WO2020145427A1

WO2020145427A1 - Heat exchanger having plate-type distributors

Info

Publication number: WO2020145427A1
Application number: PCT/KR2019/000299
Authority: WO
Inventors: 천성민; 이덕희
Original assignee: 두성산업 (주)
Priority date: 2019-01-08
Filing date: 2019-01-08
Publication date: 2020-07-16

Abstract

The present invention relates to a heat exchanger having plate-type distributors. The heat exchanger has a plurality of distributors stacked between first and second cover plates. Each of the plurality of distributors has an inlet portion and an outlet portion such that a refrigerant and a fluid to be heated respectively flow in and out, and has continuously formed on the surface thereof chevron portions formed from a V-shaped concavity and convexity. An inclined portion is formed on the inlet portion, of a distributor, through which a refrigerant flows in so as to be attached to inlet portions of stacked upper and lower distributors. A plurality of inlet-outlet holes through which the refrigerant flows in and out are formed on the inclined portion. Therefore, the refrigerant flowing in through the inlet/outlet holes is vaporized and is provided in a diffused manner to the flow paths between the upper and lower distributors.

Description

Heat exchanger equipped with a plate distributor

The present invention relates to a heat exchanger provided with a plate-shaped distributor, and more particularly, to a heat exchanger provided with a plate-shaped distributor to improve heat exchange efficiency by improving the diffusivity of refrigerant flowing between the plate-shaped distributors.

In general, the heat exchanger is composed of a pair of header tanks through which heat exchange medium is introduced and discharged, and tubes connecting the header tanks to distribute heat exchange medium therein, thereby performing heat exchange.

At this time, the heat exchanger can be roughly divided into two types for each type, a fin-tube type heat exchanger made of a plurality of tubes inserted into a tank, and a plate type heat exchanger in which a plurality of plates are stacked to form a tube part and a tank part. It can be classified as a plate heat exchanger.

Among them, the plate type heat exchanger is widely used because it is easy to assemble and has a small number of required parts, which is more productive than the fin-tube type heat exchanger, and has the advantage of securing a space in the engine room by reducing the volume.

In particular, the plate-type heat exchanger can design a more complicated and diversified flow path than the fin-tube type heat exchanger by changing the shape of the plate, so it is applied when two types of fluids flow and exchange heat with each other, such as a water-cooled oil cooler. It is desirable to be.

On the other hand, in the conventional plate heat exchanger, the heat exchange efficiency was determined by considering only the area and pitch of the severon formed in the distributor, and the direction or pressure loss of the fluid flowing in the plate heat exchanger was not largely considered.

As a method for resolving the pressure loss, a method of increasing the stacking amount of a plate heat exchanger was used, which creates a problem of increasing the size and weight of the heat exchanger.

As a related conventional technique, there is Korean Patent Registration No. 10-1206858 (hereinafter referred to as'prior art document'), and in the plate heat exchanger disclosed in the prior art document, a fluid path is formed by constructing a sebron portion and a fluid distribution guide. It describes how to improve the flow.

In particular, in the plate-type heat exchanger of the prior art document, in the process of flowing the fluid to be heated flowing through the fluid inlet to the fluid outlet through the severon part, the fluid passes through the severon part and flows its own heat energy to another layer. It is exchanged with a heat medium (refrigerant).

At this time, between the upper and lower distributors, flow paths through which the fluid to be heated and the heating medium flow are formed in the sebron formed to face each other, and the heating fluid or the heating medium flowing into the respective inlets is the flow path of each layer due to the straightness due to the supply pressure. Since the fluid to be heated and the heat medium are not evenly distributed, there is a problem in that the overall heat exchange performance of the plate heat exchanger is poor.

(Advanced technical literature)

(Patent literature)

(Patent Document 1) Korean Patent No. 10-1206858

Therefore, the present invention was devised to solve the problems of the prior art as described above, and provided with a plurality of plate-shaped distributors in the heat exchanger, and a plurality of entrance holes in the inlet of the plate-shaped distributor through which the refrigerant flows, thereby forming a refrigerant. The purpose of the present invention is to provide a heat exchanger equipped with a plate-shaped distributor capable of improving the diffusibility of the refrigerant, since the refrigerant can be rapidly diffused and spread between the stacked plate-shaped distributors by flowing into the entrance hole through the inlet of each layer. .

