Title:
Heat Exchanger
Kind Code:
A1


Abstract:
A fin (6) is provided with a rib (15) extending generally parallel to an outer edge (25) of the fin (6) and insertion holes (22) placed in staggered arrangement for receiving heat exchange tubes. The insertion holes (22) and the rib (15) are formed such that when an inside diameter of the insertion holes (22) is set as D [mm], a distance between a center of the insertion hole (22) and the outer edge (25) is set as L [mm], a distance between a center of the rib (15) and the outer edge (25) is set as La [mm], a width of the rib (15) is set as LL1 [mm], a thickness of the fin (6) is set as t [mm], a height of the rib (15) is set as h1 [mm], and a minimum distance between the insertion holes is set as P [mm], then 0.4<La<(L−D/2−0.5), 0.15<LL1<0.5, 0.05<t<0.15, 0.5t<h1<2.5t, D<7.5, P>15, and D/P<0.5.



Inventors:
Kitazawa, Masaaki (Shiga, JP)
Taira, Shigeharu (Shiga, JP)
Application Number:
11/791538
Publication Date:
03/13/2008
Filing Date:
11/22/2005
Primary Class:
International Classes:
F28F1/10
View Patent Images:



Primary Examiner:
WALBERG, TERESA J
Attorney, Agent or Firm:
BIRCH, STEWART, KOLASCH & BIRCH, LLP (FALLS CHURCH, VA, US)
Claims:
1. A heat exchanger, comprising: a plurality of heat transfer tubes; and at least one plate-shaped fin (6, 73) having a first rib (15, 75) generally parallel to an outer edge (25, 77) of the fin and having insertion holes (22, 72) for receiving the heat transfer tubes, wherein the first rib (15, 75) is placed closer to the outer edge (25, 77) than all the insertion holes (22, 72) are, wherein the insertion holes (22, 72) are placed in one row or in staggered arrangement in the fin (6, 73), and wherein when an inside diameter of the insertion holes (22, 72) is set as D [mm], a distance between a center of the insertion hole (22, 72) nearest to the first rib (15, 75) and the outer edge (25, 77) is set as L [mm], a distance between a center of the first rib (15, 75) and the outer edge (25, 77) is set as La [mm], a width of the first rib (15,. 75) is set as LL1 [mm], a thickness of the fin (6, 73) is set as t [mm], a height of the first rib (15, 75) is set as h1 [mm], and a minimum value of distance between the insertion holes (22, 72) adjacent to each other is set as P [mm], then
0.4<La<(L−D/2−0.5),
0.15<LL1<0.5,
0.05<t<0.15,
0.5t<h1<2.5t,
D<7.5,
P>15, and
D/P<0.5.

2. The heat exchanger according to claim 1, wherein the insertion holes (72) are placed in staggered arrangement in the fin (73), the insertion holes (72) placed on one side of the fin is generally parallel to the outer edge (77), a second rib (76) extending generally parallel to the outer edge (77) is formed on the fin (73) between the insertion holes (72) which are adjacent to each other in a direction generally perpendicular to a direction in which the outer edge (77) extends, and when a width of the second rib (76) is set as LL2 [mm] and a height of the second rib (76) is set as h2 [mm], then
0.15<LL2<0.5, and
0.5t<h2<2.5t.

Description:

TECHNICAL FIELD

The present invention relates to a heat exchanger. More particularly, the invention relates to a heat exchanger suitable for use in air conditioners.

BACKGROUND ART

Conventionally, there has been a heat exchanger disclosed in JP 2-309195 A.

This heat exchanger includes fins and pipes. The fins are each formed from a plate in a rectangular shape. The fins are placed at intervals. The fins each have a plurality of insertion holes formed for insertion of the pipes therethrough. The insertion holes are provided in a staggered arrangement in the fins. Between the insertion holes provided in a staggered arrangement in each fin, a plurality of protruding threads in an approximately linear shape are formed. The plurality of protruding threads are generally parallel to each other. The protruding threads extend in directions different from the longitudinal direction of the fin.

The pipes are placed such that they perpendicularly intersect with each fin. More specifically, the pipes are inserted in the insertion holes of the fin in the state of extending in the normal direction to the surface of the fin.

In the conventional heat exchanger, the rigidity of the fin is improved by forming the protruding threads between the insertion holes in the fin. This prevents parts near the insertion holes in the fin from being deformed when the pipes are inserted in the insertion holes.

