KR20060012303A - Heat exchanger fin, heat exchanger, condensers, and evaporators - Google Patents

Abstract

This invention provides a heat exchanger fin capable of improving heat transfer rate while preventing generation of heat bypass flow. The invention relates to a heat exchanger fin such as a louver fin 4 provided with a plurality louvers 5 arranged at certain intervals in the introduction direction X of air A, the louvers being formed by cutting and bending the heat exchanger fin so that the air A is passed while being guided by the louvers 5. The plurality of louvers 5 include louvers different in louver width, the louver width being defined by a length of the louver along which the heat medium passes, and the wide louver and the narrow louver are arranged alternatively.

Description

Fins for heat exchangers, heat exchangers, condensers, and evaporators {HEAT EXCHANGER FIN, HEAT EXCHANGER, CONDENSERS, AND EVAPORATORS}

This application takes precedence over Japanese Patent Application No. 2003-140400 filed May 19, 2003 and US Provisional Application No. 60 / 478,360, filed June 16, 2003, the entire disclosure of which is incorporated herein by reference. Insist.

Related Applications

This application is directed to US 35 U.S.C. 35 U.S.C. of the date of filing of US Provisional Application No. 60 / 478,360, filed June 16, 2003, filed under § 111 (b). 35 U.S.C. Claiming Benefits Under §119 (e) (1) Corresponds to US application filed under § 111 (a).

The present invention relates to a heat exchanger such as a condenser or an evaporator for a vehicle air conditioner used in a refrigeration cycle for a vehicle air conditioner, for example, as a vehicle air-conditioning device, and also includes louver fins provided in these devices. Or fins for use in heat exchangers, such as corrugated fins (hereinafter referred to as "fins for heat exchangers").

A heat exchanger such as an evaporator or a condenser used in a refrigeration cycle for a vehicle air conditioner includes a heat exchanger tube through which refrigerant passes, and a heat exchanger fin disposed perpendicularly to the longitudinal direction of the heat exchange tube, and thus, through the fin, Heat exchange takes place between the refrigerant passing through the heat exchange tubes.

As heat exchanger fins, louver fins, offset fins, pin fins and the like are generally used depending on the use and / or required performance.

In the heat exchanger of the louver fin form among heat exchangers, as shown in FIG. 11, the some louver fin 50 arrange | positioned in parallel with the introduction direction X of air A has the air introduction direction X. As shown in FIG. They are arranged in parallel at predetermined intervals in the direction orthogonal to each other, and thus an air passage 60 is formed between adjacent louver pins 50. Each louver pin 50 is provided with a plurality of cut-and-bent louvers 51 arranged in the longitudinal direction (air introduction direction) of the air passage 60. Air A introduced into the air passage 60 passes through louver gaps respectively formed along the louvers 51 between adjacent louvers 51 of each louver fin 50, thus exchanging heat with air A. Heat exchange occurs between the refrigerant passing through the tube (not shown).

One way to improve the thermal performance in such a heat exchanger is to reduce the pitch of the louver 51 to increase the number of louvers 51, whereby the windward side edges of the louver 51 and the air Increasing the contact area between (A) can be considered effective.

However, if the louver pitch is made small, sand clogging and / or bridging of condensed water between adjacent louvers 51 causes air A to pass through the air passage 60 to the adjacent louvers 51. Prevents entry into each of the louver gaps formed in between. This results in a so-called bypass flow of air A, through which the air does not enter the louver gap but passes through each fin space formed between adjacent louver fins 50, resulting in a lowered heat transfer rate.

On the other hand, in a louver fin type heat exchanger, Japanese Patent Laid-Open Nos. H6-221787 (FIGS. 1 and 3) and US Pat. No. 5,702,14 disclose a technique for improving heat exchange performance by changing the angle of the louver. .

In addition, Japanese Patent Laid-Open No. H1-263498 (page 1-2) discloses a technique for defining an optimum value of pin pitch, pin thickness, louver pitch, and louver angle.

However, in the recent technical field of heat exchanger, especially the technical field of heat exchanger for vehicle air conditioner, improvement of heat exchange performance is desired further. Therefore, it is desired to further improve the heat transfer rate of the heat exchanger fins.

An object of the present invention is to provide a heat exchanger such as a condenser or an evaporator for a vehicle air conditioner having improved heat transfer rate and thus excellent heat exchange performance.

Another object of the present invention is to provide fins for heat exchangers such as louver fins and corrugated fins to be provided in the heat exchanger.

In order to achieve the above object, the present invention has the following configuration.

(1) a heat transfer plate disposed parallel to the heat medium introduction direction and provided with a plurality of louvers at predetermined intervals in the heat medium introduction direction, wherein the plurality of louvers are formed by cutting and bending the heat transfer plate so that the heat medium Fins for heat exchangers that are guided by a plurality of louvers and distributed.

The plurality of louvers includes a plurality of types of louvers having different louver widths, and the louver widths are defined by the lengths of the louvers in a direction in which the heat medium flows.

The plurality of types of louvers having different louver widths are arranged in a mixed arrangement along the heat medium introduction direction.

(2) The fin for a heat exchanger according to (1), wherein the plurality of louvers include a wide louver wide louver and a narrow louver narrow louver, and the wide louvers and the narrow louvers are arranged in a mixed arrangement.

(3) The fin for heat exchanger according to (2), wherein one or more of the wide louvers and one or more of the narrow louvers are alternately disposed.

(4) The fin for heat exchangers according to (2), wherein the wide louver and the narrow louver are alternately arranged.

In the above inventions (2) to (4), since two kinds of louvers are employed, the heat transfer rate can be further improved without complicating the structure.

(5) The louver width of the wide louver as described in any one of (2) to (4) above when the louver width of the wide louver and the louver width of the narrow louver are represented by "Lwl" and "Lws", respectively. Fin for the heat exchanger in which the ratio "Lws / Lwl" of the narrow louver width "Lws" to "Lws" is set to 0.1 to 0.7.

(6) The fin for a heat exchanger according to any one of (1) to (5), wherein the angle (louver angle) of the louver with respect to the heat transfer plate is set to 22 to 36 °.

In the inventions of (5) and (6), the heat transfer rate can be further improved.

(7) The heat exchanger according to any one of (1) to (6), wherein the heat transfer plates are arranged in plural in parallel at predetermined intervals in a direction orthogonal to the heat medium introduction direction so that an air passage is formed between adjacent heat transfer plates. pin.

