KR101776849B1 - Air to air counterflow heat exchanger - Google Patents

Abstract

An air-to-air countercurrent heat exchanger is disclosed. The air-to-air heat exchanger according to the present invention is characterized in that a plurality of plates are sequentially stacked, wherein each of the plates has a header integrally formed with openings at both ends thereof, and heat exchange . At this time, a plurality of flow paths are arranged in parallel in the respective heat exchanging parts, and the header is formed with a partition wall in a section except the opening part, and the mutually opposing flow paths of the upper and lower adjacent plates are in contact with each other to form a channel. At this time, the flow path has an orthogonal trapezoidal shape in which at least a section of the section is opened without a long side.

Description

BACKGROUND ART Air to air counterflow heat exchanger

The present invention relates to an air-to-air countercurrent heat exchanger. And more particularly to a counter-current heat exchanger having a structure for effectively discharging condensed water and maintaining a uniform pressure inside a channel.

As shown in FIG. 1, the structure of a countercurrent heat exchanger having a triangular header in which channels are joined to both ends of a countercurrent section through a transition section is disclosed in WO1997002461 "Heat exchanger with improved configuration".

The air-to-air heat exchanger of the cellular type known by WO1997002461 is characterized in that the upper and lower channels are separated by a plurality of laminated profile plates to effect heat exchange effectively, and the confluence can be prevented by the partition walls.

EP0844454 "Counterflow heat exchanger" proposed a structure in which the upper and lower plates are opposed to each other to form a channel by improving the lamination method by laying flat plates above and below the profile plate. In this case, the number and types of parts constituting the heat exchanging element can be reduced and the economical efficiency can be improved.

However, since the cross section of the channel forms a circular shape, the condensed water occupies a wide section due to the tension when applied to the sensible heat exchanger, thereby causing a problem that the wet section increases greatly.

Korean Patent No. 10-0991946 entitled "Exhaust Heat Recovery Heat Exchanger" also discloses the shape of a heat exchanger having a circular channel cross-sectional structure.

Korean Patent No. 10-0991946 has a feature that a channel formed by contacting upper and lower plates opposed to each other has a shape of S rather than a straight line. In this case, a static pressure loss due to a difference in internal pressure by each section largely occurs.

Particularly, when the header section is designed to be short in order to increase the countercurrent section, there is a problem that the performance is deteriorated due to the difference in pressure and speed between the adjacent channels.

2 illustrates a cross-sectional shape of a channel of a conventional heat exchanger. WO1997002461 has a structure as illustrated in Fig. 2 (a), in which a large number of cellular type heat exchangers follow this cross-sectional structure.

By forming flat surfaces between the upper and lower profiles to form a heat transfer surface, a wide heat exchange area can be secured, but the performance is deteriorated by the condensed water as described above.

Particularly, when the channel is formed to have a dense structure in order to secure a heat exchange area, there is a problem that the wet portion due to the condensed water increases significantly.

EP0844454 and Korean Patent No. 10-0991946 have a sectional structure as shown in FIG. 2 (b). As described above, since the condensed water does not gather and spreads to occupy a large area, it can not be regarded as a sensible heat exchanger .

1. WO1997002461 "Heat exchanger with improved configuration" 2. EP0844454 "Counterflow heat exchanger" 3. Korean Patent No. 10-0991946 entitled "Exhaust Heat Recovery Heat Exchanger"

SUMMARY OF THE INVENTION It is an object of the present invention to provide a channel structure of a heat exchanger for minimizing static pressure loss and preventing heat exchange performance deterioration.

Another object of the present invention is to provide a channel structure for minimizing the wetting period by condensed water.

In order to accomplish the above object, an air-to-air countercurrent heat exchanger according to the present invention includes: a plurality of plates sequentially stacked, wherein each of the plates has a header integrally formed with openings at both ends thereof, And a heat exchange unit having side walls formed on both sides thereof.

At this time, a plurality of integrally formed flow paths are arranged in parallel in the interior of each heat exchanging portion.

The header is formed with a partition in a section except for the opening, the channels opposing each other in the upper and lower adjacent plates are in contact with each other to form a channel, and the openings of the upper and lower plates are provided opposite to each other.

At this time, the flow path has an orthogonal trapezoidal shape in which at least a section of the section is opened without a long side.

On the other hand, each flow path has a shape of a sinusoidal waveform having a constant amplitude.

The flow paths of the upper and lower adjacent plates are supported in close contact with each other, and have a sine waveform shape in which the start positions of the waves are different from each other.

