JP2003279279A - Heat exchanger - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To reduce a cost by reducing the number of heat transfer pipes while sufficiently securing a temperature difference between a fin and an air current. <P>SOLUTION: This heat exchanger has a plate-like fin 11, and a pipe 12 penetratingly installed in the fin 11, and exchanges heat between a refrigerant R flowing in the pipe 12 and the air current passing in the extending direction of the fin 11. The fin 11 changes so that the thickness gradually becomes small for becoming more distant from a pipe installing place in at least one direction. <P>COPYRIGHT: (C)2004,JPO

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a heat exchanger used for cooling or heating an air flow or the like, and more particularly to a plate fin tube type heat exchanger used for an air conditioner or the like.

[0002]

2. Description of the Related Art Generally, as a heat exchanger used in an air conditioner or the like, one disclosed in Japanese Patent Laid-Open No. 11-173785 is known. 11 and 12 show a conventional heat exchanger, respectively. In FIG. 11, (a) is a plan view and (b) is (a).
13 is a sectional view taken along line XX in FIG.
(A) is a top view, (b) is a YY line sectional view in (a).

In FIG. 11, the heat exchanger comprises a plurality of plate-shaped fins 1 laminated in parallel with each other and the fins 1.
And a pipe 2 which is inserted in a state orthogonal to each of the above.

The fin 1 has a uniform thickness, and when the heat exchanger is used in an air conditioner, the fin 1 is formed of, for example, an aluminum material having a thickness of about 0.1 mm. A passage 3 through which the air flow passes between the adjacent fins 1.
Are formed, and this air flow passes in the direction indicated by reference numeral 4.

The pipes 2 have a cylindrical shape and are arranged in rows so as to be aligned in a direction orthogonal to the air flow passage direction 4. In the illustrated example, the pipes 2 are in two rows. . Inside the pipe 2, for example, a refrigerant R such as CFC
Is flowing. Thereby, in the heat exchanger, heat is exchanged between the refrigerant R and the airflow via the fins 1 or the pipes 2.

[0006] In such a heat exchanger, the heat exchange process when heating, for example, an air flow will be described as follows. The heat of the refrigerant R flowing in the pipe 2 is transferred to each of the fins 1 via the pipe 2, and the heat of the refrigerant R is transferred from the mounting position of the pipe 2 to the periphery inside each fin 1. become. Then, heat is transferred from the surface of each fin 1 to the airflow of the passage 3,
The air stream will be heated.

Fin efficiency is one of the factors that show the heat exchange capacity of this heat exchanger. The fin efficiency is represented by the ratio of the difference between the fin surface average temperature and the airflow temperature and the difference between the pipe surface temperature and the airflow temperature. That is, the fin efficiency (Φ) is Φ = (fin surface mean temperature−air flow temperature) /
It is represented by (pipe surface temperature-airflow temperature). Generally, the fin efficiency increases as the distance from the pipe to the end of the fin increases, the thickness of the fin increases, or the thermal conductivity of the fin increases, and the maximum value is "1". .

[0008]

Now, consider the case where the number of pipes 2 of the heat exchanger is reduced as shown in FIG. 12 for the purpose of reducing the cost of the heat exchanger. Then, the distance between the adjacent pipes 2 increases, and the area of the fins 1 per pipe increases, and as a result, the distance from the pipes 2 to the ends of the fins 1 also increases. . Since the thickness of the fin 1 is uniform over the entire area, according to FIG. 13 which schematically shows the temperature distribution inside the fin 1, the isothermal lines 5 become dense near the pipe mounting point and at the end of the fin 1. The isothermal line 5 is sparse. This indicates that the temperature is drastically reduced near the pipe mounting location, and therefore the surface temperature at the end of the fin 1 is considerably lower than that near the pipe mounting location. From this, the difference between the average surface temperature of the fins 1 and the temperature of the air flow is not sufficiently large, and the fin efficiency is small, resulting in difficulty in performing good heat exchange. .