As can be seen from (7) above, the present invention can be preferably employed as a corrugated pin and plate pin.

(8) The fin for heat exchangers according to (7), wherein a fin pitch defined by an interval between adjacent heat transfer plates is set to 1 to 2 mm.

In the invention of (8), the heat transfer rate can be further improved.

(9) In the above (7) or (8), when the pin pitch defined by the interval between adjacent heat transfer plates is represented by "Fp" and the louver width of the louver having the largest louver width is represented by "Lwmax", And a ratio "Fp / Lwmax" of the fin pitch "Fp" to the louver width "Lwmax" is set to 1 or more.

In the invention of (9), the heat transfer rate can be further improved.

(10) The heat transfer plate according to any one of (1) to (9), wherein the heat transfer plate is provided such that heat exchange occurs between air as a heat medium passing between the pair of heat exchange tubes and a refrigerant passing through the heat exchange tube. Fins for heat exchangers disposed between a pair of heat exchange tubes arranged in parallel at intervals of.

As can be seen from the above (10), the present invention can be preferably employed in a tubular heat exchanger.

(11) The heat exchanger fin according to the above (10), wherein the refrigerant is configured to condense by heat exchange with air.

As can be seen from (11) above, the present invention can be preferably employed in a condenser.

(12) The fin for heat exchangers according to (10), wherein the refrigerant is configured to evaporate by heat exchange with air.

As can be seen from (12) above, the present invention can be preferably employed in an evaporator.

The preferable structure as described in said (2)-(12) can be preferably employ | adopted also in the structure of the following (13)-(30).

(13) a heat transfer plate disposed parallel to the heat medium introduction direction and provided with a plurality of louvers at predetermined intervals in the heat medium introduction direction, wherein the plurality of louvers are formed by cutting and bending the heat transfer plate so that the heat medium It is a louver pin distributed while being guided by a plurality of louvers,

The plurality of louvers includes a plurality of types of louvers having different louver widths, and the louver widths are defined by the lengths of the louvers in a direction in which the heat medium flows.

The plurality of types of louvers having different louver widths are arranged in a mixed arrangement along the heating medium introduction direction.

In the louver fin according to the present invention, as in the above, a heat medium such as air reliably flows between the louvers, smoothly flows along each louver, and prevents the occurrence of bypass flow, thereby improving heat transfer rate.

(14) a plurality of heat transfer plates arranged parallel to the heat medium introduction direction and arranged in parallel at a predetermined interval in a direction orthogonal to the heat medium introduction direction, wherein adjacent heat transfer plates are interconnected, and each of the plurality of heat transfer plates Silver is provided with a plurality of louvers disposed at predetermined intervals in the heat medium introduction direction, the plurality of louvers are formed by cutting and bending of the heat transfer plate is a corrugated fin that is flowed while being guided by the plurality of louvers,

The plurality of louvers includes a plurality of types of louvers having different louver widths, and the louver widths are defined by the lengths of the louvers in a direction in which the heat medium flows.

The plurality of types of louvers having different louver widths are corrugated pins arranged in a mixed arrangement.

In the corrugated fin according to the present invention, as in the above, a heat medium such as air reliably flows between the louvers, smoothly flows along each louver, and prevents the occurrence of bypass flow, thereby improving heat transfer rate.

(15) a plurality of heat exchanger fins arranged in parallel to the air introduction direction and arranged in parallel at a predetermined interval in a direction orthogonal to the air introduction direction, and a refrigerant passage through which the refrigerant passes, wherein the plurality of heat exchanger plates Each includes a plurality of louvers arranged at predetermined intervals in the air introduction direction, and the plurality of louvers are formed by cutting and bending the fins for the heat exchanger, whereby air is guided by the plurality of louvers to distribute air and refrigerant. It is a heat exchanger in which heat exchange is performed between

The plurality of louvers includes a plurality of types of louvers having different louver widths, and the louver widths are defined by the lengths of the louvers in a direction in which the heat medium flows.

The plurality of types of louvers having different louver widths are arranged in a mixed arrangement.

In the heat exchanger according to the present invention, as in the above, a heat medium such as air reliably flows between the louvers, smoothly flows along each louver, and prevents the occurrence of bypass flow, thereby improving heat transfer rate.

(16) a pair of heat exchange tubes arranged in parallel at predetermined intervals, and a plurality of fins for heat exchangers each disposed in parallel with respect to the air introduction direction and arranged in parallel with each other in a predetermined interval in a direction orthogonal to the air introduction direction. And each of the plurality of heat exchanger fins includes a plurality of louvers disposed at predetermined intervals in an air introduction direction, and the plurality of louvers are formed by cutting and bending the heat exchanger fins so that air is supplied to the plurality of louvers. Is a heat exchanger that is guided by the circulation and heat exchange between the air and the refrigerant,

The plurality of louvers includes a plurality of types of louvers having different louver widths, and the louver widths are defined by lengths of the louvers in a direction in which air flows.

The plurality of types of louvers having different louver widths are arranged in a mixed arrangement.

In the heat exchanger according to the present invention, as in the above, a heat medium such as air reliably flows between the louvers, smoothly flows along each louver, and prevents the occurrence of bypass flow, thereby improving heat transfer rate.

(17) The method of (15) or (16), wherein the plurality of louvers include a wide louver wide louver and a narrow louver narrow louver, wherein the wide louvers and the narrow louvers are arranged in a mixed arrangement. heat transmitter.

In the invention of (17), as in the above, the heat transfer rate can be further improved.

(18) The heat exchanger according to (15) or (16), wherein adjacent fins of the plurality of heat exchanger fins are connected to each other.

As can be seen from the above (18), the present invention can be preferably employed in a pleated heat exchanger.

(19) a plurality of heat exchanger fins arranged in parallel to the air introduction direction and arranged in parallel at a predetermined interval in a direction orthogonal to the air introduction direction, and a refrigerant passage through which the refrigerant passes, wherein the plurality of heat exchanger plates Each includes a plurality of louvers arranged at predetermined intervals in the air introduction direction, and the plurality of louvers are formed by cutting and bending the fins for the heat exchanger, whereby air is guided by the plurality of louvers to distribute air and refrigerant. It is a condenser in which refrigerant is condensed by heat exchange between

The plurality of louvers includes a plurality of types of louvers having different louver widths, and the louver widths are defined by the lengths of the louvers in a direction in which the heat medium flows.

And the plurality of louvers having different louver widths are arranged in a mixed arrangement.