However, in the conventional heat exchanger, since the protruding threads extend in a direction different from the longitudinal direction of the fin, it is impossible to achieve sufficient reinforcement concerning the longitudinal direction of the fin, which has largest influence on the strength of the fin, thereby causing a problem of an insufficiently reinforced fin.

Moreover, the conventional heat exchanger has a difficulty in increasing rigidity of the fin even with formation of protruding threads when the size of the insertion holes is large, when the minimum distance value between the adjoining insertion holes is small, and/or when the width of the fin is small.

Moreover in the conventional heat exchanger, when the height of the protruding thread provided on the fin is large, it interferes with the flow of air passing outside of the pipe, which causes the heat exchanger to have a decreased heat exchanging efficiency.

SUMMARY OF THE INVENTION

An object of the present invention is to provide a heat exchanger capable of increasing the rigidity of a fin and preventing deterioration of heat exchanging efficiency.

In order to attain the object, the present invention provides a heat exchanger, comprising:

a plurality of heat transfer tubes; and

at least one plate-shaped fin having a first rib generally parallel to an outer edge of the fin and having insertion holes for receiving the heat transfer tubes,

wherein the first rib is placed closer to the outer edge than all the insertion holes are,

wherein the insertion holes are placed in one row or in staggered arrangement in the fin, and wherein when an inside diameter of the insertion holes is set as D [mm], a distance between a center of the insertion hole nearest to the first rib and the outer edge is set as L [mm], a distance between a center of the first rib and the outer edge is set as La [mm], a width of the first rib is set as LL1 [mm], a thickness of the fin is set as t [mm], a height of the first rib is set as h1 [mm], and a minimum value of distance between the insertion holes adjacent to each other is set as P [mm], then
0.4<La<(L−D/2−0.5),
0.15<LL1<0.5,
0.05<t<0.15,
0.5t<h1<2.5t,
D<7.5,
P>15, and
D/P<0.5.

It is to be noted that the center of the rib refers to the center in the width direction of the rib.

According to the present invention, the first rib is formed so as to extend generally parallel to the outer edge of the fin, so that the strength of the fin is increased effectively.

According to the present invention, since the insertion holes for insertion of the heat transfer tubes are placed in one row or in staggered arrangement in the fin, more heat transfer tubes can be placed without decreasing the strength of the fin.

According to the present invention, because 0.4<La holds, it is possible to prevent the center of the rib from becoming too close to the outer edge of the fin and therefore deformation of the edge portion and/or the first rib of the fin can be avoided. Also, because La<(L−D/2−0.5) holds, it is possible to prevent the center of the first rib becoming close to the insertion holes enough to cause deformation of the first rib.

According to the present invention, 0.15<LL1, 0.05<t, 0.5t<h1, D<7.5, 15<P, and D/P<0.5 hold, and the rib having a size larger than a predetermined size is formed on the fin having strength larger than a predetermined strength. This makes it possible to certainly reinforce the fin having strength larger than the predetermined strength with the rib having a high reinforcement effect. Therefore, the strength of the fin is brought to a satisfactory level, and fin deflection and fin tilting are certainly prevented from occurring during an operation of stacking the fins.

According to the present invention, because LL1<0.5 and h1<2.5t hold, the rib is not excessively large. This prevents the rib from becoming resistance against a heat transfer medium, thereby preventing generation of turbulent flow and the like in a flow of the heat transfer medium. Therefore, the flow of the heat transfer medium can be smoothed and the decrease in heat exchanging efficiency, which would otherwise be caused by change of the heat transfer medium due to the formation of the rib, is certainly prevented.

Also, according to the present invention, t<0.15 holds so that the thickness of the fin is not too large. This makes it possible to increase the stacking or packing density of fins and to thereby achieve excellent heat exchange efficiency. Also, production costs of the fin can be reduced.

In one embodiment, the insertion holes are placed in staggered arrangement in the fin,

the insertion holes placed on one side of the fin is generally parallel to the outer edge,

a second rib extending generally parallel to the outer edge is formed on the fin between the insertion holes which are adjacent to each other in a direction generally perpendicular to a direction in which the outer edge extends, and

when a width of the second rib is set as LL2 [mm] and a height of the second rib is set as h2 [mm], then
0.15<LL2<0.5, and
0.5t<h2<2.5t.

According to the embodiment, the second rib is formed in the fin between the insertion holes that are adjacent to each other in the above approximately perpendicular direction, so that the strength near the center of the fin is increased and thereby the strength of the fin can be further increased.