Meanwhile, the header has an end partition at an end thereof in a direction perpendicular to a traveling direction of the flow path, and a slant partition wall connecting the end partition to one side wall is integrally formed.

On the other hand, openings that open from the end partition wall to the other side wall are formed to allow the airflow to flow in and out.

On the other hand, each plate has an angle formed by the heat exchanging portion and the oblique partition wall, and the angle formed by the heat exchanging portion and the openings 113 and 213 are equal to each other, preferably, 40 degrees and 50 degrees.

Each of the upper and lower adjacent plates has a structure in which the contact surfaces are bonded and sequentially laminated.

On the other hand, the channel cross-section of each plate is composed of a flat portion corresponding to the upper side of an orthogonal trapezoid and a sloped portion which is a variable side portion of the flat portion. Preferably, the flat portion is designed to be shorter than 20% .

According to the present invention, it is possible to minimize the static pressure loss by allowing the airflow flowing into the countercurrent section through the header to be diffused in the channel.

In addition, by adopting a hexagon cross-sectional structure with a truncated upper and lower ends, it minimizes the wetted area by the condensed water when compared with the inverted triangular shape and minimizes the wetted area by allowing the condensed water to gather at the corner when installed perpendicular to the gravity direction It is effective.

BRIEF DESCRIPTION OF THE DRAWINGS Figure 1 is a diagram illustrating the structure of a prior art air-to-air countercurrent heat exchanger,
2 is a diagram illustrating a channel configuration of a conventional air-to-air countercurrent heat exchanger,
3 is a view showing the shape of a plate of an air-to-air countercurrent heat exchanger according to the present invention,
4 is a diagram illustrating the external shape of an air-to-air countercurrent heat exchanger according to the present invention,
Fig. 5 is a view for comparing the structures of the flow paths of adjacent upper and lower plates,
6 is a view for explaining a cross-sectional structure of a channel according to a section,
Figure 7 compares the triangular channel structure and the heat exchange area,
8 is a view for explaining a condensed water generating section.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT Hereinafter, the present invention will be described in detail with reference to preferred embodiments of the present invention and the accompanying drawings, wherein like reference numerals refer to like elements.

It is to be understood that when an element is referred to as being "comprising" another element in the description of the invention or in the claims, it is not to be construed as being limited to only that element, And the like.

FIG. 3 is a view showing the shape of a plate of the air-to-air countercurrent heat exchanger according to the present invention, and FIG. 4 is a view illustrating the outline of the air-to-air countercurrent heat exchanger according to the present invention.

The air-to-air countercurrent heat exchanger according to the present invention is manufactured by sequentially stacking a plurality of plates 100 and 200 as illustrated in FIG.

The plates 100 and 200 include at least two plates 100 and 200 that are different from each other.

Each of the plates 100 and 200 basically has the same structure, but the flow direction and the discharge direction of the air flow are opposite to each other, and the shape of the flow path is different as described later.

In FIG. 3, the first plate 100, which is one of the two kinds of plates, will be described as an example.

3, the first plate 100 is provided with a header 110 at both ends thereof, and a heat exchanging unit 120 is provided between the pair of the headers 110. As shown in FIG.

The header 110 corresponds to a passage through which the airflow flows or flows. The header 110 flows into either one of the channels, passes through the heat exchange unit 120, and is heat-exchanged.

The first plate 100 and the second plates 200, which are different types of plates, are sequentially stacked. The air-to-air heat exchanger according to the present invention can be achieved by bonding and laminating the contact surfaces.

For this purpose, an extending portion (not shown) may be formed horizontally inward along the edges of the plates 100 and 200, so that the bonding process can be performed.

According to the prior art, in the manufacturing process, since lamination has to be performed by a high-frequency fusion bonding method, not only the process is complicated but also the upper and lower channels have the same shape, resulting in an uneconomical solution in which a film film is required to be laminated in every layer .

However, by using two types of plates 100 and 200 having the structure as illustrated in FIG. 3, it is possible to roll the adhesive on the upper surfaces of the plates 100 and 200, Can be produced.

Particularly, by making the cross-sectional structure of the channel into a trapezoidal shape as will be described later, flat portions 1211 and 2211 corresponding to the upper surface of the trapezoid are formed in the inclined portions 1212 and 1213 of the corresponding channels of the adjacent upper and lower plates 100 and 200, 2212 in contact with each other.

That is, the plurality of plates 100 and 200 can be laminated by the bonding method without adding a film film to each layer, and sufficient rigidity can be obtained.

On the other hand, side walls 122 and 222 are formed on both sides of the heat exchanging part 120 to prevent leakage.