In the condenser according to the present invention, as described above, a heat medium such as air reliably flows between the louvers, smoothly flows along each louver, and prevents the occurrence of bypass flow, thereby improving heat transfer rate.

(20) a pair of heat exchange tubes arranged in parallel at predetermined intervals, and a plurality of fins for heat exchangers each disposed in parallel with respect to the air introduction direction and arranged in parallel with each other in a predetermined interval in a direction orthogonal to the air introduction direction. And each of the plurality of heat exchanger fins includes a plurality of louvers disposed at predetermined intervals in an air introduction direction, and the plurality of louvers are formed by cutting and bending the heat exchanger fins so that air is supplied to the plurality of louvers. It is circulated while being guided by the condenser in which the refrigerant is condensed by heat exchange between the air and the refrigerant,

The plurality of louvers includes a plurality of types of louvers having different louver widths, and the louver widths are defined by lengths of the louvers in a direction in which air flows.

And the plurality of louvers having different louver widths are arranged in a mixed arrangement.

In the condenser according to the present invention, as described above, a heat medium such as air reliably flows between the louvers, smoothly flows along each louver, and prevents the occurrence of bypass flow, thereby improving heat transfer rate.

(21) The method according to (19) or (20), wherein the plurality of louvers include a wide louver wide louver and a narrow louver narrow louver, wherein the wide louvers and the narrow louvers are arranged in a mixed arrangement. Condenser.

In the invention of (21), as in the above, the heat transfer rate can be further improved.

(22) The condenser according to (19) or (20), wherein adjacent fins of the plurality of heat exchanger fins are connected to each other.

As can be seen from the above (22), the present invention can be preferably employed in a pleated heat exchanger.

(23) is a condenser used in refrigeration cycles for vehicle air conditioners,

A plurality of heat exchanger fins arranged in parallel with respect to the air introduction direction and arranged in parallel at a predetermined interval in a direction orthogonal to the air introduction direction, and

A refrigerant passage through which the refrigerant passes,

Each of the plurality of heat exchanger plates includes a plurality of louvers arranged at predetermined intervals in the air introduction direction, and the plurality of louvers are formed by cutting and bending of the heat exchanger fins so that air is guided by the plurality of louvers. As it is distributed, the refrigerant is condensed by heat exchange between air and refrigerant,

The plurality of louvers includes a plurality of types of louvers having different louver widths, and the louver widths are defined by the lengths of the louvers in a direction in which the heat medium flows.

And the plurality of louvers having different louver widths are arranged in a mixed arrangement.

In the condenser according to the present invention, as described above, a heat medium such as air reliably flows between the louvers, smoothly flows along each louver, and prevents the occurrence of bypass flow, thereby improving heat transfer rate.

(24) The condenser used for refrigeration cycles for vehicle air conditioners,

A pair of heat exchange tubes arranged in parallel at a predetermined interval, and

A plurality of heat exchanger fins disposed in parallel with respect to the air introduction direction and arranged in parallel with each other at predetermined intervals in a direction orthogonal to the air introduction direction,

Each of the plurality of heat exchanger fins includes a plurality of louvers disposed at predetermined intervals in the air introduction direction, and the plurality of louvers are formed by cutting and bending the heat exchanger fins so that air is guided by the plurality of louvers. As it is distributed, the refrigerant is condensed by heat exchange between air and refrigerant,

The plurality of louvers includes a plurality of types of louvers having different louver widths, and the louver widths are defined by lengths of the louvers in a direction in which air flows.

And the plurality of louvers having different louver widths are arranged in a mixed arrangement.

In the condenser according to the present invention, as described above, a heat medium such as air reliably flows between the louvers, smoothly flows along each louver, and prevents the occurrence of bypass flow, thereby improving heat transfer rate.

(25) a plurality of heat exchanger fins arranged in parallel to the air introduction direction and arranged in parallel at a predetermined interval in a direction orthogonal to the air introduction direction, and a refrigerant passage through which the refrigerant passes, wherein the plurality of heat exchanger plates Each includes a plurality of louvers arranged at predetermined intervals in the air introduction direction, and the plurality of louvers are formed by cutting and bending the fins for the heat exchanger, whereby air is guided by the plurality of louvers to distribute air and refrigerant. It is an evaporator in which refrigerant is evaporated by heat exchange between

The plurality of louvers includes a plurality of types of louvers having different louver widths, and the louver widths are defined by the lengths of the louvers in a direction in which the heat medium flows.

And said plurality of types of louvers having different louver widths are arranged in a mixed arrangement.

In the evaporator according to the present invention, as in the above, a heat medium such as air reliably flows between the louvers, smoothly flows along each louver, and prevents the occurrence of bypass flow, thereby improving heat transfer rate.

(26) a pair of heat exchange tubes arranged in parallel at predetermined intervals, and a plurality of heat exchanger fins arranged in parallel with respect to the air introduction direction and arranged in parallel at a predetermined interval in a direction perpendicular to the air introduction direction. And each of the plurality of heat exchanger fins includes a plurality of louvers disposed at predetermined intervals in an air introduction direction, and the plurality of louvers are formed by cutting and bending the heat exchanger fins so that air is supplied to the plurality of louvers. Is an evaporator that is distributed while being guided and evaporates the refrigerant by heat exchange between the air and the refrigerant,

The plurality of louvers includes a plurality of types of louvers having different louver widths, and the louver widths are defined by lengths of the louvers in a direction in which air flows.

And said plurality of types of louvers having different louver widths are arranged in a mixed arrangement.

In the evaporator according to the present invention, as in the above, a heat medium such as air reliably flows between the louvers, smoothly flows along each louver, and prevents the occurrence of bypass flow, thereby improving heat transfer rate.

(27) The method of (25) or (26), wherein the plurality of louvers include a wide louver wide louver and a narrow louver narrow louver, wherein the wide louvers and the narrow louvers are arranged in a mixed arrangement. evaporator.

In the invention of (27), as in the above, the heat transfer rate can be further improved.

(28) The evaporator according to (25) or (26), wherein adjacent fins of the plurality of heat exchanger fins are connected to each other.

As can be seen from the above (28), the present invention can be preferably employed in a pleated heat exchanger.