It is conceivable to increase the thickness of the fin in order to avoid a decrease in fin efficiency, but this would cause a significant increase in the material cost of the fin, which deviates from the purpose of reducing the cost. It will be. It is also possible to increase the number of fins, but this not only deviates from the above-mentioned purpose of reducing the cost by increasing the material cost of the fins, but also results in a small passage between the fins. However, there is a problem in that the frictional resistance of the air flow is increased, the driving force for blowing air to generate the air flow is increased, and the noise and the driving input are increased.

In view of the above situation, the present invention provides a heat exchanger capable of reducing the cost by reducing the number of heat transfer pipes while ensuring a sufficient temperature difference between the fins and the air flow. The purpose is to

[0011]

To achieve the above object, a heat exchanger according to the present invention comprises a plate-shaped fin and a pipe penetrating the fin, and a refrigerant flowing in the pipe. In a heat exchanger that performs heat exchange with an air flow passing along the extending direction of the fins, the fins gradually have a thickness along at least one direction as the thickness of the fins increases away from the pipe mounting portion. It is characterized in that it changes so as to become smaller.

According to the present invention, since the thickness of the fin gradually decreases along at least one direction as it goes away from the pipe mounting point, even when the thickness near the pipe mounting point is sufficiently secured. It does not cause an increase in material costs.

The heat exchanger according to the next invention is characterized in that, in the above invention, the thickness of the fins varies along the passage direction of the air flow.

According to the present invention, since the thickness of the fins gradually decreases along the passage direction of the air flow as the distance from the pipe attachment point increases, the fin is substantially orthogonal to the passage direction of the air flow around the pipe attachment point. Even if a sufficient thickness is secured in the region in the direction of the arrow, the material cost of the fin does not increase.

In the heat exchanger according to the next invention, in the above invention, the thickness of the fins varies along a direction substantially orthogonal to the passage direction of the air flow. Do

According to the present invention, the thickness of the fins gradually decreases along the direction substantially orthogonal to the passage direction of the air flow as the distance from the pipe mounting location increases. Even when a sufficient thickness is secured in the region along the passage direction, the material cost of the fin does not increase.

In the heat exchanger according to the next invention, in the above invention, a plurality of pipes are installed so as to be arranged in a direction orthogonal to a passage direction of the air flow, and in the fin,
It is characterized in that a cut-and-raised portion having a front edge portion opposed to the air flow passage direction is provided at a portion located between the pipes.

According to the present invention, since the cut-and-raised portion is provided so that its front edge portion faces in the air flow passage direction,
Heat exchange is also performed via the cut-and-raised part.

The heat exchanger according to the next invention is characterized in that, in the above invention, at least one of the legs of the cut-and-raised portion is connected in the vicinity of a pipe mounting portion.

According to the present invention, since at least one of the leg portions of the cut-and-raised portion is connected to the vicinity of the mounting location of the pipe, the thickness of the leg portion becomes large.

[0021]

BEST MODE FOR CARRYING OUT THE INVENTION Preferred embodiments of a heat exchanger according to the present invention will be described in detail below with reference to the accompanying drawings. In the following, for convenience of description, heat exchange when the heat of the refrigerant heats the airflow at a high temperature will be described.

Embodiment 1. 1 and 2 show a first embodiment of a heat exchanger according to the present invention. In FIG. 1, (a) is a plan view of the heat exchanger,
2B is a sectional view taken along the line AA in FIG. 2A, FIG. 2A is an enlarged plan view showing the temperature distribution of the heat exchanger, and FIG. 2B is a sectional view taken along the line BB in FIG. It is a figure. In FIG. 1, the heat exchanger has a plurality of plate-shaped fins 11 stacked in parallel with each other, and a pipe 12 penetrating the fins 11 in a state orthogonal to each of the fins 11. A passage 13 is provided between the adjacent fins 11 for the airflow to pass therethrough. This air flow passes in the direction indicated by reference numeral 14.