In addition, for another purpose of the present invention, by stacking a plurality of plate-shaped distributors provided to be stacked in an asymmetrical structure, asymmetric regions are formed in a flow path of a refrigerant flowing through different layers and a fluid to be heated to improve heat exchange efficiency. It is to provide a heat exchanger provided with a plate-shaped distributor.

The heat exchanger provided with the plate-shaped distributor of the present invention for achieving the above object, the inlet portion and the outlet portion are respectively formed so that the refrigerant and the fluid to be heated enter and exit, respectively, and the surface thereof is made of a convex and concave-shaped severon portion continuously. A heat exchanger in which a plurality of formed distributors are stacked between the first and second cover plates, and an inclined inclined portion is formed at the inlet of the distributor in which the refrigerant flows, so that the inlet of the stacked upper and lower distributors is joined and provided. The inclined portion includes a plurality of entrance holes through which refrigerant enters and exits, and refrigerant flowing into the entrance holes is vaporized to be diffused and supplied to a flow path between upper and lower distributors.

In addition, the entrance hole may be formed in a larger number on the other side of the inclined portion facing the edge portion than one side of the inclined portion facing the central portion of the distributor, and the multiple distributors stacked alternately so that the elongated sebron portions face each other in the opposite direction. The stacked distributor may be provided to be stacked by asymmetrically contacting a flat portion that is bent outwardly from each sebron portion and extends flat.

In addition, an extended extension region is formed in a flow path between both sebron portions of the stacked distributor to generate a vortex flow in a fluid flowing through the flow path, and the flat portions of the stacked upper and lower distributors are formed with different lengths. Can be joined.

According to the heat exchanger provided with a plate-shaped distributor of the present invention, a plurality of plate-shaped distributors are stacked in a heat exchanger, and a plurality of entrance holes are formed around each inlet of a stacked plate-shaped distributor through which refrigerant flows, thereby flowing through the inlet. As some of the refrigerant flows into the entrance and exit, the refrigerant diffuses quickly and spreads in a space between vaporized and stacked plate-shaped distributors, thereby improving the diffusivity of the refrigerant and increasing heat exchange efficiency.

In addition, according to the present invention, by stacking by bonding both sides of the plurality of plate-shaped distributors provided to be stacked in an asymmetrical structure, an extended region of an asymmetrical structure is further formed in each flow path through which the refrigerant and the fluid to be heated flow, thereby flowing each layer. Since the refrigerant to be heated and the fluid to be heated flow in the vortex flow in the extended region of each flow path, the heat exchange efficiency between the refrigerant and the fluid to be heated is improved, thereby improving the heat exchange performance of the heat exchanger.

1 is a combined view of a heat exchanger according to the present invention.

2 is an exploded view of a heat exchanger according to the present invention.

Figure 3 is an enlarged view of the separation of the plate-shaped distributor configured in the heat exchanger according to the present invention.

4 is a cross-sectional view taken along line A-A in FIG. 1.

5 is a cross-sectional view taken along line B-B in FIG. 1.

6 is a cross-sectional view taken along line C-C in FIG. 1.

7 is a view showing the diffusivity of the refrigerant introduced through the entrance hole formed in each inlet of the laminated plate-shaped distributor according to the present invention.

8 is a cross-sectional view taken along line A-A of FIG. 1 according to another embodiment of the present invention.

9 is an enlarged view of a main portion of a portion D of FIG. 8.

10 is a view showing a flow of fluid generated at the inlet of a plate-shaped distributor stacked in an asymmetric structure according to another embodiment of the present invention.

Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the accompanying drawings.

1 to 10 are views showing a heat exchanger according to the present invention and a plate-shaped distributor provided in the heat exchanger, respectively.

1 and 2, the first and

second cover plates

110 and 120 and the first and second cover plates 110 provided on the outermost sides, respectively, as shown in FIGS. 1 and 2. It includes a plurality of

distributors

130 and 140 are provided to be stacked between (120).

Here, for convenience of explanation, the reference numerals of the distributor 130 positioned at the top and the distributor 140 positioned at the bottom among the plurality of distributors are differently assigned to distinguish them.

The first and

second cover plates

110 and 120 are generally rectangular flat plates, and a plurality of inlet portions 170 through which refrigerant and a heated fluid are respectively introduced and discharged at each corner of the first cover plate 110 ( 180) and the

outlet portions

171 and 181 are formed, and the inlet portion and the outlet portion are not formed in the second cover plate 120.