(29) Evaporator used in refrigeration cycles for vehicle air conditioners,

A plurality of heat exchanger fins arranged in parallel with respect to the air introduction direction and arranged in parallel at a predetermined interval in a direction orthogonal to the air introduction direction, and

A refrigerant passage through which the refrigerant passes,

Each of the plurality of heat exchanger plates includes a plurality of louvers arranged at predetermined intervals in the air introduction direction, and the plurality of louvers are formed by cutting and bending of the heat exchanger fins so that air is guided by the plurality of louvers. As it is distributed, the refrigerant is evaporated by heat exchange between air and refrigerant,

The plurality of louvers includes a plurality of types of louvers having different louver widths, and the louver widths are defined by the lengths of the louvers in a direction in which the heat medium flows.

And said plurality of types of louvers having different louver widths are arranged in a mixed arrangement.

In the evaporator according to the present invention, as in the above, a heat medium such as air reliably flows between the louvers, smoothly flows along each louver, and prevents the occurrence of bypass flow, thereby improving heat transfer rate.

(30) Evaporator used in refrigeration cycles for vehicle air conditioners,

A pair of heat exchange tubes arranged in parallel at a predetermined interval, and

A plurality of heat exchanger fins disposed in parallel with respect to the air introduction direction and arranged in parallel with each other at predetermined intervals in a direction orthogonal to the air introduction direction,

Each of the plurality of heat exchanger fins includes a plurality of louvers disposed at predetermined intervals in the air introduction direction, and the plurality of louvers are formed by cutting and bending the heat exchanger fins so that air is guided by the plurality of louvers. As it is distributed, the refrigerant is evaporated by heat exchange between air and refrigerant,

The plurality of louvers includes a plurality of types of louvers having different louver widths, and the louver widths are defined by lengths of the louvers in a direction in which air flows.

And said plurality of types of louvers having different louver widths are arranged in a mixed arrangement.

In the evaporator according to the present invention, as in the above, a heat medium such as air reliably flows between the louvers, smoothly flows along each louver, and prevents the occurrence of bypass flow, thereby improving heat transfer rate.

Other objects and advantages of the invention will appear more clearly from the following description.

BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a broken perspective view partially showing fins and their surroundings of a heat exchanger according to an embodiment of the invention.

FIG. 2 is an enlarged sectional view taken on the P-P line of FIG. 1, showing the louver pin of the embodiment. FIG.

3 is an enlarged cross-sectional view showing the fin portion of the heat exchanger according to the embodiment.

4A-4E are partial cross-sectional views of louver fins according to a variation of the invention.

5 is a graph showing the relationship between the front wind speed and heat transfer rate in the evaporator of Examples 1 to 5 and Comparative Example 1. FIG.

6 is a graph showing the relationship between front wind speed and heat transfer rate in the evaporators of Examples 6, 7 and Comparative Example 2. FIG.

7 is a graph showing the relationship between the louver angle and the heat transfer rate at the front wind speed of 1 m / s in the evaporators of Examples 8, 9 and Comparative Example 3. FIG.

FIG. 8 is a graph showing the relationship between the louver angle and the heat transfer rate at a front wind speed of 2 m / s in the evaporators of Examples 8, 9 and Comparative Example 3. FIG.

9 is a graph showing the relationship between the fin pitch and the heat transfer rate at the front wind speed of 1 m / s in the evaporators of Examples 9, 10 and Comparative Example 4. FIG.

10 is a graph showing the relationship between the fin pitch and the heat transfer rate at a front wind speed of 2 m / s in the evaporators of Examples 10, 11 and Comparative Example 4. FIG.

Fig. 11 is a sectional view showing a part of louver fin in a conventional heat exchanger.

1 is a broken perspective view partially showing fins of a heat exchanger such as an evaporator for a vehicle air conditioner according to an embodiment of the present invention and its periphery, and FIG. 2 is an enlarged sectional view showing louver fins applied to the heat exchanger of the embodiment. 3 is an enlarged cross-sectional view of the front portion of the fin of the heat exchanger according to the embodiment. In the following description, in order to facilitate understanding of the invention, it is assumed that the direction along the air introduction direction X to the heat exchanger of the present embodiment is assumed to be the front-rear direction of the heat exchanger.

As shown in these figures, in this heat exchanger, a plurality of flat heat exchange tubes 1 and 2 each extending in a direction orthogonal to the air introduction direction X (that is, up and down direction) are left and right directions of the heat exchanger. Thus, two rows are arranged in parallel with each other at predetermined intervals. Corrugated fins 3 are arranged between adjacent heat exchange tubes 1 and 2 arranged in the width direction of the heat exchanger.

The corrugated fin 3 includes a plurality of thin plate louver fins 4 as heat transfer plates which extend in the front-rear direction and are arranged at predetermined intervals in the vertical direction, and adjacent louver fins 4 are connected in a left-right alternating manner to meander. It has a meandering shape. Between adjacent louver fins 4 of the corrugated fins 3, air passages 6 extending in the front-rear direction are formed, so that during operation, air A as heat medium is introduced from each of the air passages from the front of the heat exchanger. Will be introduced in (6).

Each louver pin 4 is provided with a plurality of louvers 5 formed by cutting and bending a predetermined area at predetermined intervals in the front-rear direction. Thus, the air introduced into the air passage 6 is guided by the louvers 5 to louver gaps formed between adjacent louvers 5 respectively, and thus through the louver fins, air A and the heat exchange tube ( 1, 2) Heat exchange takes place between the refrigerant flowing through the inside.

In the present embodiment, when the louver length in the direction in which air flows is made the louver width, the plurality of louvers 5 at each louver pin 4 have a wide louver 5a with a wide louver width and a narrow louver width. A narrow louver 5b is provided, and the wide louver and the narrow louver are alternately arranged.

In the present embodiment, when the louver width of the wide louver 5a is expressed as "Lwl", it is preferable to set the width Lwl to 0.8 to 1.3 mm, and the lower limit is 0.85 mm or more and the upper limit is 1.2 mm or less. It is more preferable to set. In addition, when the louver width of the narrow louver 5b is represented by "Lws", it is preferable to set the said width Lws to 0.1-0.6 mm, and it is more preferable to set a lower limit to 0.15 mm or more.

If the louver widths Lwl and Lws are too narrow or too wide, the heat transfer rate of the louver fin 4 is lowered due to the generation of bypass flow of air or an increase in pressure loss, and as a result, the heat exchange performance is lowered.

In addition, in this embodiment, it is preferable to set the ratio Lws / Lwl of the louver width Lws of the narrow louver 5b to the louver width Lwl of the wide louver 5a to 0.1 to 0.7, and the lower limit value. Is more preferably set to 0.3 or more.

