KR20120044850A - Heat exchanger - Google Patents

Abstract

PURPOSE: A heat exchanger is provided to smoothly heat-exchange between air and heat exchange fins and to improve heat exchange rate by preventing generation of scale on the heat exchange fins. CONSTITUTION: A heat exchanger comprises a refrigerant pipe and heat exchange fins(30). Refrigerant flows through the refrigerant pipe. The heat exchange fins are coupled to the outer circumference of the refrigerant pipe. The heat exchange fin comprises a plate(40), an uneven part, slits(50), and a louver. The uneven part is projected from the plate. The slits are arranged in both sides of the uneven part and guides air to the uneven part. A louver is formed in the uneven part to heat-exchange with the air passed through the slits.

Description

Heat exchanger {HEAT EXCHANGER}

The present invention relates to a heat exchanger, and more particularly, to a heat exchanger having an improved structure for exchanging heat.

The heat exchanger is a device used in a device using a refrigeration cycle, such as an air conditioner or a refrigerator, and includes a plurality of heat exchange fins and a refrigerant pipe installed to guide the refrigerant and pass through the plurality of heat exchange fins. The heat exchange fins increase the heat exchange efficiency between the refrigerant flowing through the refrigerant pipe and the external air by increasing the contact area of the air introduced into the heat exchanger from the outside.

In general, the heat exchange efficiency is increased as the contact area of the heat exchange fin in contact with the air passing through the heat exchange fin and the resistance of the air in contact with the heat exchange fin is small. In this case, the resistance is largely applied to the air passing through the heat exchange fins, and if the contact area is narrowed to reduce the resistance applied to the air, the desired heat exchange efficiency cannot be obtained. Therefore, an optimum fin shape according to the heat exchanger is required.

In addition, when the heat exchanger is used as an evaporator (that is, when the refrigeration cycle performs a heating operation), if the outdoor temperature becomes too low, the surface temperature of the heat exchanger drops below zero, and the heat exchanger that cools the moisture contained in the outdoor air. It is implanted on the surface of the heat exchanger, and the heat exchange capacity of the heat exchanger is reduced.

One aspect of the present invention provides a heat exchanger having a structure capable of smoothly performing heat exchange between air and heat exchange fins.

In addition, the present invention provides a heat exchanger having a structure for suppressing the idea that may occur on the surface of the heat exchange fins.

According to an aspect of the present invention, a heat exchanger includes: a refrigerant pipe through which a refrigerant flows; and a heat exchange fin coupled to an outer circumferential surface of the refrigerant pipe, wherein the heat exchange fin includes: a plate; and an uneven portion protruding from the plate; And a slit portion disposed at both sides of the uneven portion to guide air to the uneven portion; and a louver portion provided at the uneven portion to heat-exchange with air past the slit portion.

The louver portion includes a first cutout portion provided in the uneven portion, and a plurality of guide plates spaced apart from each other in parallel to the uneven portion, and the first cutout portion and the plurality of guide plates include: Can be placed alternately.

The width of the guide plate is characterized in that the 0.5mm or more and 3mm or less .

The uneven portion includes a first inclined surface disposed to be inclined with the plate, the guide plate is provided on the first inclined surface, the angle formed by the guide plate and the first inclined surface is characterized in that 10 ° or more and 60 ° or less. .

The slit portion may include a second inclined surface disposed to be inclined with the plate, an upper surface formed between the second inclined surface, and a second cutout provided at a rear of the upper surface.

The upper surface has a width of 0.5 mm or more and 5 mm or less.

The first inclined surfaces are disposed symmetrically to the plate, the distance between the line formed by the first inclined surfaces and the plate forms the height of the uneven portion, and the height of the uneven portion is 0.5 mm or more and 4 mm or less.

The first inclined surface is disposed symmetrically to the plate, the distance between the plate and the flat surface formed between the first inclined surfaces and the first inclined surface forms the height of the uneven portion, the height of the uneven portion It is characterized by being 0.5 mm or more and 4 mm or less.

The heat exchange fins may be formed by stacking the plates at intervals from each other.

In addition, the heat exchanger according to the spirit of the present invention; And a heat exchanger comprising a tube for guiding the fluid; and a heat exchange fin in contact with the tube to mediate heat exchange between the fluid and the outside air, wherein the heat exchange fin, the tube And a seating groove for seating and supporting the recess, and an uneven portion provided between the seating grooves and protruding in the direction in which the tube extends; and a slit disposed around the uneven portion to accelerate a flow rate of air introduced into the uneven portion And a louver portion formed in the uneven portion to promote heat exchange between the air passing through the slit portion and the fluid.

