipe peripheral part and a convex part formed so as to surround the pipe peripheral part, and is configured to provide a fluid path that communicates the front and back of the fin with the convex part.

According to this configuration, the air flow flowing into the wake portion of the heat transfer tube can be increased by the convex portion formed so as to surround the tube peripheral portion, and the heat transfer performance of the wake portion of the heat transfer tube is improved. Can be made. Further, the fluid path formed in the convex portion can guide the water on the surface of the fin to the back surface of the fin and drain it smoothly downward in the direction of gravity, so that it is possible to suppress a decrease in drainage.

The fin includes an inclined portion inclined in a corrugated shape with respect to the air flow direction, and the convex portion is opposite to the first inclined surface inclined to the heat transfer tube side and the heat transfer tube. It has a 2nd inclined surface which inclines to the side, and it is preferable that the said inclined part and the said convex part are connected via the said 2nd inclined surface.

According to this configuration, water passing through the fluid path is guided to the corrugated valley, so that the drainage of water generated on the fin surface can be further improved.

Hereinafter, embodiments of the present invention will be described with reference to the drawings. In addition, this invention is not limited by this embodiment.

(First embodiment)
FIG. 1 is a perspective view showing the configuration of the finned tube heat exchanger according to the first embodiment. The finned-tube heat exchanger according to the first embodiment is mounted on an outdoor unit such as an air conditioner, a heat pump water heater, or a heat pump hot water heater.

As shown in FIG. 1, the finned-tube heat exchanger according to the first embodiment includes a plurality of fins 1, a plurality of heat transfer tubes 2 that respectively penetrate the plurality of fins 1, and a heat exchanger mounted on the outdoor unit. An end plate 30 is provided for fixing at the time of placement or for connecting a plurality of heat exchangers.

The plurality of fins 1 are stacked substantially in parallel with a predetermined interval Fp so that a flow path is formed in the air flow direction S.

The plurality of heat transfer tubes 2 are arranged in parallel to each other in a direction intersecting (for example, orthogonal to) the stacking direction of the plurality of fins 1. A fluid such as a refrigerant flows inside each heat transfer tube 2. The finned tube heat exchanger according to the first embodiment is configured such that the air passing between the

fins

1 and 1 adjacent to each other and the refrigerant flowing inside the heat transfer tube 2 exchange heat. Although it does not specifically limit as a refrigerant | coolant which flows through the inside of the heat exchanger tube 2, For example, what has little environmental loads, such as R410A, a propane, a propylene, and a carbon dioxide, is suitable. Note that the heat transfer tubes 2 may be connected to each other by a plurality of curved tubes to form a single meandering heat transfer tube.

The end plate 30 is provided so as to be adjacent to the fin located at the end in the stacking direction among the plurality of fins 1.

FIG. 2A is a partial plan view of the fin 1. 2B is a cross-sectional view taken along line A1-A1 of FIG. 2A. 2C is a cross-sectional view taken along line B1-B1 of FIG. 2A. FIG. 2D is an enlarged view of a region C1 surrounded by a broken line in FIG. 2A and shows how air flows.

The fin 1 is formed in a substantially flat plate shape as shown in FIG. 2A. A plurality of cylindrical fin collars 3 are formed on the fin 1. The heat transfer tube 2 is joined to the fin collar 3 by mechanical expansion or hydraulic expansion of the heat transfer tube 2. A flat tube periphery 4 is formed around the fin collar 3 as shown in FIGS. 2A and 2C.

An annular convex portion 5 is formed around the tube peripheral portion 4 so as to surround the tube peripheral portion 4. The convex part 5 has the 1st inclined surface 5a and the 2nd inclined surface 5b, and functions as a guide of the airflow S. FIG. Moreover, the convex part 5 reduces the dead water area D by attracting the airflows Sa and Sb which wrap around the wake part of the heat exchanger tube 2, as shown in FIG. 2D. The first inclined surface 5a is inclined from the ridge line of the convex portion 5 toward the heat transfer tube 2 side. The second inclined surface 5 b is inclined from the ridge line of the convex portion 5 toward the side opposite to the heat transfer tube 2.

In the convex part 5, a notch 9 is formed along the ridge line of the convex part 5 to be a fluid path communicating with the front and back of the fin 1. In the first embodiment, the cuts 9 are formed at two locations, a position including the upper end of the convex portion 5 and a position including the lower end of the convex portion 5.