As is apparent from the embodiments to be described later, if the louver width ratio Lws / Lwl is too small or too large, the heat transfer rate is lowered due to the generation of bypass flow of air or an increase in pressure loss, and consequently, the heat exchange performance is lowered.

In addition, in this embodiment, the angle La of each louver 5 with respect to the louver fin 4 as a heat transfer plate is set substantially constant. It is preferable to set the louver angle La to 22-36 degrees, and it is more preferable to set a lower limit to 24 degrees or more, and an upper limit to 32 degrees or less, respectively.

If the louver angle La is too small or too large, the heat transfer rate of the louver fins is lowered due to the generation of bypass flow of air or an increase in pressure loss, and as a result, the heat exchange performance is lowered.

In addition, in this embodiment, it is preferable to set the space | interval between adjacent louver pins 4 and 4, ie, the pin pitch Fp, to 1-2 mm, and to set an upper limit to 1.6 mm or less. .

As is apparent from the embodiments described below, if the fin pitch Fp is too small or too large, the heat transfer rate of the louver fin is lowered due to the generation of bypass flow of air or an increase in pressure loss, and as a result, the heat exchange performance is lowered.

In the present embodiment, it is preferable to set the ratio Fp / Lwl of the pin pitch Fp to the louver width Lwl of the wide louver 5a to 1 or more. If this ratio is too small or too large, the heat transfer rate decreases due to the occurrence of bypass flow of air or an increase in pressure loss, and consequently, the heat exchange performance decreases.

In the present invention, when the plurality of louvers 5 are formed of three or more kinds of louvers having different widths, the ratio (Fp / Lwmax) of the pin pitch Fp to the widest louver width Lwmax is determined as described above. Similarly, setting to 1 or more is preferable.

In the heat exchanger of the present embodiment, since the plurality of louvers 5 of each louver fin 4 have a wide louver 5a and a narrow louver 5b which are alternately arranged, they are introduced into the air passage 6. Air A is guided by louvers 5 into louver gaps formed between adjacent louvers 5, so that they flow smoothly along each louver 5. This improves the heat transfer rate by preventing the generation of bypass flow of air A, and as a result, excellent heat exchange performance is obtained.

In the said embodiment, although the some louver 5 of each louver pin 4 is equipped with two types of louvers, the wide louver 5a and the narrow louver 5b which are alternately arrange | positioned, in this invention, louver The kind and arrangement method thereof are not limited to the above. For example, in a plurality of louvers, one or more wide louvers and one or more narrow louvers may be alternately arranged. In short, a plurality of louvers are included in the present invention as long as they are formed by mixing two or more kinds of louvers having different louver widths. For example, as shown in FIG. 4A, the wide louver 5a is arranged on the side where the wind blows, and the narrow louver 5b is arranged on the side where the wind blows, and as shown in FIG. 4B, between the wide louvers 5a. Arranging narrow louvers 5b, alternately arranging one or more wide louvers 5a and one or more narrow louvers 5b, as shown in Figs. 4C-4E, wide louvers 5a and narrow louvers 5b. ) Can be arranged at random.

In the above embodiment, the present invention has been described in the case where the present invention is applied to a heat exchanger such as an evaporator, but the present invention is not limited thereto, and the present invention can be similarly applied to a heat exchanger such as a condenser or a heater core. In addition, the present invention is not limited to a heat exchanger used in an automotive air conditioner, and may be used as a heat exchanger used in another refrigeration apparatus or a heater, such as a room air conditioner or a refrigerator.

In addition, in the above embodiment, the case where the present invention is applied to the corrugated fin has been described, but the present invention is not limited thereto, and the present invention can also be applied to plate fins and the like in which adjacent heat transfer fins are independently disposed.

Moreover, in the said Example, although the case where this invention was applied to the heat transfer fin by air was demonstrated, this invention is not limited to that, It can be applied also to the heat transfer fin by heat medium other than air.

EXAMPLE

EMBODIMENT OF THE INVENTION Below, the Example concerning this invention and the comparative example which depart from the summary of this invention are demonstrated.

Based on the said Example, the evaporator for vehicle air conditioners which arrange | positioned the corrugated fin with a plurality of types of louver between the several flat heat exchange tubes which adjoin each were examined.

<Examples 1 to 5>

Table 1

Lwl (mm) Lws (mm) Lws / Lwl Fp (mm) La (°) Example 1 1.1 0.167 0.152 1.3 26 Example 2 1.0 0.333 0.333 1.3 26 Example 3 1.0 0.50 0.50 1.3 26 Example 4 0.85 0.583 0.686 1.3 26 Example 5 0.85 0.65 0.765 1.3 26 Comparative Example 1 0.75 0.75 1.0 1.3 26

Lwl: Width of wide louver (mm) Lws: Width of narrow louver (mm)

Lws / Lwl: Louver Width Ratio

Fp: Pin Pitch (mm) La: Louver Angle (°)

In Table 1, the evaporator of Example 1 is provided with a corrugated fin having a plurality of louver fins each having alternately arranged wide louvers and narrow louvers. The louver width (Lwl) of the wide louver was set to 1.1 mm, the louver width (Lws) of the narrow louver to 0.167 mm, the louver angle (La) to 26 °, and the pin pitch (Fp) to 1.3 mm. Lws / Lwl) is 0.152.

In the evaporator of Example 2, the louver width Lwl of the wide louver was set to 1.0 mm, and the louver width Lws of the narrow louver was set to 0.333 mm. The remaining dimensions were set the same as in Example 1. The louver width ratio (Lws / Lwl) is 0.333.

In the evaporator of Example 3, the louver width Lwl of the wide louver was set to 1.0 mm, and the louver width Lws of the narrow louver was set to 0.5 mm. The remaining dimensions were set the same as in Example 1. The width ratio (Lws / Lwl) of the louver is 0.50.

In the evaporator of Example 4, the louver width Lwl of the wide louver was set to 0.85 mm, and the louver width Lws of the narrow louver was set to 0.583 mm. The remaining dimensions were set the same as in Example 1. The width ratio (Lws / Lwl) of the louver is 0.686.

In the evaporator of Example 5, the louver width Lwl of the wide louver was set to 0.85 mm, and the louver width Lws of the narrow louver was set to 0.65 mm. The remaining dimensions were set the same as in Example 1. The width ratio (Lws / Lwl) of the louver is 0.765.