Therefore, the refrigerant flowing into the

inlet parts

170 and 180 of the first cover plate 110 and the fluid to be heated flow into and flow into different layers of the stacked distributor, respectively, and then exit the first cover plate 110. It is discharged through the

parts

171 and 181, respectively.

At this time, the

inlet portions

170 and 180 formed in the first cover plate 110 are formed to be spaced apart in the diagonal direction, and the

outlet portions

171 and 181 are also spaced apart in the diagonal direction. The

flow paths

150 and 160 between the plate-

shaped distributors

130 and 140 to be described later (herein referred to as "flow paths") refer to the refrigerant flow path through which the refrigerant flows and the fluid flow path through which the fluid to be heated flows. In the following, the fluid flowing through the refrigerant flow path and the fluid flow path to be heated) will be moved along the direction of the

sebron portions

131 and 141 of the

distributors

130 and 140. It is prepared to match.

That is, the

flow paths

150 and 160 between each of the

stacked distributors

130 and 140 are closed flow paths that do not communicate with each other, and the refrigerant flowing through the

flow paths

150 and 160 of each layer and the fluid to be heated are flown. By allowing them to flow in directions facing each other, it is possible to maximize heat exchange efficiency.

In addition, a separate reinforcement plate for reinforcing the strength of the first and

second cover plates

110 and 120 is provided on the inner surface of the first and

second cover plates

110 and 120 facing the

distributors

130 and 140. Each may be provided.

The reinforcing plate may be formed of the same rectangular flat plate as the first and

second cover plates

110 and 120, and the first cover plate 110 may be provided in the reinforcing plate provided on the first cover plate 110 side of the reinforcing plate. ), the

inlet portion

170, 180 and the

outlet portion

171, 181 are formed in the same way, and the reinforcing plate provided on the second cover plate 120 side is the same as the second cover plate 120. It is preferable that the part and the outlet part are not formed.

On the other hand, the refrigerant flowing through each of the

inlets

170 and 180 of the first cover plate 110 and the fluid to be heated are each distributor 130 stacked between the first and second cover plates 110 and 120. ) Flows between the

flow paths

150 and 160 between 140 and

flow paths

150 and 160 between each of the

distributors

130 and 140, respectively, as shown in FIG. 3, and the refrigerant flow path 150 on the left side. The right-to-be-heated fluid flow path 160 (or even-numbered and odd-numbered flow paths) are formed so as not to communicate with each other, so that the refrigerant and the heated fluid do not mix with each other and each

flow path

150 and 160 between the

distributors

130 and 140 And heat exchange while flowing.

And, as described above, the

distributors

130 and 140 provided to be stacked between the first and

second cover plates

110 and 120, like the first and

second cover plates

110 and 120, have a regular rectangular flat plate. It is formed, and the inlet portion and the outlet portion corresponding to the

inlet portion

170, 180 and the

outlet portion

171, 181 of the first cover plate 110 are formed in each corner portion. On the other hand, in the description of the inlet and outlet portions formed on the

distributors

130 and 140 stacked as described above, the

inlet portions

170 and 180 and the outlet portions 171 formed on the first cover plate 110 will be described below. It will be described by giving the same drawing number as (181).

As shown in FIGS. 4 and 5, each distributor 130 is provided at the inlet 170 and outlet 171 through which refrigerant flows among the inlet and outlet of the

distributors

130 and 140 provided to be stacked as described above. The

inclined portions

133 and 143 respectively inclined in the vertical direction from the

flat portions

132 and 142 of the 140 are formed, and the inner peripheral portions of the

inclined portions

133 and 143 are formed to be flat and bonded to each other. The

joints

134 and 144 to be formed are formed.

The inner periphery of the

junction

134 and 144 is formed as an inlet and an outlet, and the

inclined portions

133 and 143 have a plurality of

entrance holes

170a and 171a, which are the circumferences of the

inclined portions

133 and 143. It can be formed at regular intervals in the direction.

On the other hand, as a preferred embodiment of such an entrance hole (170a) (171a), the inclined portion (133) (143) from the central portion of the

distributor

130, 140, that is, from one side toward the sevron portion (131) (141) It is more preferable to arrange and provide

more entrance holes

170a and 171a on the other side toward the edge portion of the

distributor

130, 140, that is, the corner portion. This is because most of the vaporized refrigerant introduced into the refrigerant passage 150 flows directly into the central portion of the

distributors

130 and 140 and then flows out, so that the heat exchange efficiency is relatively lower than the edge portion of the

distributor

130 and 140. This is to achieve even heat exchange efficiency by allowing a large amount of refrigerant to flow in.

