WO2012148223A2

WO2012148223A2 - Heat exchanger

Info

Publication number: WO2012148223A2
Application number: PCT/KR2012/003301
Authority: WO
Inventors: 박태균; 박내현
Original assignee: 엘지전자 주식회사
Priority date: 2011-04-29
Filing date: 2012-04-27
Publication date: 2012-11-01
Also published as: WO2012148223A3; KR20120122560A

Abstract

The present invention relates to a heat exchanger. In one aspect of one embodiment of the present invention, an inlet region and an outlet region are arranged inside a first header, a connection region is provided only inside a second header or inside both said second header and inside a portion of said first header corresponding to a region between said inlet region and said outlet region, and an inlet tube is arranged so as to be spaced apart from a virtual straight line which bisects the distance between the centers of the uppermost and lowermost tubes from among said tubes in communication with said inlet region. Alternatively, an outlet tube is arranged so as to be spaced apart from a virtual straight line which bisects the distance between the centers of the uppermost and lowermost tubes from among said tubes in communication with said outlet region. According to said embodiment of the present invention, the heat-exchange efficiency of the heat exchanger may be substantially improved.

Description

heat exchanger

The present invention relates to a heat exchanger.

The heat exchanger performs heat exchange between the refrigerant flowing therein and the air. Such a heat exchanger generally includes a plurality of tubes through which refrigerant flows, a plurality of fins stacked on the tubes, and two headers respectively connected to both ends of the tubes. The interior of the header is partitioned by a baffle such that the flow path formed by the tube substantially forms a sandpaper that is bent a number of times throughout. The header is connected to a suction pipe for suction of the refrigerant and a discharge pipe for discharge of the refrigerant, respectively. The suction pipe and the discharge pipe may be located in each of the two headers, or both of the two headers.

However, the following problems occur in the heat exchanger according to the prior art.

When the heat exchanger is used as an evaporator, the liquid refrigerant is sucked through the suction pipe. Therefore, by the centrifugal force acting in the process of changing the flow direction of the refrigerant inside the header, the refrigerant is concentrated in a portion of the tube and flows. In addition, a disadvantage in that the heat exchange efficiency of the refrigerant and air is substantially lowered due to the nonuniform flow of the refrigerant.

The present invention has been made to solve the above-mentioned conventional problems, and an object of the present invention is to provide a heat exchanger configured to allow the refrigerant to flow evenly through the tube.

Another object of the present invention is to provide a heat exchanger configured to perform heat exchange more efficiently.

One aspect of an embodiment of a heat exchanger according to the present invention for achieving the above object is composed of a plurality of spaced apart from each other in a direction perpendicular to the longitudinal direction having a predetermined length, the flow of the refrigerant is made continuously A plurality of tubes divided into a plurality of groups; A plurality of fins for increasing the contact area of air with the tube; First and second headers respectively connected to both ends of the tube, the inside of the tube being divided into a plurality of regions; A suction pipe connected to the first header and into which a refrigerant flowing through the tube is sucked; A discharge pipe connected to the first header and discharging the refrigerant flowing through the tube; Wherein each group of tubes comprises three or more tubes, the region comprising: a suction region provided inside the first header and communicating the suction tube and a portion of the tube; A discharge area provided inside the first header and communicating the discharge pipe with another part of the tube; And at least one connection area provided in the second header or in the first header corresponding to the inside of the second header and between the suction area and the discharge area and communicating with the rest of the tubes adjacent to each other. ; Wherein the suction pipe is spaced apart from an imaginary straight line bisecting a distance between a center of a tube located at the top and the bottom of the tube communicating with the suction area, or the discharge pipe is in communication with the discharge area. It is positioned away from an imaginary straight line that bisects the distance between the centers of the tubes located at the top and bottom of the tubes.