It should be noted that the width of each notch 9 is preferably about 0.05 mm to 0.5 mm. In this case, water generated on the surface of the fin 1 can be easily guided to the back surface of the fin 1 by capillary action.

Also, the length L1 of each notch 9 is preferably about 0.5 to 1.5 times (0.5 Fp to 1.5 Fp) of the arrangement interval Fp of the fins 1. In this case, it is possible to suppress a phenomenon (bridge phenomenon) in which water generated on the surface of the fin 1 is formed so as to straddle the stacked fins 1.

Further, each of the cuts 9 is preferably formed in a range where the angle θ with respect to the center line CL parallel to the gravity direction G of the heat transfer tube 2 is about θ = ± 45 °. In this case, since the cut 9 is formed at a position where water on the surface of the fin 1 is likely to accumulate, the water generated on the surface of the fin 1 can be smoothly guided to the back surface of the fin 1.

Next, the drainage action of the fin 1 will be described.

For example, when a fin tube heat exchanger is used as an evaporator, condensed water 20 in which moisture in the air is condensed is generated around the heat transfer tube 2 on the surface side of the fin 1 as shown in FIG. 3A. Since the notch 9 is formed in the convex part 5 along the ridgeline, the condensed water 20 is guided from the surface of the fin 1 to the back surface through the notch 9 as shown in FIG. It is guided (drained) downward in the direction of gravity G along the back surface. Thereby, as shown in FIG. 3C, most of the condensed water 20 generated on the surface of the fin 1 is drained.

Further, the condensed water 20 flowing along the surface of the fin 1 is guided to the back surface of the fin 1 through the notch 9 formed at the upper end of the convex portion 5. The condensed water 20 guided to the back surface of the fin 1 is guided (drained) downward in the gravity direction G along the edge of the convex portion 5.

As described above, according to the finned tube heat exchanger according to the first embodiment, the air flow Sa that wraps around the wake portion of the heat transfer tube 2 by the convex portion 5 formed so as to surround the tube peripheral portion 4. , Sb can be attracted and the dead water area D can be reduced. Thereby, the air flows Sa and Sb flowing into the downstream portion of the heat transfer tube 2 can be increased, and the heat transfer performance of the downstream portion of the heat transfer tube 2 can be improved.

Further, according to the fin tube heat exchanger according to the first embodiment, the condensate 20 on the surface of the fin 1 is guided to the back surface of the fin 1 by the notches 9 formed in the convex portion 5, and the gravity direction G It can drain smoothly downward. Thereby, the fall of the drainage property of the water which generate | occur | produces on the surface of the fin 1 can be suppressed.

Moreover, according to the fin tube heat exchanger concerning this 1st Embodiment, since the notch 9 is provided along the ridgeline of the convex part 5, an assembly of a heat exchanger can be performed irrespective of the direction of the fin 1. FIG. it can. As a result, the working time in the manufacturing process can be shortened, and the production cost can be reduced.

In the first embodiment, the fins 1 are formed in a substantially flat plate shape, but the present invention is not limited to this. For example, as shown in FIGS. 4A to 4C, the fin 1 may be formed in a corrugated shape. That is, the fin 1 may be formed in an M shape so as to be continuous in the order of the valley portion 14a, the mountain portion 13, the valley portion 14, the mountain portion 13, and the valley portion 14a with respect to the air flow direction S. In addition, the peak part 13, the valley part 14, and the valley part 14a are formed by the inclination part 15 which inclines with respect to the air flow direction S.

Further, as shown in FIG. 4A, the convex portion 5 is formed by an inclined surface 5a inclined toward the heat transfer tube 2 and an inclined surface 5b inclined toward the opposite side of the heat transfer tube 2 with the ridge line as a boundary. The formed convex portion 5 and the inclined portion 15 are preferably connected via an inclined surface 5b.

According to this configuration, the condensed water 20 generated on the surface of the fin 1 is guided to the back surface of the fin 1 through the cuts 9 as shown in FIG. 5A. The condensed water 20 guided to the back surface of the fin 1 is guided to the peak portion 13 (becomes a valley when viewed from the back surface side of the fin 1) as shown in FIG. Induced (drained) at any time. Thereby, as shown in FIG. 5C, most of the condensed water 20 generated on the surface of the fin 1 is drained. That is, according to this configuration, since the fluid flow path through which the condensed water 20 flows is formed by the corrugated fins 1 and the notches 9, the drainage of the condensed water 20 can be further improved. .