The louver part may include a plurality of guide plates spaced apart from each other and arranged in parallel, and a plurality of first cutout parts alternately arranged with the plurality of guide plates.

The uneven parts may include a first inclined surface symmetrically disposed to form a 'V' shape, and the plurality of guide plates and the plurality of first cutouts may be provided on the first inclined surface.

The angle formed between the first slope and the guide plate provided on the first slope is 10 ° or more and 60 ° or less.

The width of the guide plate is characterized in that the 0.5mm or more and 5mm or less.

The slit part may include a second inclined surface protruding in a direction in which the tube extends, an upper surface formed between the second inclined surface, and a second cutout provided at a rear of the upper surface.

The upper surface has a width of 0.5 mm or more and 5 mm or less.

The concave-convex portion includes a first inclined surface disposed symmetrically with each other, and a flat surface connected to the first inclined surface and formed between the first inclined surface, wherein the plurality of guide plates and the plurality of first cutouts are formed in the first inclined surface. It may be provided on an inclined surface or the flat surface.

According to the embodiments of the present invention, since the heat exchange between the air and the heat exchange fin is smooth, the heat exchange efficiency is increased.

In addition, the heat exchange efficiency is increased because the idea that can occur on the surface of the heat exchange fin is suppressed.

1 is a perspective view of a heat exchanger according to an embodiment of the present invention.
FIG. 2 is a perspective view of a portion of the heat exchange fin shown in FIG. 1; FIG.
3 is a front view of FIG. 2;
4 is a cross-sectional view taken along line II of FIG. 3.
5 is an enlarged cross-sectional view of a portion of FIG. 4.
FIG. 6 illustrates a flow of air flowing around the heat exchange fin of FIG. 3.
7 is a cross-sectional view of the II-II portion of FIG.
8 is a diagram illustrating heat exchange performance of the heat exchange fin of FIG. 3.
9 is a front view of an existing pin.
10 is a cross-sectional view of the AA portion of FIG. 9.
11 is a front view of a heat exchanger according to a second embodiment of the present invention.
12 is a front view of a heat exchanger according to a third embodiment of the present invention.
13 is a cross-sectional view taken along the line III-III of FIG. 12;
14 is a front view of a heat exchanger according to a fourth embodiment of the present invention.
15 is a cross-sectional view taken along the line IV-IV of FIG. 14.
16 is a front view of a heat exchanger according to a fifth embodiment of the present invention.
17 is a cross-sectional view taken along the line VV of FIG. 16.
18 is a front view of a heat exchanger according to a sixth embodiment of the present invention.
19 is a cross-sectional view taken along the line VI-VI of FIG. 18;

Hereinafter, with reference to the accompanying drawings an embodiment according to the present invention will be described in detail.

1 is a perspective view of a heat exchanger according to an embodiment of the present invention.

As illustrated in FIG. 1, the heat exchanger 10 includes a coolant tube 20 through which a coolant flows, and a heat exchange fin 30 coupled to an outer circumferential surface of the coolant tube 20.

The coolant tube 20 is provided in a tube shape in which the inside of the coolant tube flows. The refrigerant pipe 20 is preferably formed as long as possible in order to widen the heat exchange area between the refrigerant flowing through the refrigerant pipe 20 and the outside air, but since the space is restricted to form only one direction, the heat exchanger ( At both ends of 10), the refrigerant pipe 20 is bent in a direction opposite to the direction in which it has been extended. By repeating this bending several times, it is possible to efficiently expand the heat exchange area in a limited space.

The refrigerant flowing in the refrigerant pipe 20 is a mixture of Freon having different properties, and a plurality of refrigerants including R-134a and R410A are used.

The refrigerant exchanges heat with the outside air while the phase changes (compresses) from the gaseous state to the liquid state, or heat exchanges with the outside air with the phase change (expanded) from the liquid state to the gaseous state. When the heat exchanger 10 is used as a condenser, the heat exchanger 10 is used as an evaporator when the refrigerant phase changes from a liquid state to a gaseous state.