In particular, the refrigerant is supplied in a liquefied state due to the pressure and temperature rising due to the supply pressure by the pressurization of the pump, and the refrigerant supplied in this way is a

stacked distributor

130, 140 in the conventional case where there is no access hole 170a ) Is calculated and supplied as the required amount of input from the inlet portion 170, and thus, when such a liquefied refrigerant flows into the inlet portion 170 of the

stacked distributors

130 and 140, a large area of the inlet portion 170 It is vaporized under reduced pressure. As described above, the refrigerant vaporized at the inlet 170 flows differently in pressure and flow rate for each layer, so that the diffusion rate of the refrigerant flowing through the refrigerant passage 150 of each layer decreases, resulting in low heat exchange efficiency. Moreover, since most of the refrigerant supplied to the refrigerant passage 150 flows only to the central portion and only a relatively small amount flows to the edge side, an imbalance of heat exchange is caused.

Therefore, in the present invention, in order to improve this point, a plurality of entrance holes 170a are formed in the

inclined portions

133 and 143 of each inlet portion 170 of the

stacked distributors

130 and 140 to be stacked. By supplying the refrigerant in the liquefied state flowing into the inlet 170 of the distributed

distributors

130 and 140 into the refrigerant passage 150 through the entrance holes 170a of each layer to vaporize the refrigerant, the refrigerant is stacked in each layer. It is to quickly supply the refrigerant flow path (150).

In addition, it is to solve the imbalance of heat exchange by arranging more of the entrance hole 170a at the edge portion than the central portion of the

distributors

130 and 140.

That is, when the pump pressurizes and supplies the refrigerant calculated as the required amount of input in the exit hole 170a formed in each layer of the

stacked distributors

130 and 140, the refrigerant in the liquefied state is the

distributor

130 and 140 It is supplied as it is in a liquefied state without phase change to the inlet part 170 of the, and the refrigerant in the liquefied state thus supplied is of each layer through the entrance hole 170a formed in the inlet part of each layer due to the supply pressure of the pump. It is supplied to the refrigerant passage 150, and after being supplied to the refrigerant passage 150, a reduced pressure is generated due to the large area of the refrigerant passage 150 and is vaporized at the same time as the supply.

Accordingly, the vaporized refrigerant is rapidly diffused and spread throughout the refrigerant flow path 150 as a vaporized state, as shown in FIG. 7, thereby improving heat exchange efficiency, and a relatively large amount of refrigerant is supplied to the edge portion to exchange heat. The imbalance can be resolved.

As described above, the refrigerant in the vaporized state flowing through the refrigerant flow path 150 is discharged through the exit hole 171a on the side of the outlet portion 171 to the outside through the outlet portion 171 of the

stacked distributors

130 and 140. Is discharged.

In addition, although the inlet portion 170 and the outlet portion 171 through which the fluid to be heated flows may be formed as the inlet and outlet portions through which the refrigerant flows, the fluid to be heated flows in this embodiment due to the characteristics of the fluid to be heated. 6, the inlet 180 and the outlet 181 will be described by exemplifying a structure in which an entrance hole is not formed.

As a result, the refrigerant flows only through the refrigerant passage 150 through the inlet portion 170 and the entrance hole 170a formed in the

distributor

130 and 140 stacked as in FIGS. 4 and 5, and then in FIG. 5. Likewise, the fluid to be heated is discharged to the outlet 171 through the entrance hole 171a, and the fluid to be heated is heated through the inlet 180 of the

distributor

130, 140 as shown in FIGS. 4 and 6. ), while being heat exchanged with the vaporized refrigerant while flowing only, is discharged to the outlet 181 as shown in FIG. 6.

Further, on the surface of the

distributors

130 and 140 as described above, each of the

sebron portions

131 and 141 protruding in an uneven shape is formed, and the

sebron portions

131 and 141 are the distributors 130 2 and 3 based on the center line of the center of 140, the left and right sides of the

severon portions

131 and 141 are formed to be inclined from the center line side to the edge, so that the

severon portions

131 and 141 The entire shape is formed in a V-shape.