Another aspect of an embodiment of the present invention includes a plurality of tubes in which a refrigerant flows, has a predetermined length, and is spaced apart in a direction orthogonal to the longitudinal direction; A plurality of fins for increasing the contact area of air with the tube; First and second headers connected to both ends of the tube, respectively; A suction pipe connected to the first header and into which a refrigerant flowing through the tube is sucked; A discharge pipe connected to the first header and discharging the refrigerant flowing through the tube; A heat exchanger comprising: the tube includes an inlet-side tube which is composed of a plurality of refrigerants flowing in a predetermined direction and receives the refrigerant sucked through the suction pipe; And an outlet tube configured to have a plurality of refrigerants flowing in a direction opposite to the inlet tube, and to deliver the refrigerant to the discharge tube. And a distance l1 between the center of the tube closest to the outlet tube among the inlet tubes and the center of the suction tube is located at the outermost side in a direction orthogonal to the longitudinal direction of the inlet tubes. Less than 1/2 of the distance L1 between the centers of the two tubes, or the distance l2 between the center of the tube closest to the inlet tube and the center of the discharge tube among the outlet tubes is the outlet It is less than 1/2 of the distance L2 between the centers of the two tubes located outermost in the direction orthogonal to the longitudinal direction of the side tubes.

In an embodiment of the heat exchanger according to the present invention, a suction tube for supplying the refrigerant to the tube and a discharge tube for discharging the refrigerant flowing through the tube are positioned to allow the refrigerant to flow evenly through the tube. Therefore, according to the embodiment of the present invention, the heat exchange efficiency of the heat exchanger can be substantially improved.

1 is a cross-sectional view showing a first embodiment of a heat exchanger according to the present invention.

Figure 2 is a cross-sectional view showing a second embodiment of the heat exchanger according to the present invention.

Figure 3 is a cross-sectional view showing a third embodiment of the heat exchanger according to the present invention.

Figure 4 is a sectional view showing a fourth embodiment of the heat exchanger according to the present invention.

Hereinafter, a configuration of a first embodiment of a heat exchanger according to the present invention will be described in more detail with reference to the accompanying drawings.

Referring to FIG. 1, the heat exchanger 100 according to the present embodiment includes a plurality of tubes 110 through which refrigerant flows, a plurality of fins 120 stacked on the tubes 110, and a plurality of tubes 110. Two

headers

130 and 140 connected to both ends, a suction pipe 150 for sucking the refrigerant flowing through the tube 110, and a discharge pipe 160 for discharging the refrigerant flowing through the tube 110. Include.

In more detail, the tube 110 has a predetermined length and is disposed to extend in parallel with each other in the horizontal direction. The tubes 110 are spaced apart from each other in a direction orthogonal to the longitudinal direction. The tube 110 is formed in a tubular shape in which one or a plurality of flow paths through which refrigerant flows are provided. In particular, when a plurality of flow paths are provided inside the tube 110, it may be called a micro channel type tube.

Meanwhile, the tube 110 is divided into a plurality of groups. That is, the first tube 111 receives the refrigerant sucked through the suction pipe 150, the second tube 112 receives the refrigerant from the first tube 111, and the refrigerant from the second tube 112. Receiving a third tube 113, and receives the refrigerant from the third tube 113 includes a fourth tube 114 to deliver to the discharge pipe (160). Substantially, the first and

fourth tubes

111 and 114 are located at the inlet and outlet sides relative to the flow direction of the refrigerant. Therefore, the first tube 111 may be referred to as an inlet side tube and the fourth tube 114 may be referred to as an outlet side tube. The second and

third tubes

112 and 113 may serve to substantially connect the first and

fourth tubes

111 and 114. Accordingly, the second and

third tubes

112 and 113 may be referred to as connection tubes, respectively.

In FIG. 1, although the first to

fourth tubes

111, 112, 113, and 114 are respectively configured as three, the first to

fourth tubes

111, 112, and 113 are respectively configured. 114 may be comprised of four or more. In addition, the first to

fourth tubes

111, 112, 113, and 114 do not necessarily have the same number. That is, the number of the first to

fourth tubes

111, 112, 113, and 114 may be gradually increased. For example, the first tube 111 is composed of three, the second tube 112 is composed of four, the third tube 113 is composed of five, the fourth tube 114 May be composed of six.