According to the embodiment, 0.15<LL2<0.5 and 0.5t<h2<2.5t, so that reinforcement of the fin is ensured while the flow of a heat transfer medium is smoothed.

EFFECT OF THE INVENTION

According to the present invention, the first rib is formed so as to extend generally parallel to the outer edge of the fin, so that the strength of the fin is increased effectively.

According to the present invention, since the insertion holes for insertion of the heat transfer tubes are placed in one row or in staggered arrangement in the fin, more heat transfer tubes can be placed without decreasing the strength of the fin.

According to the present invention, 0.4<La<(L−D/2−0.5), 0.15<LL1, 0.05<t, 0.5t<h1, D<7.5, 15<P, and D/P<0.5 hold, it is possible to certainly reinforce a fin having strength larger than a predetermined strength with the rib having a high reinforcement effect. Therefore, the strength of the fin is brought to a satisfactory level, and fin deflection and fin tilting is certainly prevented from occurring during stacking of fins.

According to the present invention, because LL1<0.5 and h1<2.5t hold, the rib is not excessively large. This prevents the rib from becoming resistance against a heat transfer medium, thereby preventing generation of turbulence and the like in a flow of the heat transfer medium. Therefore, the flow of the heat transfer medium can be smoothed and the decrease in heat exchanging efficiency, which would otherwise be caused by change of the heat transfer medium, is certainly prevented.

Also, according to the present invention, because of t<0.15, it is possible to increase the stacking ability of fins and to thereby achieve excellent heat exchange efficiency.

According to the present invention, the second rib is formed between the adjacent rows of the insertion holes in the fin, so that the strength of a part near the center of the fin is increased and thereby the strength of the fin can be further increased.

BRIEF DESCRIPTION OF THE DRAWINGS

The present invention will become more fully understood from the detailed description given hereinbelow and the accompanying drawings which are given by way of illustration only, and thus are not intended to limit the present invention, and wherein:

FIG. 1 is a schematic cross sectional view showing an air conditioner having a heat exchanger in a first embodiment of the present invention;

FIG. 2A is a detailed view showing a part of a fin included in the heat exchanger of the first embodiment;

FIG. 2B is a detailed view showing a part of a fin included in the heat exchanger of the first embodiment;

FIG. 3A is a view showing an example of the first rib formed on the fin;

FIG. 3B is a view showing an example of the first rib formed on the fin;

FIG. 3C is a view showing an example of the first rib formed on the fin;

FIG. 3D is a view showing an example of the first rib formed on the fin; and

FIG. 4 is a partial enlarged view showing a fin of a heat exchanger in a second embodiment of the present invention.

DETAILED DESCRIPTION OF THE INVENTION

The present invention will be described in detail below based on the embodiments shown in the figures.

First Embodiment

FIG. 1 is a schematic cross sectional view showing an air conditioner using a heat exchanger in the first embodiment of the present invention. In FIG. 1, reference numeral 1 denotes a blower fan, and 2 denotes a heat exchanger. In FIG. 1, arrow a shows a vertically upward direction in the state where the heat exchanger is placed in the air conditioner in use, and arrow b shows a flow direction of air as a heat transfer medium. In FIG. 1, a casing in which the blower fan 1 and the heat exchanger 2 are housed is omitted for simplicity's sake.

This air conditioner is designed such that the blower fan 1 is rotated to blow out air, which was sucked in via the heat exchanger 2, through an unshown blowoff opening.

The heat exchanger 2 includes fins 6 and heat transfer tubes (unshown). The fins 6 are provided so as to be disposed at specified intervals in a direction perpendicular to the drawing sheet of FIG. 1. Each fin 6 is in a flat plate shape. The fin 6 has a configuration which is bent like an upset V-letter so that its upper part in the vertical direction shown in FIG. 1 by arrow a forms a protruding section.

The fin 6 has an outer edge inclined with respect to the vertical direction, and also has a first section 8 and a second section 9 which form the bent part, and a third section 10 which links to a lower part in the vertical direction of the second section 9. As shown in FIG. 1, the first section 8 is located downstream of the flow of air from the second section 9. The third section 10 extends in a generally vertical direction. The first section 8, the second section 9, and the third section 10 have an elongate, rectangular-shaped cross section.