Therefore, the refrigerant or the fluid to be heated flowing through each of the

flow paths

150 and 160 between the upper and

lower distributors

130 and 140 flows and moves in the direction of the vertex of the V-shaped

sebron parts

131 and 141.

In particular, in the present invention, in consideration of the flow of the fluid, the direction of the upper and

lower distributors

130 and 140 stacked between the first and

second cover plates

110 and 120, the direction of the

Severon portion

131, 141 They are stacked by being alternately provided so as to be opposite to each other.

Then, between the stacked upper and

lower distributors

130 and 140,

flow paths

150 and 160 are formed by the

sebron portions

131 and 141, and each

flow path

150 and 160 is as shown in FIG. Each of the

inlet portion

170, 180 and the

outlet portion

171, 181 are formed in communication. Among them, the inlet portion 170 and the outlet portion 171 through which the refrigerant flows are formed to communicate with the refrigerant passage 150 through the

entrance holes

170a and 171a formed in the

inclined portions

133 and 143 thereof.

In addition, as shown in FIG. 4, the refrigerant passages 150 on the left and right sides based on the centers of the

distributors

130 and 140 are separated so as not to communicate with each other while having a height difference (phase difference). Is formed.

Therefore, based on FIG. 4, the refrigerant flowing into the left inlet 170 of the first cover plate 110 flows only through the refrigerant passage 150 located on the left, and flows into the right inlet 180 The fluid to be heated flows only the fluid fluid passage 160 on the right.

In addition, as another embodiment of the

distributors

130 and 140 stacked as described above, as shown in FIGS. 8 and 9, the

inlet

170, 180 and outlet of each distributor 130, 140 ( The

flat portions

132 and 142 which are bent outwardly from the 171 and 181 and are flatly extended are joined and provided as an asymmetric structure. 5 and 6, this structure is also configured on both sides of the

sebron portion

131, 141 formed between the

inlet portion

170 and 180 and the

outlet portion

171 and 181. desirable.

That is, the

inclined portions

133 and 143 and the

inclined portions

133 and 143 are formed to be bent upward or downward from both ends of the

inlet portions

170 and 180 and the

outlet portions

171 and 181.

Flat portions

132 and 142 are formed to extend outwardly from the ends of the.

The

flat portions

132 and 142 are provided with the

flat portions

132 and 142 of the

distributors

130 and 140 stacked up and down in contact with each other, and the flat portions of the

stacked distributors

130 and 140 are stacked ( 132) (142) length (L1) (L2) is formed in a different length as shown in Figure 9 is joined.

The

flat portions

132 and 142 of the

distributors

130 and 140 that are joined in this way will be described in more detail with reference to FIG. 9, the flow path 150 formed by the

stacked distributors

130 and 140. On the basis of 160, the flat portion 142 length L1 of the lower distributor 140 is formed shorter than the length L2 of the flat portion 132 of the upper distributor 130, so that the lower distributor 140 Since the flat portion 142 is provided to protrude toward the

flow path

150 and 160, an extended region 135 extending toward the inclined portion 133 of the upper distributor 130 is formed in the

flow path

150 and 160.

Accordingly, the refrigerant and the fluid to be heated flowing through the

flow paths

150 and 160 by the expansion region 135 formed as described above flow through the

flow paths

150 and 160 in the vortex flow, respectively, thereby cooling the refrigerant and the fluid to be heated. Is distributed quickly and evenly so that it can flow.

In particular, the flat portion 142 of the lower distributor 140 as described above and the flat portion 132 of the upper distributor 130 are preferably formed at a ratio of 1:1.1 to 1.3.

This is, if the ratio of the flat portion 142 of the lower distributor 140 to the flat portion 132 of the upper distributor 130 is less than 1.1, the vortex effect of the fluid in the

flow path

150 and 160 is insufficient, and the fluid is even. Dispensing cannot be expected, and if it exceeds 1.3, the area of the

flow paths

150 and 160 is relatively narrow compared to the expansion area 135, thereby preventing the overall flow of the fluid.

Therefore, it is best that the flat portion 142 of the lower distributor 140 and the flat portion 132 of the upper distributor 130 are formed in a ratio of 1:1.2.

In addition, the inlet portion 170 and the outlet portion 171 side adjacent to the refrigerant flow path 150 are configured in a symmetrical structure in which the flow path side is turned upside down, as shown in FIG. 9.