In the evaporator of Comparative Example 1, the corrugated fin has a plurality of louvers arranged at a constant louver width (louver pitch) of 0.75 mm. The remaining dimensions were set the same as in Example 1.

With respect to the evaporator, the respective heat transfer rates for front wind velocity were measured by computer simulation. The results are shown in the graph of FIG.

As is apparent from this graph, the evaporators of Examples 1 to 5 are approximately 10 to 20% higher in heat transfer rate in the entire front wind speed region than the evaporators of Comparative Example 1, and thus have excellent heat exchange performance. In particular, the heat transfer rate is excellent in a low speed running state or an idling state whose front wind speed is 2 m / s or less.

In addition, the evaporator of Example 1 has a higher heat transfer rate than the evaporator of Example 2.

In Examples 1 to 5, the heat transfer rate in Examples 1 to 4, wherein the ratio (Lws / Lwl) of the narrow louver to the louver width Lwl of the wide louver is 0.1 to 0.7, The width ratio of the louvers (Lws / Lwl) is more stable than the heat transfer rate in Example 5, which exceeds 0.7. Among them, in each of Examples 2 to 4 in which the louver width ratio (Lws / Lwl) was 0.3 to 0.7, sufficient heat transfer rate was obtained in all front wind speed regions.

<Example 6, 7>

Table 2

Lwl (mm) Lws (mm) Lws / Lwl Fp (mm) La (°) Example 6 1.0 0.333 0.333 1.3 28 Example 7 1.0 0.50 0.50 1.3 28 Comparative Example 2 0.75 0.75 1.0 1.3 28

Lwl: Width of wide louver (mm) Lws: Width of narrow louver (mm)

Lws / Lwl: Louver Width Ratio

Fp: Pin Pitch (mm) La: Louver Angle (°)

As shown in Table 2, the evaporator of Example 6 was prepared in the same manner as in Example 2 except that the louver angle La was set to 28 °.

The evaporator of Example 7 was prepared in the same manner as in Example 3 except that the louver angle La was set to 28 °.

An evaporator of Comparative Example 2 was prepared in the same manner as in Comparative Example 1 except that the louver angle La was set to 28 °.

For the evaporator, the respective heat transfer rates for the front wind speeds were measured by computer simulation. The results are shown in the graph of FIG.

As is apparent from this graph, even when the louver angle La was set to 28 °, the evaporators of Examples 6 and 7 had a higher heat transfer rate in the entire front wind speed region than the evaporators of Comparative Example 2, and thus the heat exchange performance. This is excellent. In particular, the heat transfer rate is high in a low speed running state or idling state whose front wind speed is 2 m / s or less.

<Example 8, 9>

Table 3

Lwl (mm) Lws (mm) Lws / Lwl Fp (mm) La (°) Example 8 1.0 0.333 0.333 1.3 - Example 9 1.0 0.50 0.50 1.3 - Comparative Example 3 0.75 0.75 1.0 1.3 -

Lwl: Width of wide louver (mm) Lws: Width of narrow louver (mm)

Lws / Lwl: Louver Width Ratio

Fp: Pin Pitch (mm) La: Louver Angle (°)

The evaporators of Examples 8, 9 and Comparative Example 3 were prepared in the same manner as in Examples 2, 3 and Comparative Example 1, except that the louver angle La was set as a variable.

In each of these evaporators, the respective heat transfer rates for louver angle La with front wind speeds of 1 m / s and 2 m / s were measured by computer simulation. The results are shown in the graphs of FIG. 7 and FIG.

As is apparent from these graphs, in comparison with the evaporator of Comparative Example 3, the evaporators of Example 8 and Example 9 had a significantly higher heat transfer rate at a louver angle of 17 to 36 ° when the wind speed was 1 m / s, and 36 °. It is slightly above the louver angle exceeding. Also, when the wind speed was 2 m / s, the heat transfer rates of each of Examples 8 and 9 were high at louver angles of 17 to 31 °, whereas at louver angles exceeding 30 °, a significant difference between the Examples and Comparative Examples Could not be recognized.

As shown in Fig. 7, in the idling state where the high performance is hard to be obtained (front wind speed of 1 m / s), the evaporators of Examples 8 and 9 can obtain a high heat transfer rate at a louver angle La of 22 to 36 °. have. When the lower limit is 24 ° or more and the upper limit is 32 ° or less, higher heat transfer rates can be obtained.

In addition, as shown in FIG. 8, when the front wind speed is 2 m / s, a high heat transfer rate can be obtained at a louver angle La of 20 to 30 degrees. When the lower limit is 22 ° or more and the upper limit is 28 ° or less, higher heat transfer rates can be obtained.

<Examples 10 and 11>

Table 4

Lwl (mm) Lws (mm) Lws / Lwl Fp (mm) La (°) Example 10 1.0 0.333 0.333 - 26 Example 11 1.0 0.50 0.50 - 26 Comparative Example 4 0.75 0.75 1.0 - 26

Lwl: Width of wide louver (mm) Lws: Width of narrow louver (mm)

Lws / Lwl: Louver Width Ratio

Fp: Pin Pitch (mm) La: Louver Angle (°)

As shown in Table 4, the evaporators of Examples 10, 11 and 4 were prepared in the same manner as in Examples 2, 3 and Comparative Example 1, except that the fin pitch Fp was set as a variable.

In each of these evaporators, the respective heat transfer rates for the fin pitch Fp were measured by computer simulations with front wind speeds of 1 m / s and 2 m / s. The results are shown in the graphs of FIGS. 9 and 10.

As is apparent from these graphs, in comparison with the evaporator of Comparative Example 4, the evaporators of Examples 10 and 11 had a pin pitch Fp of 1.0 to 2.4 mm when the wind speeds were 1 m / s and 2 m / s. The heat transfer rate is remarkably high.

In particular, in the evaporators of Examples 10 and 11, when the fin pitch Fp is 1.6 or less, sufficient heat transfer rate is obtained.

In the heat exchanger fin according to the present invention, since a plurality of louvers of different widths are included in the plurality of louvers, a heat medium such as air is reliably introduced into each lower gap formed between adjacent louvers, thus bypass flow. By preventing the occurrence of heat transfer rate is improved.

The terms and expressions used herein are used without limitation for the purpose of description, and the use of such terms and expressions is not intended to exclude any of the equivalents of the figures and the disclosed configuration or parts thereof.

The present invention may be applied to a heat exchanger such as a condenser or an evaporator for a vehicle air conditioner, and may also be applied to a heat exchanger fin such as a louver fin or a corrugated fin to be provided in the heat exchanger.