By convention, the header usually has the shape of a triangle. In the present invention, the header 100 preferably has a regular trapezoidal shape.

However, if the length of the channel is designed to be long in order to maximize the heat exchanging area, the space to be allocated to the header 100 is reduced, and the flow angle of the airflow and the discharge angle are large There is a problem that it is lost.

That is, when a portion in contact with the heat exchanging portion 120 is referred to as a base, the planar shape of the header is not equal to a regular triangle, but the left and right lower chambers are close to a shape having a low height of less than 45 degrees, To avoid this, installation direction is restricted.

Accordingly, the present invention is characterized in that the header 100 has an orthogonal trapezoidal shape so that the angle from the end partition wall 112 vertically erected at both ends to the both side walls 122 of the heat exchange unit 120 is about 45 So that it can be designed to be close to the figure.

Preferably between 40 degrees and 50 degrees, so that the inflow and outflow angles of the airflow are gently maintained.

The end partition walls 112 at both ends of the header 100 are preferably perpendicular to the traveling direction of the flow path 121. In the section extending from the end partition wall 112 to one of the side walls 122, (111) are integrally formed.

The end partition wall 112 and the oblique partition wall 111 have the same height and the opening 113 is formed in the section leading to the other side wall 122 so that the airflow can be introduced and discharged.

As shown in FIG. 3, a plurality of flow paths 121 are arranged in parallel within the heat exchange unit 120.

The plate 100 is preferably manufactured by machining a single plate material (preferably a polymer material), and the plurality of channels 121 is formed by processing the plate material and protruding downward.

The channel 121 of the first plate 100 and the channel 221 of the second plate 200 adjacent to each other are in contact with each other to form the channel 300.

FIG. 5 is a view for comparing the structures of the channels of the adjacent upper and lower plates, and FIG. 6 is a view for explaining the cross-sectional structure of channels according to the sections.

5, the flow path 121 of the first plate 100 and the flow path 221 of the second plate 200 each have a planar shape close to a sinusoidal waveform.

That is, the flow paths 121 and 221 are elongated in the shape of a sinusoidal waveform having a constant wavelength and amplitude along the longitudinal direction of the heat exchange units 120 and 220, and the plurality of flow paths 121 and 221 are parallel .

5, the flow path 121 of the first plate 100 and the flow path 221 of the second plate 200 preferably have a planar shape of a sinusoidal waveform in which the start positions of the waves are different from each other .

That is, they are not symmetrical with respect to each other throughout the whole range, but have a shape which is offset from each other by a difference of about half wavelength.

6 (a) corresponds to a sectional view taken along the line a-a 'of FIG. 5. The flow path 121 of the first plate 100 and the flow path 221 of the second plate 200 which are shifted from each other are brought into contact with each other at half wavelengths and have a cross section as illustrated in FIG. 6 (a).

The channel 300 corresponds to a space between the flow path 121 of the first plate 100 and the flow path 221 of the second plate 200. In FIG. 6 (a), a plurality of mutually separated channels 300 ) Seems to exist.

However, as shown in FIG. 6 (b), the flow path 121 of the first plate 100 and the flow path 221 of the second plate 200 are staggered from each other to connect the spaces.

The airflow passing through the channel 300 can be diffused through the adjacent space, thereby improving the static pressure loss due to the pressure difference of the inlet air flow.

Meanwhile, a known heat exchanger as illustrated in FIG. 2 has a triangular or circular cross-section of a channel, and the condensed water occupies a wide section due to the tension.

In order to solve this problem, the channel 121 of the first plate 100 and the channel 221 of the second plate 200 are designed to have an orthogonal trapezoidal shape with their lower sides opened.

FIG. 7 is a diagram comparing the triangular channel structure with the heat exchange area.

The portion indicated by a dotted line in Fig. 7 corresponds to a virtual display of the heat transfer surface. In the case of laminating the heat transfer surface in the dotted line, the heat exchange area increases but the problem of the static pressure loss and the performance deterioration due to the condensed water occurs. Therefore, the heat transfer surface indicated by the dotted line is removed and the cross section is formed into the shape of an orthogonal trapezoid .

The flow passages 121 and 221 of the plates 100 and 200 can be compactly designed to compensate for the reduction of the heat exchange area due to the absence of the heat transfer surface.

That is, the ratio of the flat portions 1211 and 2211 corresponding to the upper side of the normal trapezoid to the inclined portions 1212 and 2212 on the left and right sides of the flat portions 1211 and 2211 is set to 1: Is designed to be less than 20% of the length of the inclined portions 1212 and 2212. By designing the acute angle between the inclined portions 1212 and 2212 to be less than 40 degrees, the heat exchange area can be sufficiently enlarged, It is possible to solve the problem of increase in the wet (wet) section due to condensed water as described later.