A first rib 15 extending generally in parallel with the longitudinal direction of the second section 9 is formed on a longitudinal edge portion on the leeward of the second section 9. Thus, in the first embodiment, the fin 6 has a rectangular-shaped section, with the first rib 15 extending generally in parallel with an outer edge of the longitudinal direction of the rectangular-shaped section.

There are arranged a plurality of heat transfer tubes. Each heat transfer tube extends in a direction in which the fins 6 are arranged or arrayed, i.e., in the direction normal to the surface of the plate-shaped fin 5 (a direction perpendicular to the drawing sheet of FIG. 1). The heat transfer tubes are inserted through the fins 6 which are arrayed at specified intervals. As shown in FIG. 1, in each of the first section 8, the second section 9, and the third section 10, the heat transfer tubes are provided in two rows in staggered arrangement.

More specifically, in the first section 8, the insertion holes are arranged in two rows in the width direction and in 16 rows in the longitudinal direction, while in the second section 9, the insertion holes are arranged in two rows in the width direction and twelve rows in the longitudinal direction. In the third section 10, the insertion holes are arranged in two rows in the width direction and in eight rows in the longitudinal direction.

Each of the two rows arranged in the width direction of the insertion holes in the first section 8 is generally parallel to the longitudinal outer edge of the first section 8, while each of the two rows arranged in the width direction of the insertion holes in the second section 9 is generally parallel to the longitudinal outer edge of the second section 9. Each of the two rows arranged in the width direction of the insertion holes in the third section 10 is generally parallel to the longitudinal outer edge of the third section 10.

Fluid runs through the heat transfer tubes. This heat exchanger performs heat exchange between the fluid flowing through the heat transfer tubes and the air running over the heat transfer tube.

FIGS. 2A and 2B are views showing the second section 9 of the fin 6 in detail. More specifically, FIG. 2A is a partial enlarged view showing the second section 9 of the fin 6. FIG. 2B is a part of the cross sectional view of FIG. 2A taken along an α-α line.

In FIG. 2A and FIG. 2B, reference numeral 15 denotes a first rib and reference numeral 22 denotes an insertion hole for insertion of the heat transfer tube formed in the fin 6. In FIG. 2A, arrow b shows a flow of air. In FIG. 2A, only the inside diameter of the insertion hole 22 is shown and the detailed aperture shape of the insertion hole is omitted for simplicity's sake.

The rib 15 extends generally in parallel with an outer edge 25 of the plate-shaped fin 6. The plate-shaped fin 6 has insertion holes 22 for insertion of a plurality of heat transfer tubes. Moreover, the first rib 15 is placed closer to the outer edge 25 than all the insertion holes 22 are.

In the first embodiment, as shown in FIG. 2A and FIG. 2B, when the inside diameter of the insertion hole 22 is set as D [mm], a distance between the center of the insertion hole 22 nearest to the rib 15 and the outer edge 25 is set as L [mm], and a distance between the center of the rib 15 and the outer edge 25 is set as La [mm], then La is designed to satisfy the following equation (1):
0.4<La<(L−D/2−0.5) (1)

As shown in FIG. 2A, when a minimum value of the distance between the insertion holes 22 adjacent to each other is set as P [mm], the insertion hole 22 is formed such that the following equations (2) to (4) are satisfied:
D<7.5 (2)
15<P (3)
D/P<0.5 (4)

As shown in FIG. 2B, when the width of the first rib 15 is set as LL1 [mm], the thickness of the fin 6 is set as t [mm] and the height of the first rib 15 is set as h1 [mm], then the fin 6 and the first rib 15 are set so as to satisfy the following equations (5) to (7).
0.15<LL1<0.5 (5)
0.05<t<0.15 (6)
0.5t<h1<2.5t (7)

According to the heat exchanger in the first embodiment, the first rib 15 is formed so as to extend along the outer edge 25 of the fin 6 (generally parallel to the outer edge 25 of the fin 6), so that the strength of the fin 6 is increased effectively.

According to the heat exchanger in the first embodiment, the heat transfer tubes are placed in staggered arrangement through the fin 6, so that an increased number of heat transfer tubes can be placed without decreasing the strength of the fin 6.

According to the heat exchanger in the first embodiment, 0.4<La holds, which prevents the center of the first rib 15 from becoming too close to the outer edge of the fin 6 and thus avoids deformation of the edge portion and/or the first rib 15 of the fin 6. Also, because La<(L−D/2−0.5) holds, the center of the first rib 2 is prevented from becoming too close to the insertion holes 22 and thus deformation of the first rib 15 is avoided.