Claims (30)

And a heat transfer plate disposed in parallel with the heat medium introduction direction and provided with a plurality of louvers provided at predetermined intervals in the heat medium introduction direction, wherein the plurality of louvers are formed by cutting and bending the heat transfer plate, thereby forming the plurality of heat carriers. Fins for heat exchangers that are distributed while being guided by louvers of The plurality of louvers includes a plurality of types of louvers having different louver widths, and the louver widths are defined by the lengths of the louvers in a direction in which the heat medium flows. The plurality of types of louvers having different louver widths are arranged in a mixed arrangement along the heat medium introduction direction. 2. The fin of claim 1, wherein the plurality of louvers include a wide louver wide louver and a narrow louver narrow louver, wherein the wide louvers and the narrow louvers are arranged in a mixed arrangement. 3. The fin of claim 2 wherein at least one said wide louver and at least one said narrow louver are alternately disposed. 3. The fin of claim 2, wherein the wide louver and the narrow louver are alternately disposed. The louver width "Lwl" of the wide louver, according to any one of claims 2 to 4, when the louver width of the wide louver and the louver width of the narrow louver are represented by "Lwl" and "Lws", respectively. Fin for the heat exchanger in which the ratio "Lws / Lwl" of the louver width "Lws" of the narrow louver is set to 0.1 to 0.7. The fin for a heat exchanger according to any one of claims 1 to 5, wherein an angle (louver angle) of said louver with respect to said heat transfer plate is set to 22 to 36 degrees. The heat exchanger fin according to any one of claims 1 to 6, wherein the plurality of heat transfer plates are arranged in parallel to each other at predetermined intervals in a direction orthogonal to the heat medium introduction direction to form an air passage between adjacent heat transfer plates. . 8. The fin of heat exchanger according to claim 7, wherein the fin pitch defined by the spacing between adjacent heat transfer plates is set to 1 to 2 mm. The louver width according to claim 7 or 8, wherein the pin pitch defined by the spacing between adjacent heat transfer plates is represented by "Fp" and the louver width of the louver having the widest louver width is represented by "Lwmax". Fin for heat exchanger in which ratio "Fp / Lwmax" of fin pitch "Fp" to Lwmax "is set to 1 or more. The heat transfer plate according to any one of claims 1 to 9, wherein the heat transfer plates are mutually spaced at predetermined intervals so that heat exchange occurs between air as a heat medium passing between the pair of heat exchange tubes and a refrigerant passing through the heat exchange tubes. Fins for heat exchangers disposed between the pair of heat exchange tubes arranged in parallel. The fin of claim 10, wherein the refrigerant is configured to condense by heat exchange with air. The fin of claim 10, wherein the refrigerant is configured to evaporate by heat exchange with air. A heat transfer plate having a plurality of louvers disposed parallel to the heat medium introduction direction and provided at predetermined intervals in the heat medium introduction direction, wherein the plurality of louvers are formed by cutting and bending of the heat transfer plate, thereby providing a plurality of heat carriers. Louver pins that are distributed while being guided by louvers, The plurality of louvers includes a plurality of types of louvers having different louver widths, and the louver widths are defined by the lengths of the louvers in a direction in which the heat medium flows. The plurality of types of louvers having different louver widths are arranged in a mixed arrangement along the heating medium introduction direction. A plurality of heat transfer plates disposed parallel to the heat medium introduction direction and arranged in parallel at a predetermined interval in a direction orthogonal to the heat medium introduction direction, wherein adjacent heat transfer plates are interconnected, and each of the plurality of heat transfer plates each introduces a heat medium. A plurality of louvers arranged at predetermined intervals in a direction, wherein the plurality of louvers are formed by cutting and bending of the heat transfer plate, so that a heat medium is guided by the plurality of louvers and is a corrugated fin. The plurality of louvers includes a plurality of types of louvers having different louver widths, and the louver widths are defined by the lengths of the louvers in a direction in which the heat medium flows. The plurality of types of louvers having different louver widths are corrugated pins arranged in a mixed arrangement. A plurality of heat exchanger fins arranged in parallel with respect to the air introduction direction and arranged in parallel at a predetermined interval in a direction orthogonal to the air introduction direction, and a refrigerant passage through which the refrigerant passes, wherein each of the plurality of heat exchanger plates includes air And a plurality of louvers arranged at predetermined intervals in the introduction direction, wherein the plurality of louvers are formed by cutting and bending the fins for the heat exchanger so that air is circulated while being guided by the plurality of louvers to exchange heat between air and refrigerant. Is a heat exchanger made up of, The plurality of louvers includes a plurality of types of louvers having different louver widths, and the louver widths are defined by the lengths of the louvers in a direction in which the heat medium flows. The plurality of types of louvers having different louver widths are arranged in a mixed arrangement. A pair of heat exchange tubes arranged in parallel at a predetermined interval, and a plurality of heat exchanger fins arranged in parallel with respect to the air introduction direction and arranged in parallel at a predetermined interval in a direction orthogonal to the air introduction direction, Each of the plurality of heat exchanger fins includes a plurality of louvers disposed at predetermined intervals in the air introduction direction, and the plurality of louvers are formed by cutting and bending of the heat exchanger fins so that air is guided by the plurality of louvers. Is a heat exchanger that is circulated and exchanges heat between air and a refrigerant, The plurality of louvers includes a plurality of types of louvers having different louver widths, and the louver widths are defined by lengths of the louvers in a direction in which air flows. The plurality of types of louvers having different louver widths are arranged in a mixed arrangement. The heat exchanger according to claim 15 or 16, wherein the plurality of louvers have a wide louver wide louver and a narrow louver narrow louver, and the wide louvers and the narrow louvers are arranged in a mixed arrangement. The heat exchanger according to claim 15 or 16, wherein adjacent fins of the plurality of heat exchanger fins are in contact with each other. A plurality of heat exchanger fins arranged in parallel with respect to the air introduction direction and arranged in parallel at a predetermined interval in a direction orthogonal to the air introduction direction, and a refrigerant passage through which the refrigerant passes, wherein each of the plurality of heat exchanger plates includes air And a plurality of louvers arranged at predetermined intervals in the introduction direction, wherein the plurality of louvers are formed by cutting and bending the fins for the heat exchanger so that air is circulated while being guided by the plurality of louvers to exchange heat between the air and the refrigerant. Condenser where the refrigerant is condensed by The plurality of louvers includes a plurality of types of louvers having different louver widths, and the louver widths are defined by the lengths of the louvers in a direction in which the heat medium flows. And the plurality of louvers having different louver widths are arranged in a mixed arrangement. A pair of heat exchange tubes arranged in parallel at a predetermined interval, and a plurality of heat exchanger fins arranged in parallel with respect to the air introduction direction and arranged in parallel at a predetermined interval in a direction orthogonal to the air introduction direction, Each of the plurality of heat exchanger fins includes a plurality of louvers disposed at predetermined intervals in the air introduction direction, and the plurality of louvers are formed by cutting and bending of the heat exchanger fins so that air is guided by the plurality of louvers. It is a condenser that is circulated and condensed refrigerant by heat exchange between air and refrigerant, The plurality of louvers includes a plurality of types of louvers having different louver widths, and the louver widths are defined by lengths of the louvers in a direction in which air flows. And the plurality of louvers having different louver widths are arranged in a mixed arrangement. 