The pins 120 are stacked on the tube 110. At this time, the pins 120 are stacked in a direction orthogonal to the longitudinal direction of the tube 110. The fins 120 adjacent to each other are spaced apart from each other in the longitudinal direction of the tube 110. The fin 120 serves to increase the contact area between the tube 110 and the air.

The

headers

130 and 140 are connected to both ends of the tube 110, respectively. Hereinafter, for convenience of description, the right header in FIG. 1 is referred to as the first header 130 and the left header in the drawing is referred to as a second header 140. A plurality of

baffles

131 and 141 are provided in the first and

second headers

130 and 140, respectively. The

baffles

131 and 141 divide the interior of the first and

second headers

130 and 140 into a plurality of regions, respectively. In more detail, two baffles 131 (hereinafter referred to as 'first baffles') are provided inside the first header 130. The first baffle 131 is an area in which the inside of the first header 130 communicates with the right end of the drawing of the first tube 111, and the second and

third tubes

112 and 113. And the area communicating with the right end in the drawing, and the area communicating with the right end in the drawing of the fourth tube 114. In addition, one baffle 141 (hereinafter referred to as a “second baffle” for convenience of description) is provided inside the second header 140. The second baffle 141 is a region in which the left end portion of the second header 140 communicates with each other in the drawing of the first and

second tubes

111 and 112, and the third and fourth portions. The left end of the

tube

113, 114 is divided into areas in communication with each other. Hereinafter, for convenience of description, each of the inner end portions of the first header 130 which communicates with the right end portion in the drawing of the first tube 111 and the right end portion in the drawing of the fourth tube 114 are respectively sucked. The area S1 and the discharge area S5 are called. And an inner portion of the second header 140 in communication with the left end of the first and

second tubes

111 and 112, and a right side in the drawings of the second and

third tubes

112 and 113. The inner rest of the first header 130 in communication with the end, the inner rest of the second header 140 in communication with the left end in the drawings of the third and

fourth tubes

113, 114, respectively, The first to third connection regions S2, S3, and S4 are referred to. Therefore, in the heat exchanger 100, the suction region S1-> the first tube 111-> the first connection region S2-> the second tube 112-> the second connection region (S3)-> the third tube 113-> the third connection region (S4)-> the fourth tube 114-> the discharge region (S5) in the order can be said to be formed. have.

Meanwhile, the suction pipe 150 and the discharge pipe 160 are connected to the first header 130, respectively. Substantially, the suction pipe 150 is in communication with the suction area S1, and the discharge pipe 160 is in communication with the discharge area S5. Therefore, the refrigerant sucked through the suction pipe 150 is transferred to the first tube 111 via the suction region S1. The refrigerant delivered to the first tube 111 flows from the right side to the left side of the first tube 111, and the flow direction thereof is changed while passing through the first connection region S2. Delivered to tube 112. The refrigerant transferred to the second tube 112 flows the second tube 112 from the left to the right in the drawing, and the flow direction thereof is changed while passing through the second connection region S3 to the third tube. It is delivered to the tube 113. The refrigerant delivered to the third tube 113 flows from the right side to the left side of the third tube 113, and the flow direction thereof is changed while passing through the third connection region S4. It is delivered to four tubes 114. Finally, the refrigerant transferred to the fourth tube 114 flows the fourth tube 114 from the left to the right in the drawing, and the heat exchange is performed through the discharge pipe 160 via the discharge area S5. It is discharged to the outside of the machine (100).

In the present embodiment, the position of the suction pipe 150 is designed to evenly flow the entire first to

fourth tubes

111, 112, 113, 114. More specifically, the suction pipe 150 is located between the tube located at the top of the first tube 111 and the tube located directly below it. In addition, the discharge pipe 160 is located at the center of the discharge area S5 in the vertical direction.