The fin 11 is, as shown in FIG.
The thickness thereof changes along the air flow passage direction 14.
More specifically, the fin 11 has the maximum thickness in the vicinity (hereinafter, also referred to as the central portion) 11a where the pipe 12 is mounted, and the fin 11 has front end portions 11b and 11b corresponding to the upstream side and the downstream side of the passage 13, respectively. The rear end portion 11c (hereinafter, also simply referred to as an end portion) has a minimum thickness, that is, the central portion 1
While the thickness of 1a is sufficiently secured, the thickness is gradually reduced as the distance from the central portion 11a increases in the passing direction 14. Further, in the fin 11, as shown in FIG. 2B, the thickness of the central portion 11a is set to d.
1, and the thickness of the end portions 11b and 11c is d2, the ratio of the two is defined to satisfy the following relationship. d2 / d
1 <0.5

The pipes 12 have a cylindrical shape and are arranged in rows so as to be arranged in a direction orthogonal to the air flow passage direction 14. A refrigerant R such as CFC flows inside the pipe 12. Thereby, in the heat exchanger, via the fin 11 or the pipe 12,
Heat exchange is performed between the refrigerant R and the air flow.

In such a heat exchanger, the fins 1
As shown in FIG. 2A, the temperature distribution of No. 1 is the isothermal line 1
5 becomes substantially equidistant. As a result, this fin 11
It has a gentle temperature gradient. The principle of obtaining a gentle temperature gradient in this way will be described below.

FIG. 3 is for explaining the heat radiation path of the refrigerant in the pipe. (A) is an enlarged sectional view showing a part of a conventional heat exchanger in an enlarged manner, and (b) is an implementation. FIG. 3 is an enlarged cross-sectional view showing a part of the heat exchanger according to Embodiment 1 in an enlarged manner, and (c) is a graph showing a fin temperature distribution in the cases of (a) and (b). In FIG. 3A, the thickness of the fin is uniform over the entire area, and the thickness L thereof is defined to satisfy the following formula. L = (d1
+ D2) / 2 Therefore, in the case of (a) and the case of (b), the average value of the thickness of the fin is substantially the same. Also, FIG.
The arrows in (a) and (b) indicate the heat paths of the refrigerant,
The thickness indicates the amount of heat.

In the heat exchanger according to the first embodiment, as shown in FIG. 3B, the central portion 11 of the fin 11 is formed.
Since the thickness of a is sufficiently large, the cross-sectional area of the central portion 11a is also large, and the amount of heat flowing through the fins 11 can be sufficiently secured. As a result, the fin efficiency of the fins 11 is sufficiently large. be able to. Therefore, the fins 11 as a whole have a gentle temperature gradient (FIG. 3 (c)), and the passages 1 are also formed at the ends 11b and 11c.
Since a sufficient temperature difference from the air flow of No. 3 can be secured, the amount of heat radiated to the air flow becomes sufficiently large. Moreover, the thickness of the fin 11 varies from the central portion 11a to the end portion 11b,
Since it is gradually decreasing toward 11c,
The material cost of the fin 11 does not increase.

On the other hand, in the conventional heat exchanger, since the thickness of the central portion is smaller than that of the heat exchanger according to the first embodiment, the sectional area of the central portion does not have a sufficient size, Therefore, a sufficient amount of heat flowing through the fin cannot be secured, and the amount of heat sharply decreases from the central portion to the end portion of the fin. As a result, the entire fin has a sharp temperature gradient (see FIG. 3 (c)). Therefore, the fin cannot secure a temperature difference from the airflow, the amount of heat radiation to the airflow is small, and a sufficiently large effective heat radiation area cannot be obtained.

FIG. 4 is an explanatory diagram showing a heat flow between adjacent pipes of the heat exchanger according to the first embodiment. In addition, the code | symbol 16 in FIG. 4 shows the flow of heat.