Accordingly, since the inclined portion 143 of the lower distributor 140 enters the

flow path

150 and 160 more than the inclined portion 133 of the upper distributor 130, the inlet portion 170 and the outlet portion 171 On the side, an extended region 145 extending toward the inclined portion 143 of the lower distributor 140 is formed.

Accordingly, the refrigerant flowing through the inlet portion 170 and the outlet portion 171 also flows in a vortex flow as in the

flow paths

150 and 160, so that the fluid is rapidly and evenly distributed and supplied.

On the other hand, in the case of the inlet portion 170 and the outlet portion 171, the length ratio between the upper and lower

flat portions

132 and 142 as in the

flow paths

150 and 160 is not described in detail, but the flow path 150 Given the symmetrical relationship with the structure of the

flat parts

132 and 142 of 160, the length L1 of the

flat parts

132 and 142 forming the extended area 135 in the flow path 150 and 160 ) (L2) ratio and the length ratio between the

flat portions

132 and 142 forming the extended area 145 in the inlet portion 170 and the outlet portion 171 can be seen to have an organic relationship.

In addition, although not illustrated in the present embodiment, the fluid flow path 160 to be heated may also be configured in the same structure as the refrigerant flow path 150 described above.

Therefore, in the heat exchanger 100 formed as described above, when the refrigerant and the fluid to be heated flow into each of the

inlets

170 and 180, the refrigerant and the fluid to be heated flow through the

inlets

170 and 180, respectively. Quickly and evenly flows to the lowermost portion of the

stacked distributors

130 and 140, and the introduced refrigerant and the fluid to be heated are rapidly flowed into each

flow path

150 and 160 as shown by the arrows shown on the right side of FIG. While being supplied, it can be seen that the flow of the vortex appears on the extended region 135 side of the

flow path

150 and 160.

As described above, the refrigerant flowing through the vortex and the fluid to be heated are rapidly and evenly diffused and flow through the

entire flow paths

150 and 160 of each layer, thereby balancing heat exchange efficiency over the entire area of the

distributors

130 and 140. Heat exchange performance is improved.

In this way, heat exchange efficiency and performance are improved as different fluids flowing through the

adjacent flow paths

150 and 160 exchange heat through the entire area of the

distributors

130 and 140 in the process of moving the fluid.

Although the present invention has been described in detail through specific examples, the present invention is specifically for describing the present invention, and the present invention is not limited to this, and by those skilled in the art within the technical spirit of the present invention. It is clear that the modification and improvement are possible.

All simple modifications or changes of the present invention belong to the scope of the present invention, and the specific protection scope of the present invention will be clarified by the appended claims.

(Explanation of codes)

100: heat exchanger 110,120: cover plate

130,140: Distributor 131,141: Severon

132,142: flat part 133,143: inclined part

134,144: connection 135,145: extended area

150,160: Euro 170,180: Entrance

171,181:

Exit

170a,171a: Entrance

L1,L2: Length of flat part

Claims

While the inlet and outlet portions are respectively formed so that the refrigerant and the fluid to be heated are allowed to enter and exit, a plurality of distributors, each of which has a severon portion formed of an uneven convex shape, is stacked between the first and second cover plates. As a heat exchanger,

An inclined portion is formed at the inlet portion of the distributor where the refrigerant flows in, so that the inlet portion of the stacked upper and lower distributors is joined, and a plurality of inlets and outlets through which refrigerant enters and exits is formed in the inclined portion, and the refrigerant introduced into the outlet is vaporized up and down A heat exchanger that is diffused and supplied to the flow path between distributors.
The method according to claim 1,

The heat exchanger in which the entrance hole is formed in a larger number on the other side of the inclined portion facing the edge than the one side of the inclined portion facing the central portion of the distributor.
The method according to claim 1,

A plurality of distributors to be stacked are provided with alternating stacked so that the elongated sebron parts face each other in opposite directions,

The stacked distributor is a heat exchanger that is provided to be stacked by asymmetrically contacting and flattening the flat portions that are bent outwardly from each of the sebron portions and extend flat.
The method according to claim 1,

An heat exchanger for generating a flow of vortices in a fluid flowing through the flow path by forming an extended extension region in the flow path between both sebron portions of the stacked distributor.
The method according to claim 4,

Heat exchangers where the flat parts of the stacked upper and lower distributors are formed and joined in different lengths.