When the suction pipe 150 is positioned as described above, the refrigerant may flow evenly through the first to

fourth tubes

111, 112, 113, and 114. In Table 1 below, (A) is the same as in the prior art in which the suction pipe 150 and the discharge pipe 160 are respectively positioned at the center of the suction area S1 and the discharge area S5 in the vertical direction. . In Table 1, (B) is the case where the suction pipe 150 and the discharge pipe 160 are positioned as in this embodiment.

Table 1

	Pressure loss (psi)	(Qi-Q) / Qi × 100 (%)
A	1.46	13.19
B	1.37	6.49

Here, the pressure loss refers to a pressure between the pressure of the refrigerant sucked into the heat exchanger 100 through the suction pipe 150 and the pressure of the refrigerant discharged to the outside of the heat exchanger 100 through the discharge pipe 160. Means tea. Therefore, as the pressure loss increases, the load on the compressor constituting the heat exchange cycle together with the heat exchanger 100 increases substantially. In addition, Qi is the designed heat exchange output of the heat exchanger 100, and Q is the actual heat exchange output of the heat exchanger 100. Therefore, a percentage of a value obtained by dividing the difference between the designed heat exchanger output Qi of the heat exchanger 100 and the actual heat exchanger output Q of the heat exchanger 100 by the designed heat exchanger output Qi of the heat exchanger 100. It can be said that the smaller this is, the output close to the substantially designed heat exchange output. However, referring to [Table 1], in the case of (B) compared to (A), that is, the case in which the suction pipe 150 is positioned as in this embodiment, the pressure loss and the designed heat exchange output of the heat exchanger 100 ( It can be seen that the percentage of the difference between the difference between Qi) and the actual heat exchanger output Q of the heat exchanger 100 divided by the designed heat exchanger output Qi of the heat exchanger 100 is relatively reduced. This is substantially because in the present embodiment, the refrigerant flows evenly throughout the first to

fourth tubes

111, 112, 113, and 114.

Hereinafter, a second embodiment of a heat exchanger according to the present invention will be described in more detail with reference to the accompanying drawings.

2 is a cross-sectional view showing a second embodiment of a heat exchanger according to the present invention. The same reference numerals as in FIG. 1 are used for the same components as those of the first embodiment of the present invention, and detailed description thereof will be omitted.

Referring to FIG. 2, in this embodiment, the positions of the suction pipe 150 and the discharge pipe 160 are designed to evenly flow the entire first to

fourth tubes

111, 112, 113, and 114. do. More specifically, the suction pipe 150 is located between the tube located at the top of the first tube 111 and the tube located directly below it. This is the same as the first embodiment of the present invention described above. In the present embodiment, the discharge pipe 160 is positioned between the tube located at the lowermost end of the fourth tube 114 and the tube located directly above it.

In Table 2 below, the suction pipe 150 and the discharge pipe 160 are each positioned in the center of the suction area S1 and the discharge area S5 in the vertical direction, respectively. As in the embodiment, the experimental data in the case where the suction pipe 150 and the discharge pipe 160 are located (C), respectively.

TABLE 2

	Pressure loss (psi)	(Qi-Q) / Qi × 100 (%)
A	1.46	13.19
C	0.90	2.15

Therefore, referring to [Table 2], it can be seen that in the case where the suction pipe 150 and the discharge pipe 160 are positioned as in the present embodiment (C), the pressure loss and the output deviation are relatively reduced compared to (A). have. In addition, in the case (C) according to the present embodiment, the pressure loss and the designed heat exchange output Qi of the heat exchanger 100 and the heat exchanger are substantially reduced as compared with the case (B) of the first embodiment of the present invention. It can be seen that the percentage of the difference between the actual heat exchange output Q of 100 divided by the designed heat exchange output Q i of the heat exchanger 100 is further reduced.

Hereinafter, a third embodiment of a heat exchanger according to the present invention will be described in more detail with reference to the accompanying drawings.

3 is a cross-sectional view showing a third embodiment of a heat exchanger according to the present invention.