The refrigerant flows through the refrigerant pipe 20 and releases heat to or absorbs heat from the surroundings while compressing or expanding the refrigerant pipe 20. The refrigerant is supplied to the refrigerant pipe 20 in order to allow the refrigerant to efficiently release or absorb heat during compression or expansion. Heat exchange fins 30 are coupled.

The heat exchange fins 30 are stacked in plural at regular intervals in a direction in which the refrigerant pipe 20 extends.

The heat exchange fin 30 is made of various metal materials including aluminum having high thermal conductivity, and is in contact with and coupled to the outer circumferential surface of the refrigerant pipe 20 to substantially widen the contact area between the outside air and the refrigerant pipe 20.

As the spacing between the heat exchange fins 30 is narrower, a greater number of heat exchange fins 30 may be arranged. However, when the spacing becomes too narrow, air flowing into the heat exchanger 10 as shown in FIG. It is necessary to adjust the gap properly because it acts as a resistance to (F) and may cause a pressure loss.

FIG. 2 is a perspective view illustrating a portion of the heat exchange fin in FIG. 1, FIG. 3 is a front view of FIG. 2, FIG. 4 is a cross-sectional view taken along line II of FIG. 3, and FIG. 5 is an enlarged portion of FIG. 4. It is a cross section.

As shown in FIGS. 2 to 5, the heat exchange fin 30 has a plate 40, an uneven portion 70 protruding from the plate 40, and slits provided on both sides of the uneven portion 70. ) 50 and a louver portion 60 provided in the uneven portion 70.

The plate 40 is a thin plate having a material such as aluminum alloy, and includes a seating groove 32 in contact with the refrigerant pipe 30.

The seating groove 32 is provided in a shape corresponding to the outer circumferential surface of the coolant pipe 30 so as to contact the outer circumferential surface of the coolant pipe 30 to support the coolant pipe.

As shown in FIG. 2, the seating groove 32 protrudes forward and backward of the plate 40, which stably supports the coolant pipe 30 and at the same time the coolant pipe 30 and the heat exchange fin 30. In order to facilitate the heat exchange by widening the contact area.

In the front of the plate 40, the uneven portion 70 is formed to protrude.

The uneven portion 70 includes a first inclined surface 72 formed to be inclined at a predetermined angle with the plate 40, and the first inclined surface 72 is disposed symmetrically with each other on the plate 40 so as to be approximately 'V'. To form a child shape.

The first inclined surface 72 guides the air passing through the slit portion 50 to the louver portion 60. That is, the air accelerated while passing through the slit portion 50 may naturally flow on the first slope 72 so that the flow rate of air is not reduced, and the air flowing on the first slope 72 is louver. The heat transfer efficiency is increased by performing heat exchange with the refrigerant flowing through the refrigerant pipe 20 in contact with the (Louver) unit 60.

As described above, the first inclined surface 72 is disposed symmetrically on the plate 40 to form a substantially 'V' shape, where the first inclined surface 72 meets while forming the 'V' shape. The tangent 74 is formed in the vertical direction, and the distance between the tangent 74 and the plate 40 forms the height H of the uneven portion 70.

As the height H of the uneven portion 70 is increased, the area of the first inclined surface 72 is increased, so that the area in contact with the outside air is widened. However, the height H of the uneven portion 70 is too high. In this case, it acts as a resistance to the flow of external air to reduce the flow rate of the air, and to reduce the pressure of the air (pressure loss), because the heat transfer efficiency may be lowered prerequisites, appropriate adjustment is necessary, so the uneven portion 70 It is preferable that height H of () is 0.5 mm or more and 4.0 mm or less.

On the other hand, the first inclined surface 72 may be disposed not symmetrically on the plate 40, details will be described later in the heat exchange fin 300 according to the third embodiment of the present invention.

Slit portions 50 are disposed on both sides of the uneven portion 70.

The slit part 50 prevents the phenomenon of moisture contained in the outdoor air on the surface of the heat exchange fin 30, and accelerates the external air introduced into the heat exchanger 10 to prevent unevenness. A second inclined surface 52 disposed to be inclined with the plate 40 and an upper surface 54 formed between the second inclined surface 52 in a configuration for guiding the 70 and the louver portion 60; The second cutout 56 is provided at the rear of the upper surface 54.

The second inclined surface 52 forms a predetermined angle with the plate 40 to protrude obliquely to form a space through which the outside air can flow between the plate 40 and the upper surface 54.