Since the thickness of the fin 11 varies along the air flow passage direction 14 centering on the central portion 11a,
The central region 11d between the adjacent pipes 12 has a large thickness. As a result, since the central region 11d has the same thickness as the central portion 11a, the cross-sectional area is sufficiently large, and the heat of the refrigerant R in the pipe 12 can be sufficiently obtained. As a result, it has a temperature close to the temperature of the refrigerant R. Therefore, the respective isothermal lines 15 of the fins 11 are formed in a direction substantially orthogonal to the passing direction 14 of the air flow, though they partially overlap with the case of FIG. That is, most of the heat from the refrigerant R
After reaching the central area 11d from the mounting point, the end 11
It spreads toward b and 11c.

FIG. 5 is an explanatory view schematically showing a rolling step which is a part of a manufacturing step of the fins constituting the heat exchanger according to the first embodiment. In the fin material rolling step, a multi-stage rolling process is performed. It shows that a rolling roller consisting of is used. In this rolling process, the circular rolling roller 17 and the elliptical rolling roller 1 located at the subsequent stage of the circular rolling roller 17
8 and are used.

The circular rolling roller 17 is composed of the fin material 110.
The purpose is to roll so that the thickness becomes d1. The elliptical rolling roller 18 is intended to roll the fin material 110 having a thickness of d1 so that a part of the fin material 110 has a thickness of d2.

In the rolling process, the thickness of the fin material 110 being conveyed is d by the circular rolling roller 17.
Rolled to 1. Fin material 110 having a thickness of d1
Is further rolled by the elliptical rolling roller 18 and has a shape having a region having a thickness of d2 periodically.

Then, an insertion hole (not shown) for inserting the pipe is formed in a region where the fin material 110 has a large thickness, that is, a region where the thickness is d1, and the pipe is inserted to expand the pipe. Thus, the heat exchanger can be manufactured by fixing the fin and the pipe. In the illustrated example, the post-rolling roller has an elliptical cross-sectional shape, but by changing this shape arbitrarily, the ratio of the thicker region and the thinner region can be adjusted appropriately.

According to the heat exchanger according to the first embodiment having the above-mentioned structure, a sufficiently large fin efficiency can be obtained without increasing the material cost.
A sufficient temperature difference between the fin 11 and the airflow can be secured, and a sufficiently large effective heat dissipation area can be obtained.
Further, since the temperature close to the temperature of the refrigerant R in the pipes 12 can be maintained in the central region 11d between the adjacent pipes 12, the interval between the adjacent pipes 12 can be expanded. Therefore, as a result of being able to reduce the number of pipes 12, the cost can be reduced.

Embodiment 2. FIG. 6 shows Embodiment 2 of the heat exchanger according to the present invention, and (a)
Is an enlarged plan view of the heat exchanger, (b) is C- in (a)
It is a C line sectional view. In the following description, configurations that are the same as or equivalent to the configurations described in the above-described first embodiment will be assigned the same reference numerals and redundant description will be omitted.

In FIG. 6, the heat exchanger comprises a plurality of plate-like fins 21 laminated in parallel with each other, and these fins 2.
1 and the pipe 12 penetrated in a state orthogonal to each other. A passage 13 is provided between the adjacent fins 21 for the airflow to pass therethrough.
This air flow passes in the direction indicated by reference numeral 14.

The fin 21 is, as shown in FIG.
The thickness thereof changes along the air flow passage direction 14.
More specifically, the fin 21 has a maximum thickness in the vicinity (hereinafter also referred to as a central portion) 21a where the pipe 12 is mounted, and the front end portion 21b corresponding to each of the upstream side and the downstream side of the passage 13 is formed. The thickness is gradually reduced toward the rear end portion 21c (hereinafter, also simply referred to as an end portion). The thickness of the front end portion 21b of the fin 21 is larger than the thickness of the rear end portion 21c.

In the heat exchanger having such a structure, since the thickness of the front end portion 21b is larger than the thickness of the rear end portion 21c, the cross sectional area becomes large. As a result, the amount of heat flowing through the fins 21 is larger than that of the rear end portion 21c.
As a result of the increase in 1b, the temperature of the front end portion 21b becomes higher than the temperature of the rear end portion 21c. That is, the front end 2
1b has a temperature closer to that of the refrigerant R. As a result, the isothermal line 15 shown in FIG. 6A is obtained. Therefore, the heat exchanger according to the second embodiment is
The following operational effects can be achieved.