Also, according to this configuration, as shown in FIG. 4B, the air flow is like a meandering air flow Sc, so that the temperature boundary layer can be made thin to promote heat transfer. Thereby, the heat transfer performance of the fin tube heat exchanger can be further improved.

In the above description, the fin 1 is formed as an M-shaped corrugated fin, but may be a V-shaped corrugated fin in which only one peak 13 is formed on the fin 1.

Further, the heat transfer tube 2 is not limited to the round tube as shown in FIG. 2A, and may be a flat tube, for example.

Further, the shape of the convex portion 5 is not limited to a circle as shown in FIG. 2A, and may be a polygon, for example.

(Second Embodiment)
FIG. 6 is a partial plan view showing the configuration of the fins of the finned tube heat exchanger according to the second embodiment of the present invention. The fin tube heat exchanger of the second embodiment is different from the fin tube heat exchanger of the first embodiment in that a small hole 10 is formed as a fluid path communicating with the front and back of the fin 1 instead of the notch 9. It is a point that has been.

The small hole 10 is formed along the ridgeline of the convex portion 5. In the second embodiment, the small holes 10 are formed at two locations, a position including the upper end of the convex portion 5 and a position including the lower end of the convex portion 5.

According to the finned tube heat exchanger according to the second embodiment, the drainage of the condensed water 20 can be improved while securing the rigidity of the fins 1 and the heat exchanger can be easily assembled. it can.

The diameter of each small hole 10 is preferably about 0.2 mm to 1.0 mm. In this case, water generated on the surface of the fin 1 can be easily guided to the back surface of the fin 1 by capillary action.

Further, the fin 1 may be formed in a corrugated shape as shown in FIG. In this case, the temperature boundary layer can be thinned to promote heat transfer, and the heat transfer performance of the finned tube heat exchanger can be further improved.

(Third embodiment)
FIG. 8A is a partial plan view of a fin included in the finned tube heat exchanger according to the third embodiment of the present invention. 8B is a cross-sectional view taken along line A3-A3 of FIG. 8A. 8C is a cross-sectional view taken along line B3-B3 of FIG. 8A. FIG. 8D is an enlarged view of a region C2 surrounded by a broken line in FIG. 8A and shows how air flows.

The fin tube heat exchanger according to the third embodiment is different from the fin tube heat exchanger according to the first embodiment in that fluids communicating the front and back of the fin 1 with the

inclined surfaces

5a and 5b forming the convex portion 5, respectively. This is the point where the

notches

9a and 9b are formed as paths.

As shown in FIG. 8A, the convex portion 5 is inclined toward the heat transfer tube 2 side with the ridge line as a boundary, and is inclined toward the opposite side of the heat transfer tube 2 and connected to the inclined portion 15. The inclined surface 5b is formed. As shown in FIG. 8D, the convex portion 5 reduces the dead water area D by attracting the air flows Sa and Sb that wrap around the downstream portion of the heat transfer tube 2.

The

notches

9a and 9b are formed at two locations below and above the convex portion 5. The cut 9a is formed to extend in the direction in which the inclined surface 5a is inclined, and the cut 9b is formed to extend in the direction in which the inclined surface 5b is inclined.

The width of the

cuts

9a and 9b is preferably about 0.05 mm to 0.5 mm. In this case, water generated on the surface of the fin 1 can be easily guided to the back surface of the fin 1 by capillary action.

Note that the lengths of the

cuts

9a and 9b are not particularly limited. For example, the cut 9a may be formed up to a portion where the convex portion 5 and the tube surrounding portion 4 are in contact with each other. Further, the notch 9b may be formed up to a portion where the convex portion 5 and the flat plate-like portion of the fin 1 are in contact with each other. Further, the cut 9a and the cut 9b may be formed so as to be connected by a ridge line of the convex portion 5 and integrated.

Next, the drainage action of the fin 1 will be described.

For example, when a finned tube heat exchanger is used as an evaporator, condensed water 20 in which moisture in the air is condensed is generated around the heat transfer tube 2 on the surface side of the fin 1 as shown in FIG. 9A. Since the notch 9a is formed in the inclined surface 5a, and the notch 9b is formed in the inclined surface 5b, the condensed water 20 flows from the front surface of the fin 1 through the

notches

9a and 9b as shown in FIG. 9B. And is guided (drained) downward in the direction of gravity G along the back surface of the fin 1. Thereby, as shown in FIG. 9C, most of the condensed water 20 generated on the surface of the fin 1 is drained.