According to the heat exchanger in the first embodiment, 0.15<LL1, 0.05<t, 0.5t<h1, D<7.5, 15<P, and D/P<0.5 hold, and the first rib 15 having a size larger than a predetermined size is formed on the fin 6 having strength larger than a predetermined strength. This makes it possible to certainly reinforce the fin 6 having strength larger than a predetermined strength with the first rib 15 having a high reinforcement effect. Therefore, the strength of the fin 6 is brought to a satisfactory level, and fin deflection and fin tilting are certainly prevented from occurring during a stacking operation of the fins 6.

According to the heat exchanger in the first embodiment, LL1<0.5 and h1<2.5t holds, which conditions prevent the first rib 15 from becoming too large. This in turn prevents the first rib 15 from becoming resistance against air flow, thereby preventing generation of turbulent flow and the like in the air flow. Therefore, the air flow can be smoothed and the decrease in heat exchanging efficiency, which would otherwise be caused by change of the air flow due to the formation of the first rib 15, is certainly prevented.

According to the heat exchanger in the first embodiment, t<0.15 holds so that the thickness of the fin 6 is not too large. This makes it possible to increase the stacking or packing density of the fins 6 and to achieve excellent heat exchange efficiency.

In the heat exchanger in the first embodiment, as shown in FIG. 2B, the first rib 15 is formed in such a manner that it projects from one surface 27 of the plate-shaped fin 6 so as to satisfy the equations (1) to (7). However, in this invention, a plurality of first ribs that satisfy the equations (1) to (7) may be formed so that they project from one surface of the plate-shaped fin. A plurality of first ribs that satisfy the equations (1) to (7) may also be formed so as to project from both the surfaces (e.g., surface 27 and surface 28 in FIG. 2B) of the plate-shaped fin.

In the heat exchanger of the first embodiment, one first rib 15 generally parallel to the outer edge 25 is formed only on the leeward side in the width direction of the second section 9. However, in this invention, a plurality of ribs may be formed so as to satisfy the equation (1) to (7). For example, it is acceptable not only to provide one or more first ribs generally parallel to the outer edge on the leeward side in the width direction of the second section, but also to provide one or more first ribs generally parallel to the outer edge of the first section on the windward side in the width direction of the first section, while providing one or more first ribs generally parallel to the outer edge of the first section on the leeward side in the width direction of the first section and providing one or more first ribs generally parallel to the outer edge of the third section on the leeward side in the width direction of the third section.

Although in the heat exchanger of the first embodiment, the heat transfer tubes are placed in two rows in staggered arrangement in the width direction of the second section 9 and one first rib is formed on the leeward side of the second section 9, the heat exchanger in this invention may be structured so that heat transfer tubes are arranged in one row, i.e., one per the width of the fin, or in three or more rows in staggered arrangement in the width direction of the fin at least in a part of the fin and that one or more first ribs which satisfy the equations (1) to (7) are formed at least in a part of the longitudinal edge portion of the fin.

For example, as shown in FIG. 3A, holes for insertion of heat transfer tubes may be placed in one row in a fin 30, while at an longitudinal edge portion of the fin 30 on the downstream side of the flow of air shown by arrow c, one first rib 32 generally parallel to an outer edge of the edge portion may be formed. Also, as shown in FIG. 3B, holes for insertion of heat transfer tubes may be placed in one row, i.e., one hole per the width, in a fin 40, while at a longitudinal edge portion of the fin 40 on the upstream side of the flow of air shown by arrow d, one first rib 42 generally parallel to an outer edge of the edge portion may be formed. Also, as shown in FIG. 3C, holes for insertion of heat transfer tubes may be placed in one row in a fin 50, while at longitudinal edge portions of the fin 50 on the upstream side and the downstream side of the flow of air shown by arrow e, first ribs 52 and 53 generally parallel to outer edges of those edge portions may be formed, respectively. Also, as shown in FIG. 3D, holes for insertion of heat transfer tubes may be placed in two rows in staggered arrangement in the width direction of a fin 60, while at longitudinal edge portions of the fin 60 on both the upstream side and the downstream side of the flow of air shown by an arrow f, first ribs 62, 63 generally parallel to outer edges of those edge portions may be formed, respectively.