When the air velocity is low, the passage 1
The temperature change of the air flow in 3 cannot be ignored.
That is, the airflow in the passage 13 is the front end portion 21 of the fin 21.
As a result of performing heat exchange near b and further heat exchange near the central portion 21a, the temperature is close to that of the refrigerant R when passing near the rear end portion 21c. Therefore, in the rear end portion 21c, the amount of heat exchange with the airflow becomes small.

Therefore, according to the heat exchanger of the second embodiment, a sufficient temperature difference between the fin 21 and the airflow can be ensured at the front end portion 21b of the fin 21, so that the amount of heat radiated to the airflow is also sufficiently large. As a result, good heat exchange can be performed, and as a result, the heat exchange capacity can be improved. On the other hand, the rear end portion 21c of the fin 21 is easily affected by the temperature of the air flow because of its small thickness, but since the air flow is heat-exchanged and has a sufficiently high temperature, the temperature of the air flow cannot be lowered. Absent.

Embodiment 3. FIG. 7 shows Embodiment 3 of the heat exchanger according to the present invention, and (a)
Is an enlarged plan view of the heat exchanger, (b) is D- in (a)
It is a D line sectional view. In the description below, configurations that are the same as or equivalent to the configurations described in the first and second embodiments will be assigned the same reference numerals and redundant description will be omitted. In addition, the code | symbol 34 in FIG.7 (a) shows the flow of heat.

In FIG. 7, the heat exchanger comprises a plurality of plate-like fins 31 laminated in parallel with each other and these fins 3.
1 and the pipe 12 penetrated in a state orthogonal to each other. A passage 13 is provided between the adjacent fins 31 for the airflow to pass therethrough.
This air flow passes in the direction indicated by reference numeral 14.

The fin 31 is, as shown in FIG.
The thickness changes along a direction substantially orthogonal to the air flow passage direction 14. More specifically, the fins 31 are
A region (hereinafter, also referred to as a pipe mounting region) 32 having a portion 31a where the pipe 12 is mounted, and a pipe-side front end portion 31b and a pipe-side rear end portion 31c (hereinafter, also simply referred to as pipe-side end portions) corresponding to the portion 31a Secure enough thickness of
In a region 33 between adjacent pipes 12 (hereinafter, also referred to as a pipe-to-pipe region), the thickness is gradually reduced to a middle portion of the pipe-to-pipe region 33 along a center line connecting the pipes 12.

In the heat exchanger having such a structure, since the thickness of the pipe mounting region 32 is sufficiently secured, the heat of the refrigerant R in the pipe 12 is transferred to the pipe mounting region 32. After that, the heat diffuses in a direction substantially orthogonal to the passing direction 14 of the air flow (reference numeral 34).
reference). And, finally, it is used for heat exchange with the air flow, so that heat is radiated. As a result, FIG.
The isotherm 35 shown therein is obtained.

As described above, in the heat exchanger according to the third embodiment, since the thickness of the pipe mounting region 32 is sufficiently large,
The cross-sectional area of the pipe mounting region 32 is also sufficiently large, and the amount of heat flowing through the fin 31 can be sufficiently secured. As a result, the fin efficiency of the fin 31 can be sufficiently large. Therefore, the temperature difference between the fin 31 and the airflow can be sufficiently secured, and the amount of heat radiated to the airflow can be sufficiently large. Moreover, fin 3
In the inter-pipe region 33, the thickness of No. 1 gradually changes to the middle portion of the inter-pipe region 33, so that the material cost of the fin 31 does not increase.

Therefore, according to the heat exchanger according to the third embodiment, a sufficiently large fin efficiency can be obtained without increasing the material cost, so that a sufficient temperature difference between the fin 31 and the airflow can be secured. Therefore, a sufficiently large effective heat dissipation area can be obtained. Further, the number of pipes 12 arranged along the air flow passage direction 14 can be reduced, and as a result, the cost can be reduced.