Referring to FIG. 3, even in this embodiment, the heat exchanger 200 includes a plurality of tubes 210, a plurality of fins 220, first and second headers 230 and 240, a suction pipe 250, and the like. The discharge pipe 260 is included. The tube 210 includes first to fourth tubes 211, 212, 213, and 214. In the first and second headers 230 and 240, the suction area S1, the discharge area S5, and the first area, which are partitioned by the first and second baffles 231 and 241, respectively. To third connection regions S3, S4, and S5. The suction pipe 250 and the discharge pipe 260 are connected to the first header 230 so as to communicate with the suction area S1 and the discharge area S5, respectively. Such a configuration can be said to be the same as the first embodiment of the present invention described above.

However, in the present embodiment, a tube of a micro channel type having a plurality of flow paths therein is used as the tube 210. The fin 220 is bent several times and positioned between the tubes 210 adjacent to each other.

In addition, in the present embodiment, the suction pipe 250 is positioned to be spaced apart from an imaginary straight line that bisects the distance L1 between the centers of the tubes located at the top and bottom of the first tube 211. In addition, the discharge pipe 260 is positioned to be spaced apart from an imaginary straight line bisecting the distance (L2) between the center of the tube located at the top and bottom of the fourth tube (214).

More specifically, the distance l1 between the center of the tube located at the top of the first tube 211 and the center of the suction tube 250 is the first tube 211. It is located at a position which is less than 1/2 of the distance L1 between the centers of the tubes located at the top and bottom of the middle. In addition, the discharge pipe 260 has a distance l2 between the center of the tube located at the lowest end of the fourth tube 214 and the center of the discharge pipe 260, the top and bottom of the fourth tube 214. It is located at a position that is less than 1/2 of the distance L2 between the centers of the tubes located at. Preferably, the distance l1 between the center of the tube located at the top of the first tube 211 and the center of the suction tube 250 is located at the top and the bottom of the first tube 211. It is at least 1/4 and less than 1/2 of the distance L1 between the centers of. The distance l2 between the center of the tube located at the bottom of the fourth tube 214 and the center of the discharge tube 260 is between the center of the tube located at the top and bottom of the fourth tube 214. Is 1/4 or more and 1/3 or less of the distance L2. If this is expressed as an expression, it is as follows.

(1) 1/4 ≤ l1 / L1 <1/2

(2) 1/4 ≤ l2 / L2 ≤ 1/3

Also in this embodiment, similar to the second embodiment of the present invention described above, the refrigerant may flow evenly through the entire first to fourth tubes 211, 212, 213, 214. Therefore, according to this embodiment, it will be expected to substantially increase the heat exchange efficiency of the heat exchanger 200.

Hereinafter, with reference to the accompanying drawings a fourth embodiment of the heat exchanger according to the present invention will be described in more detail.

4 is a cross-sectional view showing a fourth embodiment of a heat exchanger according to the present invention.

Referring to FIG. 4, even in this embodiment, the heat exchanger 300 includes a plurality of tubes 310, a plurality of fins 320, first and second headers 330, 340, a suction pipe 350, and the like. The discharge pipe 360 is included. In this embodiment, the tube 310 includes first and

second tubes

311 and 312. The number of the first and

second tubes

311 and 312 may be configured in a ratio of 4: 5. For example, the first tube 311 is composed of eight, the second tube 312 may be composed of ten. In addition, an inside of the first header 340 is provided with a suction region S1 and a discharge region S5, which are partitioned off by the first baffle 331. In addition, a connection area S3 is provided inside the second header 340. In addition, the suction pipe 350 and the discharge pipe 360 are connected to the first header 330 so as to communicate with the suction area S1 and the discharge area S5, respectively. Such a configuration can be said to be the same as the first embodiment of the present invention described above.

In this embodiment, a tube of a micro channel type having a plurality of flow paths is used as the tube 310. In addition, the fin 320 is composed of a plurality of stacked in the direction orthogonal to the longitudinal direction of the tube (310).