The upper surface 54 is provided between the second slopes 52 in a substantially trapezoidal plane. The air passing through the slit portion 50 meets the upper surface 54 and splits about the upper surface 54 while flowing through the front and rear surfaces of the upper surface 54 while becoming turbulent flow and further accelerating. do.

Although not shown, the upper surface 54 may be provided in other shapes. That is, it may be provided in a triangular shape, semicircle shape, arc shape, square shape, and the like different from the trapezoidal shape. Although the upper surface 54 has the shape as described above, the air passing through the slit portion 50 meets the upper surface 54 and splits about the upper surface 54. The upper surface 54 is trapezoidal. It is the same as when provided in the plane of shape.

The upper surface 54 and the second inclined surface 52 form a corner portion 58, and the corner portion 58 prevents implantation. Implantation (着 霜) is a phenomenon that the moisture contained in the outside air is attached to the freezing on the surface of the heat exchange fin 30, in particular formed on a flat surface, such as a certain amount of moisture can be easily aggregated, the corner portion 58 as described above By forming a, a predetermined amount or more of moisture hardly aggregates, thereby preventing frosting or slowing down the progression of frosting.

The second cutout 56 is provided at the rear of the upper surface 54 to guide the outside air flowing into the heat exchanger 10 to the louver portion 60, and to the air flowing through the upper surface 54. Ensure that the resistance applied is minimized.

When the heat exchanger 10 is used as an evaporator for heating in winter, the refrigerant flowing through the refrigerant pipe 20 absorbs heat while expanding from a liquid state to a gaseous state, and the temperature of the surface of the refrigerant pipe 20 is generally Although the temperature falls below 0 ° C., the second cutout 56 may be formed to delay the heat exchange between the refrigerant pipe 20 and the slit 50, thereby preventing frosting.

The width D of the upper surface 54 is preferably formed to be 0.5 mm or more and 5.0 mm or less in consideration of resistance acting on the air passing through the slit portion 50.

The slit portion 50 may be disposed on both sides of the uneven portion 70, and at least two or more slits may be separated in the up and down directions of the plate 40.

By dividing the slit portion 50 in the up and down directions of the plate 40, the slit portion 50 and the plate 40 as compared with the case where the slit portion 50 is not separated. ) Has the effect of strengthening the strength.

The louver portion 60 is provided at the uneven portion 70.

The louver portion 60 includes a guide plate 62 provided on the first inclined surface 72 and a first cut portion 64 alternately disposed with the guide plate 62.

The guide plate 62 forms a predetermined angle with the first inclined surface 72 and is spaced apart from each other and arranged in parallel.

The external air accelerated past the slit part 50 flows on the first inclined surface 72 to be in contact with the guide plate 62 to exchange heat. The guide plate 62 increases the heat exchange efficiency by substantially widening the contact area between the heat exchange fin 30 and the outside air.

The smaller the pitch (P, P, width) of the guide plate 62 or the larger the inclination angle α between the guide plate 62 and the first inclined surface 72, the larger the contact area with the outside air. When the pitch P is too small or the inclination angle α becomes too large, the flow rate of air flowing through the louver 60 may decrease due to the influence of the guide plate 62, thereby causing a pressure drop. This results in a decrease in the overall heat transfer efficiency. Therefore, appropriate adjustment of the pitch P and the inclination angle α of the guide plate 62 is required, and the pitch P is preferably 0.5 mm or more and 3.0 mm or less, and the inclination angle α is 10 ° or more and 60 ° or less.

In addition, the corners formed at the outer side of the guide plate 62 prevent the conception or slow the progression of the conception as described above.

The first cutout 64 is provided with a first inclined surface 72 and is alternately disposed with the guide plate 62. The outside air accelerated past the slit part 50 is guided to flow along one surface of the guide plate 62 so that heat transfer between the guide plate 62 and the outside air can proceed smoothly.

FIG. 6 is a view illustrating a flow of air flowing around the heat exchange fin of FIG. 3, and FIG. 7 is a cross-sectional view of part 'A' of FIG. 6.

6 to 7 show the results of calculating the flow of air around the heat exchange fins 30 through the CFD (Computational Fluid Dynamics) method. The lines shown in the figure indicate the direction in which air flows, and the length of the line indicates the flow rate of air, which means that the longer the length of the line is, the faster the flow rate of air is.