8 (a) illustrates a state where the heat exchanger according to the present invention is installed horizontally and condensed water is concentrated on the bottom of the channel due to gravity.

The area of the wet section is greatly reduced because the condensed water spreads laterally as compared with the case where the cross section of the channel is inverted triangular.

Meanwhile, FIG. 8 (b) illustrates a state where the heat exchanger according to the present invention is installed vertically and the condensed water is conveyed toward the bottom along each corner portion. The number of corners is large, and since there is no sharp acute angle, it is possible to prevent the wet section from extending due to the cohesive force of the condensed water.

In the above description, the first plate 100 is used as a reference, but the second plate 200, which is cross-laminated, has basically the same structure.

A pair of second header 210 and a second heat exchanger 220 are provided at positions corresponding to the first plate 100.

The second header 210 has a second diagonal barrier rib 211 on one side of the second end partition wall 212 and a second opening 213 on the opposite side and the second heat exchanger 220 has vertically A second side wall 222, and a plurality of second flow paths 221 therein.

4, the positions of the openings 113 and 213 are opposite to those of the first plate 100 and the second plate 200, and the flow paths 121 and 221 are opposed to each other, .

On the other hand, the flow paths 121 and 221 are configured to have a sinusoidal planar shape, preferably staggered so as to differ from each other by half the wavelength.

The technical idea of the present invention has been described through several embodiments.

It will be apparent to those skilled in the art that various changes and modifications may be made to the embodiments described above from the description of the present invention. Further, although not explicitly shown or described, those skilled in the art can make various modifications including the technical idea of the present invention from the description of the present invention Which is still within the scope of the present invention. The above-described embodiments described with reference to the accompanying drawings are for the purpose of illustrating the present invention, and the scope of the present invention is not limited to these embodiments.

The present invention is applicable to the field of heat exchanger technology.

1: Condensate
100: first plate
110: first header
111: first diagonal partition wall 112: first end partition wall
113: first opening
120: a first heat exchanger
121: First Euro
1211: first flat part 1212: first inclined part
122: first side wall
200: second plate
210: second header
211: second diagonal partition wall 212: second end partition wall
213: second opening
220: second heat exchanger
221: 2nd Euro
2211: second flat portion 2212: second inclined portion
222: second side wall
300: channel

Claims (7)

A plurality of plates (100, 200) are sequentially stacked,
Each of the plates has a header 110, 210 integrally formed with openings 113, 213 at both ends thereof,
Heat exchange units 120 and 220 having sidewalls 122 and 222 on both sides are provided between the pair of the headers 110 and 210,
A plurality of flow paths 121 and 221 are arranged in parallel within the respective heat exchanging sections 120 and 220,
The header 110 and 210 are formed with barrier ribs in a section except for the openings 113 and 213,
The channels (121, 221) opposed to each other of the upper and lower plates (100, 200) are in contact with each other to form a channel (300)
The openings 113 and 213 of the upper and lower adjacent plates 100 and 200 are provided in mutually opposite directions;

In order to improve the heat exchange efficiency by increasing the length of the channel 300 and minimize the static pressure loss of the air flow, the planar structures of the headers 110 and 210 have an orthogonal trapezoidal shape, End partition walls 112 and 212 are formed at the ends in the direction orthogonal to the traveling direction of the flow paths 121 and 221 and the diagonal partition walls 112 and 212 connecting the one side walls 122 and 222 from the end partition walls 112 and 212 111 and 211 are integrally formed and openings 113 and 213 which are opened from the end partition walls 112 and 212 to the other side walls 122 and 222 are formed,

In order to minimize the static pressure loss in the channel 300 and to minimize the wetted area of the condensed water, the planar shape of the flow paths 121 and 221 should have a sinusoidal waveform shape, , The flow paths (121, 221) overlap each other, and the sectional structures of the flow paths (121, 221) overlap each other continuously or symmetrically with each other,
The air flow passing through the channel 300 is diffused through the flow paths 121 and 221 connected to each other in a section where the sectional structures of the flow paths 121 and 221 are equal to each other, Loss is improved,
Wherein the upper and lower ends of the flow paths (121, 221) are symmetrical with respect to each other. delete delete delete delete The method according to claim 1,
Wherein each of the upper and lower adjacent plates (100, 200) has a contact surface bonded and sequentially laminated. delete

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