Fourth Embodiment FIG. 8 shows Embodiment 4 of the heat exchanger according to the present invention, (a)
Is an enlarged plan view of the heat exchanger, (b) is E- in (a)
It is an E line sectional view. In the following description, configurations that are the same as or equivalent to the configurations described in the first to third embodiments will be assigned the same reference numerals and redundant description will be omitted.

In FIG. 8, the heat exchanger comprises a plurality of plate-like fins 41 laminated in parallel with each other, and these fins 4
1 and the pipe 12 penetrated in a state orthogonal to each other. A passage 13 is provided between the adjacent fins 41 for the airflow to pass therethrough.
This air flow passes in the direction indicated by reference numeral 14.

The fin 41 is, as shown in FIG.
The thickness changes along a direction substantially orthogonal to the air flow passage direction 14. More specifically, the fin 41 is
A region (hereinafter also referred to as a pipe mounting region) 42 having a portion 41a where the pipe 12 is mounted, and a pipe-side front end portion 41b and a pipe-side rear end portion 41c (hereinafter, also simply referred to as pipe-side end portions) corresponding thereto 42 Has the maximum thickness, and in the region 43 between adjacent pipes 12 (hereinafter also referred to as the inter-pipe region) 43, the thickness gradually decreases along the center line connecting the pipes 12 to the middle portion of the inter-pipe region 43. Has been formed.

Further, the fin 41 has an inter-pipe region 43.
In, a plurality of cut-and-raised parts 50 are provided by, for example, press working. Cut and raised part 5 of each
No. 0 is provided such that its front edge portion 51 faces the air flow passage direction 14, and its leg portion 52 is connected to the pipe mounting portion 41a and its vicinity. Therefore, in each of the cut-and-raised parts 50, the thickness of the front edge part 51 is equal to the thickness of the inter-pipe region 43, and the thickness of the leg part 52 is close to the thickness of the pipe mounting region 42. 52
The thickness gradually decreases from the front edge portion 51 to the front edge portion 51.

In the heat exchanger having such a structure, the cut-and-raised portion 50 has a front edge portion 51 having a small thickness and a leg portion 52 having a large thickness, so that heat is diffused throughout the cut-and-raised portion 50. Easier to do.

Therefore, according to the heat exchanger according to the fourth embodiment, heat is easily diffused sufficiently in the cut-and-raised portion 50, so that a sufficient temperature difference between the cut-and-raised portion 50 and the air flow should be ensured. As a result, the heat exchange capacity between the refrigerant R and the air flow can be made sufficiently high. Also,
In the fin 41, the cut-and-raised part 50 secures a sufficient temperature difference from the airflow even in the inter-pipe region 43 where the surface temperature is the lowest, so that a sufficiently large effective heat dissipation area can be obtained. Therefore, the cost can be reduced by reducing the number of pipes as the heat exchange capacity is improved.

Further, in the fourth embodiment, as shown in FIG. 9, at least one of the cut-and-raised portions 50a may have its leg portion 52a connected to the pipe mounting region 42. Even with such a configuration, the same operational effects as described above can be obtained. Further, as shown in FIG. 10, two cut-and-raised parts 50b and 50c are provided side by side in a direction orthogonal to the air flow passage direction 14, and the leg portions 5 of the respective cut-and-raised parts 50b and 50c are provided.
One of 2b and 52c may be connected to the pipe mounting area 42. Even if such a configuration is adopted, the heat from the refrigerant R is likely to diffuse to the entire cut-and-raised parts 50b and 50c, and the same effect as the above can be obtained.

[0055]

As described above, according to the present invention, the thickness of the fins gradually decreases in at least one direction as the distance from the pipe mounting location increases, so that the thickness in the vicinity of the pipe mounting location is sufficient. Even if it is ensured, the cost of material of the fin does not increase. When a sufficient thickness near the pipe mounting portion is secured, a sufficiently large fin efficiency can be obtained, and a sufficient temperature difference between the fin and the airflow can be secured. It is possible to obtain a large heat dissipation area.
Therefore, the number of pipes can be reduced and the cost can be reduced while maintaining the heat exchange capacity.