6 to 7, it can be seen that the air passing through the slit portion 50 of the heat exchange fin 30 is faster than the surrounding air that does not pass through the slit portion 50. have. This is because the air flowing into the slit part 50 is accelerated while meeting the upper surface 54 of the slit part 50.

It can be seen that the air accelerated by the slit portion 50 flows to the louver portion 60 provided on the first inclined surface 72 without decreasing the flow velocity. As described above, the slit unit 50 not only accelerates the air flowing into the slit unit 50, but also guides the introduced air to flow into the louver unit 60. Do it.

The air flows with a particularly high flow rate between the surface of the guide plate 62 and between the guide plate 62 and the guide plate 62, that is, around the first cutout 64, thereby allowing heat exchange with the guide plate 62. do.

FIG. 8 is a diagram illustrating heat exchange performance of the heat exchange fin of FIG. 3, and FIGS. 9 and 10 are front and cross-sectional views of a conventional fin as compared with that of FIG. 3.

As shown in FIGS. 9 and 10, the existing fin 1 includes a slit 5 in the center, but the uneven portion 70 and the louver included in the heat exchange fin 30 of FIG. 3. Louver) 60 is not included.

In the diagram of FIG. 8, the wind speed refers to the flow rate of external air flowing into the fin, and the fin pitch refers to the distance between the fin and the fin. The smaller the pitch, the larger the number of fins in the limited space. Means that.

Comparing the heat transfer performance of the existing and new fins at the same pitch (Pitch = 1.5mm), it can be seen that the new fin has increased heat transfer performance over the existing fins at all wind speeds, and the increase in performance is approximately 7.4% ~ 8.2%.

In addition, even when the pitch of the new fin is increased from 1.5mm to 1.7mm it can be seen that the heat transfer performance of the existing fin with a pitch of 1.5mm. This means that new fins can be used to obtain better heat transfer even if they are used in fewer spaces than conventional fins, thus reducing the cost of materials used to fabricate fins.

11 to 19 are front and cross-sectional views of the heat exchange fins 200, 300, 400, 500 and 600 according to other embodiments of the present invention.

FIG. 11 illustrates a heat exchange fin 200 according to a second embodiment of the present invention, in which a slit part 250 protruding from the front surface of the heat exchange fin 200 is not separated into two parts. Is formed.

12 and 13 illustrate a heat exchange fin 300 according to a third embodiment of the present invention, wherein the uneven portion 370 of the heat exchange fin 300 is asymmetrically formed. That is, the first inclined surfaces 372a and 372b forming the uneven portion 370 form an asymmetric 'V' shape.

The inclination angle β formed between the first inclined surface 372a and the front surface of the plate 40 forming the uneven portion 370 is larger than the inclination angle β 'formed between the first inclined surface 372b and the front surface of the plate 40. Therefore, the width of the first slope 372a is smaller than the width of the first slope 372b. In addition, a tangent 374 is formed at a position where the first inclined surfaces 372a and 372b meet with each other, and is provided at a position away from the center of the plate 40.

14 and 15 illustrate a heat exchange fin 400 according to a fourth embodiment of the present invention, wherein the inclination angle of the guide plate 462 provided at the louver portion 60 of the heat exchange fin 400 is constant. Not.

That is, the inclination angles formed by the plurality of guide plates 462 provided on the first inclined surface 72 and the first inclined surface 72 may be different from each other.

16 and 17 illustrate a heat exchange fin 500 according to a fifth embodiment of the present invention, in which a slit portion 50 protruding from the front surface of the heat exchange fin 500 has one side of the uneven portion 70. Is placed only on.

In this case, it is preferable that the slit part 50 is disposed on one side into which the outside air flows.

18 and 19 illustrate a heat exchange fin 600 according to a sixth embodiment of the present invention, wherein the uneven portion 670 of the heat exchange fin 600 includes a flat surface 676.

The flat surface 676 may be formed between the first sloped surfaces 672, and the first sloped surface 672 may be symmetrically disposed with respect to the flat surface 676. The distance between the flat surface 676 and the plate 40 forms the height of the uneven portion 670, and the height of the uneven portion 670 is preferably 0.5 mm or more and 4 mm or less.

The guide plate 62 may be selectively provided at any one of the first inclined surface 672 or the flat surface 676, or may be provided at both the first inclined surface 672 and the flat surface 676.