21. The condenser of claim 19 or 20, wherein the plurality of louvers have a wide louver wide louver and a narrow louver narrow louver, wherein the wide louvers and the narrow louvers are arranged in a mixed arrangement. 21. The condenser of claim 19 or 20, wherein adjacent fins of the plurality of heat exchanger fins are in contact with each other. The condenser used in refrigeration cycles for vehicle air conditioners, A plurality of heat exchanger fins arranged in parallel with respect to the air introduction direction and arranged in parallel at a predetermined interval in a direction orthogonal to the air introduction direction, and A refrigerant passage through which the refrigerant passes, Each of the plurality of heat exchanger plates includes a plurality of louvers arranged at predetermined intervals in the air introduction direction, and the plurality of louvers are formed by cutting and bending of the heat exchanger fins so that air is guided by the plurality of louvers. As it is distributed, the refrigerant is condensed by heat exchange between air and refrigerant, The plurality of louvers includes a plurality of types of louvers having different louver widths, and the louver widths are defined by the lengths of the louvers in a direction in which the heat medium flows. And the plurality of louvers having different louver widths are arranged in a mixed arrangement. The condenser used in refrigeration cycles for vehicle air conditioners, A pair of heat exchange tubes arranged in parallel at a predetermined interval, and A plurality of heat exchanger fins disposed in parallel with respect to the air introduction direction and arranged in parallel with each other at predetermined intervals in a direction orthogonal to the air introduction direction, Each of the plurality of heat exchanger fins includes a plurality of louvers disposed at predetermined intervals in the air introduction direction, and the plurality of louvers are formed by cutting and bending the heat exchanger fins so that air is guided by the plurality of louvers. As it is distributed, the refrigerant is condensed by heat exchange between air and refrigerant, The plurality of louvers includes a plurality of types of louvers having different louver widths, and the louver widths are defined by lengths of the louvers in a direction in which air flows. And the plurality of louvers having different louver widths are arranged in a mixed arrangement. A plurality of heat exchanger fins arranged in parallel with respect to the air introduction direction and arranged in parallel at a predetermined interval in a direction orthogonal to the air introduction direction, and a refrigerant passage through which the refrigerant passes, wherein each of the plurality of heat exchanger plates includes air And a plurality of louvers arranged at predetermined intervals in the introduction direction, wherein the plurality of louvers are formed by cutting and bending the fins for the heat exchanger so that air is guided by the plurality of louvers and flows between the air and the refrigerant. Evaporator in which the refrigerant is evaporated by heat exchange, The plurality of louvers includes a plurality of types of louvers having different louver widths, and the louver widths are defined by the lengths of the louvers in a direction in which the heat medium flows. And said plurality of types of louvers having different louver widths are arranged in a mixed arrangement. A pair of heat exchange tubes arranged in parallel at a predetermined interval, and a plurality of heat exchanger fins arranged in parallel with respect to the air introduction direction and arranged in parallel at a predetermined interval in a direction orthogonal to the air introduction direction, Each of the plurality of heat exchanger fins includes a plurality of louvers disposed at predetermined intervals in the air introduction direction, and the plurality of louvers are formed by cutting and bending of the heat exchanger fins so that air is guided by the plurality of louvers. Is an evaporator that is distributed and evaporates the refrigerant by heat exchange between air and the refrigerant, The plurality of louvers includes a plurality of types of louvers having different louver widths, and the louver widths are defined by lengths of the louvers in a direction in which air flows. And said plurality of types of louvers having different louver widths are arranged in a mixed arrangement. 27. The evaporator of claim 25 or 26 wherein the plurality of louvers have a wide louver wide louver and a narrow louver narrow louver, wherein the wide louvers and the narrow louvers are arranged in a mixed arrangement. 27. The evaporator of claim 25 or 26 wherein adjacent fins of the plurality of heat exchanger fins are in contact with each other. Evaporator used in refrigeration cycles for vehicle air conditioners, A plurality of heat exchanger fins arranged in parallel with respect to the air introduction direction and arranged in parallel at a predetermined interval in a direction orthogonal to the air introduction direction, and A refrigerant passage through which the refrigerant passes, Each of the plurality of heat exchanger plates includes a plurality of louvers arranged at predetermined intervals in the air introduction direction, and the plurality of louvers are formed by cutting and bending of the heat exchanger fins so that air is guided by the plurality of louvers. As it is distributed, the refrigerant is evaporated by heat exchange between air and refrigerant, The plurality of louvers includes a plurality of types of louvers having different louver widths, and the louver widths are defined by the lengths of the louvers in a direction in which the heat medium flows. And said plurality of types of louvers having different louver widths are arranged in a mixed arrangement. Evaporator used in refrigeration cycles for vehicle air conditioners, A pair of heat exchange tubes arranged in parallel at a predetermined interval, and A plurality of heat exchanger fins each disposed in parallel to the air introduction direction and arranged in parallel to each other at a predetermined interval in a direction orthogonal to the air introduction direction, Each of the plurality of heat exchanger fins includes a plurality of louvers disposed at predetermined intervals in the air introduction direction, and the plurality of louvers are formed by cutting and bending the heat exchanger fins so that air is guided by the plurality of louvers. As it is distributed, the refrigerant is evaporated by heat exchange between air and refrigerant, The plurality of louvers includes a plurality of types of louvers having different louver widths, and the louver widths are defined by lengths of the louvers in a direction in which air flows. And said plurality of types of louvers having different louver widths are arranged in a mixed arrangement.

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