Further, according to the following invention, since the thickness of the fins becomes gradually smaller along the passage direction of the air flow, as the distance from the pipe mounting portion increases, the fins are thicker than the pipe mounting portion. Even if a sufficient thickness is secured in the region in the substantially orthogonal direction, the material cost of the fin does not increase. When a sufficient thickness of the region is secured, a sufficiently large fin efficiency can be obtained and a sufficient temperature difference between the fin and the airflow can be secured, so that a sufficiently large effective heat dissipation area can be obtained. Can be obtained. Therefore, the number of pipes can be reduced and the cost can be reduced while maintaining the heat exchange capacity. In particular, when a sufficient thickness is secured in a region in a direction substantially orthogonal to the passage direction of the air flow centering on the pipe mounting location, a sufficient amount of heat flowing through the fins can be secured, resulting in that region. A temperature close to the temperature of the refrigerant in the pipe can be maintained. Therefore, it is possible to reduce the number of pipes arranged in the direction substantially orthogonal to the passage direction of the airflow, and thereby reduce the cost.

Further, according to the following invention, the thickness of the fins becomes gradually smaller as the distance from the pipe mounting portion increases along the direction substantially orthogonal to the passage direction of the air flow.
Even when a sufficient thickness is secured in the region along the passage direction of the air flow centering on the pipe mounting portion, the material cost of the fin does not increase. When a sufficient thickness of the region is secured, a sufficiently large fin efficiency can be obtained and a sufficient temperature difference between the fin and the airflow can be secured, so that a sufficiently large effective heat dissipation area can be obtained. Can be obtained. Therefore, the number of pipes can be reduced and the cost can be reduced while maintaining the heat exchange capacity. In particular, when a sufficient thickness is secured in the area along the air flow passage centering on the pipe mounting location,
As a result of being able to secure a sufficient amount of heat flowing through the fins, a temperature close to the temperature of the refrigerant in the pipe can be maintained in this region. Therefore, it is possible to reduce the number of pipes arranged along the passage direction of the airflow, and thereby reduce the cost.

Further, according to the next invention, since the cut-and-raised portion is provided so that its front edge portion faces the air flow passage direction, heat exchange is also performed through the cut-and-raised portion. Therefore, the heat exchange capacity between the refrigerant in the pipe and the air flow can be made sufficiently high.

Further, according to the next invention, since at least one of the leg portions of the cut-and-raised portion is connected to the vicinity of the mounting location of the pipe, the thickness of the leg portion becomes large. Therefore, it is possible to receive the heat supply from the part where the thickness of the fin is large,
As a result, heat is sufficiently diffused throughout the cut and raised portion,
As a result, the heat exchange capacity between the refrigerant in the pipe and the air flow can be made sufficiently higher.

[Brief description of drawings]

FIG. 1 shows a heat exchanger according to a first embodiment of the present invention, in which (a) is a plan view of the heat exchanger,
(B) is the sectional view on the AA line in (a).

FIG. 2 shows a heat exchanger according to the first embodiment of the present invention, (a) is an enlarged plan view showing a temperature distribution of the heat exchanger, (b) is a BB line in (a). It is a line sectional view.

3A and 3B are diagrams for explaining a heat radiation path of a refrigerant in a pipe, FIG. 3A is an enlarged sectional view showing a part of a conventional heat exchanger in an enlarged manner, and FIG. 3B is a first embodiment. The expanded sectional view which expanded and showed a part of heat exchanger in FIG.
[Fig. 3] is a graph showing the temperature distribution of fins in the cases of (a) and (b).

FIG. 4 is an explanatory diagram showing a heat flow between adjacent pipes of the heat exchanger according to the first embodiment of the present invention.

FIG. 5 is an explanatory view schematically showing a rolling process which is a part of a manufacturing process of fins constituting the heat exchanger according to the first embodiment of the present invention.