In the heat exchanger of the embodiment, the first rib 15 is formed in almost the entire edge portion on the leeward of the second section 9. According to this invention, however, the first rib may be provided only in a part of the edge portion such that the first rib extends generally parallel to the part of the outer edge of the fin. For example, the first rib may be provided only in a part of the edge portion on the leeward of the second section so as to extend generally parallel to the outer edge of that part of the edge portion.

In the heat exchanger of the first embodiment, the fin 6 is composed of the first section 8 and second section 9 which form a bend section, and the third section 10. However, according to this invention, the fin on which the first rib is formed may take any shape, without being limited to the shape described in this embodiment, for example, the fin may be composed of one plate having a flat or circular-arc shaped cross section.

In the heat exchanger of the first embodiment, as shown in FIG. 2B, a groove 29 having a trapezoidal cross section is formed on the back side of the area where the first rib 15 is formed. In this invention, however, grooves other than the groove having a trapezoidal cross section, such as grooves having a V-shaped section or a U-shaped section, may be formed on the back side of the area where the first rib is formed. It is not imperative to form the groove on the back side of the area where the first rib is formed.

Moreover in the heat exchanger of this invention, the first rib may be formed in all of the plurality of fins. The first rib may be formed only in one or more of the plurality of fins and there may be fins without the first rib.

Second Embodiment

FIG. 4 is a partial enlarged view showing a second section 79 of a fin 73 included in a heat exchanger of a second embodiment. The heat exchanger of the second embodiment is different from the heat exchanger of the first embodiment only in that a second rib 76 being generally parallel to the first rib 75 and having the shape generally identical to the first rib 75 is formed between the rows of insertion holes 72 placed in staggered arrangement in the width direction in the second section 79 for receiving the heat transfer tubes.

In the heat exchanger of the second embodiment, description of the component parts identical to those in the heat exchanger of the first embodiment will be omitted. In the heat exchanger of the second embodiment, description of operation, effects and modifications similar or identical to those of the heat exchanger in the first embodiment will be omitted, and only the structure, operation, effects and modifications different from those of the heat exchanger in the first embodiment will be explained.

As shown in FIG. 4, the insertion holes 72 for insertion of heat transfer tubes are placed in two rows and in staggered arrangement in width direction in the second section 79 of the fin 73. Each row of the insertion holes 72 provided totally in staggered arrangement in width direction is generally parallel to a longitudinal outer edge 77 of the second section 79 and to the first rib 75. The second rib 76 is formed between the rows of the insertion holes 72 in the second section 79 in the state generally parallel to the outer edge 77 and the first rib 75.

In the heat exchanger of the second embodiment, the second rib 76 is formed between the rows of the insertion holes 72 in the second section 79 of the fin 73, so that the strength of a central area of the second section 79 of the fin 73 is increased, by which the strength of the fin 73 is increased further.

In the heat exchanger of the second embodiment, the insertion holes 72 are arranged in two rows and in staggered arrangement in the width direction of the second section 79 and the second rib 76 is formed between the two rows juxtaposed in the width direction. However, in this invention, the insertion holes for insertion of heat transfer tubes may be arranged in two or more rows juxtaposed in the width direction in at least a part of the fin, and two or more second ribs may be formed between a given row and a row adjacent to the row in the width direction. The insertion holes for insertion of heat transfer tubes may also be arranged in three or more rows in at least a part of the fin, and one or more second ribs may be placed between two or more different rows.

Moreover, in the heat exchanger of the second embodiment, the second rib 76 being generally parallel to the first rib 75 and having the shape generally identical to the first rib 75 is formed between the rows of the insertion holes 72. In this invention, a second rib, which is generally parallel to the first rib and which satisfies equations obtained by rewriting the equations (5) and (7) [herein, the equations obtained by rewriting the equations (5) and (7) refer to the equations obtained by rewriting the width LL1 [mm] of the first rib 15 as the width LL2 [mm] of the second rib 76, and the height h1 [mm] of the first rib 15 as the height h2 [mm] of the second rib 76 in the equations (5) and (7)], may be formed between the rows of the insertion holes for insertion of heat transfer tubes.

Although the heat exchanger of this invention is applied to air conditioners in the first and the second embodiments, it should be understood that the heat exchanger of this invention can be applied to devices other than the air conditioners, such as the refrigerators.

Embodiments of the invention being thus described, it will be obvious that the same may be varied in many ways. Such variations are not to be regarded as a departure from the spirit and scope of the invention, and all such modifications as would be obvious to one skilled in the art are intended to be included within the scope of the following claims.