Also, in this embodiment, the suction pipe 350 and the discharge pipe 360 are positioned similarly to the third embodiment of the present invention described above. That is, the suction pipe 350 has a distance l1 between the center of the tube located at the uppermost end of the first tube 311 and the center of the suction pipe 350, and is the uppermost and lowermost end of the first tube 311. It is located at a position that is less than 1/2 of the distance L1 between the centers of the tubes located at. Preferably, a distance l1 between the center of the tube located at the top of the first tube 311 and the center of the suction tube 350 is located at the top and bottom of the first tube 311. It is at least 1/4 and less than 1/2 of the distance L1 between the centers of. The discharge pipe 360 has a distance l2 between the center of the tube located at the lowermost end of the second tube 312 and the center of the discharge pipe 360. It is located at a position that is less than 1/2 of the distance L2 between the centers of the tubes located at. Preferably, the distance l2 between the center of the tube located at the bottom of the second tube 312 and the center of the discharge pipe 360 is a tube located at the top and bottom of the second tube 312. Is equal to or greater than 1/4 and less than 1/3 of the distance L2 between the centers.

And the experimental data according to the position of the suction pipe 350 and the discharge pipe 360 can be confirmed as shown in Table 3 below. Here, (A) is the prior art, that is, the distance l1 between the center of the tube located at the top of the first tube 311 and the center of the suction pipe 350 is the top of the first tube 311 And a half of the distance L1 between the center of the tube located at the bottom end, and the distance l2 between the center of the tube located at the bottom of the second tube 312 and the center of the discharge pipe 360 is In this case, 1/2 of the distance (L2) between the center of the tube located at the top and the bottom of the second tube (312). And (D), the distance l1 between the center of the tube located at the top of the first tube 311 and the center of the suction tube 350 is located at the top and the bottom of the first tube 311. 1/4 of the distance L1 between the center of the tube, and the distance l2 between the center of the tube located at the bottom of the second tube 312 and the center of the discharge pipe 360 is the second. It is the case of 1/2 of the distance L2 between the center of the tube located in the uppermost and lowermost part of the tube 312. In addition, (E), the distance l1 between the center of the tube located at the top of the first tube 311 and the center of the suction pipe 350 is located at the top and the bottom of the first tube 311. 1/4 of the distance L1 between the center of the tube, and the distance l2 between the center of the tube located at the bottom of the second tube 312 and the center of the discharge pipe 360 is the second. This is the case of 1/3 of the distance L2 between the center of the tube located at the top and bottom of the tube 312.

TABLE 3

	Suction tube position (l1 / l1)	Location of discharge pipe (l2 / l2)	Pressure loss	(Qi-Q) / Qi × 100 (%)
A	1/2	1/2	1.46	9.63
D	1/4	1/2	1.37	6.49
E	1/4	1/3	0.90	1.4

As shown in Table 3, the pressure loss and the heat exchange of the suction pipe 350 or the suction pipe 350 and the discharge pipe 360 are changed in comparison with the conventional case (A). The percentage of the difference between the designed heat exchanger output Qi of the heat exchanger 100 and the actual heat exchanger output Q of the heat exchanger 100 divided by the designed heat exchanger output Qi of the heat exchanger 100 is relatively It can be seen that the decrease.

Within the scope of the basic technical idea of the present invention as well as many other modifications are possible to those skilled in the art, the scope of the present invention should be interpreted based on the appended claims. .

Claims

A plurality of tubes having a predetermined length and arranged to be spaced apart from each other in a direction orthogonal to the longitudinal direction, the plurality of tubes being divided into a plurality of groups in which the flow of the refrigerant is continuously formed;

A plurality of fins for increasing the contact area of air with the tube;

First and second headers respectively connected to both ends of the tube, the inside of the tube being divided into a plurality of regions;

A suction pipe connected to the first header and into which a refrigerant flowing through the tube is sucked; And

A discharge pipe connected to the first header and discharging the refrigerant flowing through the tube; Including,

Each group of tubes consists of three or more tubes,

The area is,

A suction area provided inside the first header and communicating part of the suction pipe and the tube;

A discharge area provided inside the first header and communicating the discharge pipe with another part of the tube; And

And at least one connection area provided in the second header or in the first header corresponding to the inside of the second header and between the suction area and the discharge area and communicating with the rest of the tubes adjacent to each other. ; Including,