Further, the condensed water 20 flowing along the surface of the fin 1 is guided to the back surface of the fin 1 through the

cuts

9 a and 9 b formed above the convex portion 5. The condensed water 20 guided to the back surface of the fin 1 is guided (drained) downward in the gravity direction G along the edge of the convex portion 5.

As described above, according to the finned tube heat exchanger according to the third embodiment, the air flow Sa that wraps around the downstream portion of the heat transfer tube 2 by the convex portion 5 formed so as to surround the tube surrounding portion 4. , Sb can be attracted and the dead water area D can be reduced. Thereby, the air flows Sa and Sb flowing into the downstream portion of the heat transfer tube 2 can be increased, and the heat transfer performance of the downstream portion of the heat transfer tube 2 can be improved.

Further, according to the finned tube heat exchanger according to the third embodiment, the condensate 20 generated on the surface of the fin 1 is guided to the back surface of the fin 1 by the

notches

9 a and 9 b formed in the convex portion 5. The water can be smoothly drained downward in the direction of gravity G. Thereby, the fall of the drainage property of the water which generate | occur | produces on the surface of the fin 1 can be suppressed.

In addition, it is preferable to form the

notches

9a and 9b perpendicular to the ridgeline of the convex portion 5. In this case, as shown in FIG. 10, the heat conduction in the fin 1 spreads radially around the heat transfer tube 2. Thereby, the fall of the heat transfer rate of the fin 1 can be suppressed further.

Also, the fin 1 is preferably formed in a corrugated shape as shown in FIGS. 11A to 11C. According to this configuration, since the air flow is like a meandering air flow Sc, the temperature boundary layer can be made thin to promote heat transfer. Thereby, the heat transfer performance of the fin tube heat exchanger can be further improved.

Moreover, according to this structure, since the fluid flow path through which the condensed water 20 flows is formed by the corrugated fin 1 and the

cuts

9a and 9b, the drainage of the condensed water 20 can be further improved. Can do.

Also, according to this configuration, as shown in FIG. 11B, the air flow is like a meandering air flow Sc, so that the temperature boundary layer can be made thin to promote heat transfer. Thereby, the heat transfer performance of the fin tube heat exchanger can be further improved.

Further, as shown in FIG. 13, a plurality of

cuts

9a and 9b may be provided. At this time, the

cuts

9a and 9b are formed radially around the heat transfer tube 2 side so that the end of the

cuts

9a and 9b opposite to the heat transfer tube 2 is located outside the ridge line of the valley portion 14. Is preferred. Thereby, more condensed water 20 can be drained and heat transfer performance can be improved further.

Although the present invention has been fully described in connection with preferred embodiments with reference to the accompanying drawings, various changes and modifications will be apparent to those skilled in the art. Such changes and modifications are to be understood as being included therein, so long as they do not depart from the scope of the present invention according to the appended claims.

As described above, the finned tube heat exchanger according to the present invention can improve the heat transfer performance of the downstream portion of the heat transfer tube without reducing the drainage of water generated on the surface of the fin. It is useful as a heat exchanger used in an air conditioner, a hot water supply device, a heating device or the like.

DESCRIPTION OF SYMBOLS 1 Fin 2 Heat transfer tube 4 Tube surrounding part 5 Convex part 5a 1st inclined surface 5b 2nd

inclined surface

9, 9a, 9b Cutting (fluid path)
10 Small hole (fluid path)
13

Mountain portion

14, 14a Valley portion 15 Inclined portion 30 End plate S Air flow direction Sa, Sb, Sc Air flow G Gravitational direction

Claims

A plurality of fins, and a plurality of heat transfer tubes that pass through the plurality of fins and in which a fluid flows, and the fins include a tube peripheral portion formed around the heat transfer tubes, and the tube peripheral portion. A finned tube heat exchanger having a convex portion formed so as to surround, and provided with a fluid path that communicates the front and back of the fin with the convex portion.
The fin includes an inclined portion that is inclined in a wave shape with respect to the air flow direction, and the convex portion is provided on a side opposite to the heat transfer tube, and a first inclined surface that is inclined toward the heat transfer tube side. 2. The finned tube heat exchanger according to claim 1, further comprising an inclined second inclined surface, wherein the inclined portion and the convex portion are connected via the second inclined surface.