Embodiments described above may be combined with each other two or more embodiments. For example, when combining the third and fourth embodiments, the guide plate 462 is formed on the first inclined surfaces 372a and 372b (characteristic of the third embodiment) of the uneven portion 370 which is formed asymmetrically. Each of the first inclined surfaces 372a and 372b may be disposed at different inclination angles (characteristic of the fourth embodiment).

10: heat exchanger, 20: refrigerant tube,
30: heat exchange fin, 32: seating groove,
40: plate, 50: slit portion,
52: second inclined plane, 54: upper plane,
56: first incision, 58: corner,
60: louver part, 62: guide plate,
64: second incision, 70: uneven portion,
72: first inclined plane, 74: tangential.

Claims (17)

A refrigerant pipe through which a refrigerant flows;
And a heat exchange fin coupled to an outer circumferential surface of the refrigerant pipe.
The heat exchange fins,
Plate;
Uneven parts protruding from the plate;
A slit portion disposed at both sides of the uneven portion to guide air to the uneven portion; and
And a louver unit provided to the uneven portion to heat-exchange with the air passing through the slit unit. The method of claim 1,
The louver unit,
A first incision provided in the uneven portion,
It includes a plurality of guide plates spaced apart from each other in parallel to the uneven portion,
And the first cutout and the plurality of guide plates are alternately arranged. The method of claim 2,
Heat exchanger, characterized in that the width of the guide plate is 0.5mm or more and 3mm or less. The method of claim 2,
The uneven portion includes a first inclined surface disposed to be inclined with the plate,
The guide plate is provided on the first inclined surface,
An angle formed between the guide plate and the first inclined surface is 10 ° or more and 60 ° or less. The method of claim 1,
The slit portion,
A second slope inclined with the plate,
An upper surface formed between the second inclined surfaces,
And a second cutout provided at a rear of the upper surface. 6. The method of claim 5,
Heat exchanger, characterized in that the width of the upper surface is 0.5mm or more and 5mm or less. The method of claim 4, wherein
The first inclined surfaces are symmetrically disposed on the plate,
The distance between the line formed by the first inclined surfaces and the plate forms a height of the uneven portion,
The height of the concave-convex portion is a heat exchanger, characterized in that 0.5mm or more and 4mm or less. The method of claim 4, wherein
The first inclined surface is disposed symmetrically to each other on the plate,
The distance between the plate and the flat surface formed between the first inclined surfaces and the first inclined surfaces forms the height of the uneven portion.
The height of the concave-convex portion is a heat exchanger, characterized in that 0.5mm or more and 4mm or less. The method of claim 1,
The heat exchange fin is a heat exchanger, characterized in that the plate is formed by laminating at intervals from each other. A heat exchanger comprising: a tube for guiding fluid; and a heat exchange fin in contact with the tube to mediate heat exchange between the fluid and external air.
The heat exchange fins,
A seating groove for seating and supporting the tube; and
An uneven portion provided between the seating grooves and protruding in a direction in which the tube extends;
A slit portion disposed around the uneven portion to accelerate a flow rate of air flowing into the uneven portion; and
And a louver portion formed in the uneven portion to promote heat exchange between the air passing through the slit portion and the fluid. The method of claim 10,
The louver unit,
A plurality of guide plates spaced apart from each other and arranged in parallel,
And a plurality of first cutouts disposed alternately with the plurality of guide plates. 12. The method of claim 11,
The uneven portion includes a first inclined surface disposed symmetrically with each other to form a 'V' shape,
And the plurality of guide plates and the plurality of first cutouts are provided on the first inclined surface. The method of claim 12,
An angle formed between the first inclined plane and the guide plate provided on the first inclined plane is 10 ° or more and 60 ° or less. The method of claim 13,
Heat exchanger, characterized in that the width of the guide plate is 0.5mm or more and 3mm or less. The method of claim 14,
The slit portion,
A second inclined surface protruding in the direction in which the tube extends;
An upper surface formed between the second inclined surfaces,
And a second cutout provided at a rear of the upper surface. 16. The method of claim 15,
Heat exchanger, characterized in that the width of the upper surface is 0.5mm or more and 5mm or less. 12. The method of claim 11,
The uneven portion and the first inclined surface disposed symmetrically with each other,
A flat surface connected to the first slope and formed between the first slope,
And the plurality of guide plates and the plurality of first cutouts are provided on the first inclined surface or the flat surface.

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