The suction pipe is located away from an imaginary straight line bisecting the distance between the center of the tube located at the top and bottom of the tube in communication with the suction area, or the top of the tube in which the discharge pipe is in communication with the discharge area; A heat exchanger positioned spaced apart from an imaginary straight line that bisects the distance between the centers of the tubes located at the lowest end.
The method of claim 1,

And a heat exchanger located between the tube closest to the connection area or the discharge area among the tubes in communication with the suction area and the tube closest to it.
The method of claim 1,

And the discharge pipe is located between a tube most adjacent to the connection area or the suction area among the tubes in communication with the discharge area and a tube closest to it.
The method of claim 1,

A larger heat exchanger comprising a relatively large number of said tubes in communication with said discharge zone as compared to said tubes in communication with said suction zone.
The method of claim 1,

Inside the tube, one flow path is provided,

And a plurality of fins are stacked in a direction orthogonal to the longitudinal direction of the tube.
The method of claim 1,

The inside of the tube is provided with a plurality of flow paths partitioned from each other,

And a plurality of fins stacked between the tubes adjacent to each other or in a direction orthogonal to a length direction of the tubes.
The method of claim 1,

The inside of the tube is provided with a plurality of flow paths partitioned from each other,

And the fins are located between the tubes adjacent to each other.
A plurality of tubes in which the refrigerant flows, has a predetermined length, and is spaced apart in a direction orthogonal to the length direction; A plurality of fins for increasing the contact area of air with the tube; First and second headers connected to both ends of the tube, respectively; A suction pipe connected to the first header and into which a refrigerant flowing through the tube is sucked; A discharge pipe connected to the first header and discharging the refrigerant flowing through the tube; In a heat exchanger comprising:

The tube,

An inlet-side tube composed of a plurality of refrigerants flowing in a predetermined direction and receiving refrigerant sucked through the suction pipe; And

An outlet tube configured to have a plurality of refrigerants flowing in a direction opposite to the inlet tube, and to deliver the refrigerant to the discharge tube; Including,

The distance l1 between the center of the tube closest to the outlet tube among the inlet tubes and the center of the suction tube is located at the outermost side in the direction orthogonal to the longitudinal direction of the inlet tubes. The distance l2 between less than half of the distance L1 between the centers of the outlet tubes or the center of the tube closest to the inlet tube among the outlet tubes and the center of the outlet tube is equal to that of the outlet tube. A heat exchanger of less than one half of the distance (L2) between the centers of two tubes located at the outermost side in a direction orthogonal to the longitudinal direction.
The method of claim 8,

The distance l1 between the center of the tube closest to the outlet tube among the inlet tubes and the center of the suction tube is located at the outermost side in the direction orthogonal to the longitudinal direction of the inlet tubes. A heat exchanger of at least 1/4 and less than 1/2 of the distance L1 between the centers of the.
The method of claim 8,

The distance l2 between the center of the tube closest to the inlet side tube and the center of the discharge tube among the outlet side tubes is located at the outermost side in the direction orthogonal to the longitudinal direction of the outlet side tubes. A heat exchanger of at least 1/4 and less than 1/3 of the distance (L2) between the centers of the.
The method of claim 8,

The inlet tube and the outlet tube are each composed of three or more tubes.
The method of claim 8,

A heat exchanger comprising a plurality of the outlet tube relatively compared to the inlet tube.
The method of claim 8,

And a plurality of connection tubes configured to flow in the same direction as any one of the inlet tube and the outlet tube, and receive a refrigerant from the inlet tube and deliver the refrigerant to the outlet tube.
The method of claim 8,

The tube is a tube type provided with one flow path therein,

And a plurality of fins are stacked in a direction orthogonal to the longitudinal direction of the tube.
The method of claim 8,

The tube is of a micro channel type having a plurality of flow paths partitioned therein,

And a plurality of fins stacked between the tubes adjacent to each other or in a direction orthogonal to the longitudinal direction of the tubes.