FIG. 6 shows a heat exchanger according to a second embodiment of the present invention, (a) is an enlarged plan view of the heat exchanger,
(B) is the CC sectional view taken on the line in (a).

FIG. 7 shows a heat exchanger according to a third embodiment of the present invention, (a) is an enlarged plan view of the heat exchanger,
(B) is the DD sectional view taken on the line in (a).

FIG. 8 shows a heat exchanger according to a fourth embodiment of the present invention, (a) is an enlarged plan view of the heat exchanger,
(B) is the EE sectional view taken on the line in (a).

9A and 9B are views showing a modification of the heat exchanger according to the fourth embodiment of the present invention, in which FIG. 9A is an enlarged plan view of the heat exchanger, and FIG. 9B is a sectional view taken along line FF in FIG. 9A. It is a figure.

FIG. 10 shows a modified example of the heat exchanger according to the fourth embodiment of the present invention, (a) is an enlarged plan view of the heat exchanger, (b) is a cross section taken along line GG in (a). It is a figure.

11A and 11B show a conventional heat exchanger, in which FIG. 11A is a plan view and FIG. 11B is a sectional view taken along line XX in FIG.

12A and 12B show a conventional heat exchanger, in which FIG. 12A is a plan view and FIG. 12B is a sectional view taken along line YY in FIG.

FIG. 13 is an enlarged plan view showing a temperature distribution of a conventional heat exchanger.

[Explanation of symbols]

11 fins, 11a central part, 11b front end part, 11
c rear end portion, 11d central region, 12 pipes, 13 passages, 14 passage direction, 15 isothermal lines, 16 heat flow,
17 circular rolling roller, 18 oval rolling roller, 21
Fin, 21a central part, 21b front end part, 21c
Rear end part, 31 fins, 31a pipe mounting part, 31
b pipe-side front end portion, 31c pipe-side rear end portion, 32
Pipe mounting area, 33 inter-pipe area, 34 heat flow, 41 fins, 41a pipe mounting location, 41b
Pipe-side front end portion, 41c Pipe-side rear end portion, 42 Pipe mounting area, 43 Pipe-to-pipe area, 50 Cut and raised portion, 51 Front edge portion, 52 Leg portion, 50a Cut and raised portion,
50b Cut-and-raised part, 52a Leg part, 52b Leg part, 5
2c leg, 110 fin material.

   ─────────────────────────────────────────────────── ─── Continued front page    (72) Inventor Shinji Nakajima             2-3 2-3 Marunouchi, Chiyoda-ku, Tokyo             Inside Ryo Electric Co., Ltd. (72) Inventor Katsuhisa Otatsu             2-3 2-3 Marunouchi, Chiyoda-ku, Tokyo             Inside Ryo Electric Co., Ltd. (72) Inventor Shoji Yamada             2-3 2-3 Marunouchi, Chiyoda-ku, Tokyo             Inside Ryo Electric Co., Ltd.

Claims (5)

[Claims] 1. A plate-shaped fin and a pipe penetrating the fin are provided, and heat exchange is performed between a refrigerant flowing in the pipe and an air stream passing along an extending direction of the fin. The heat exchanger according to claim 1, wherein the fins change in thickness along at least one direction such that the thickness of the fins gradually decreases as the fins move away from the pipe mounting portion. 2. The heat exchanger according to claim 1, wherein the fins have a thickness that varies along a passage direction of the air flow. 3. The heat exchanger according to claim 1, wherein the fins have a thickness that varies along a direction substantially orthogonal to a passage direction of the air flow. 4. A plurality of pipes are arranged so as to be aligned in a direction orthogonal to the air flow passage direction, and a front edge portion facing the air flow passage direction is provided at a portion of the fin located between the pipes. The heat exchanger according to claim 3, further comprising a cut-and-raised part having the cut-and-raised part. 5. The heat exchanger according to claim 4, wherein at least one of the legs of the cut-and-raised portion is connected to the vicinity of a pipe mounting location.