Heat exchanger and air treatment device

Abstract

Provided are a heat exchanger and an air treatment device. A heat exchanger according to the present invention includes a plurality of core fins and a plurality of films. The core fins and the films are alternately layered and form an airflow passage. The plurality of core fins include first core fins and second core fins, the airflow passage being formed between the first and second core fins. The airflow passage is provided with two port sections that are disposed facing each other. One of the port sections is an inlet section, and the other of the port sections is an outlet section. An airflow flows from the inlet section to the outlet section along an airflow direction. At least the outermost-side height of at least one of the port sections in the layering direction of the first and second core fins is greater than the height at other positions between the inlet section and the outlet section of the airflow passage. Using the heat exchanger according to the present invention reduces the resistance occurring when the airflow enters the heat exchanger and results in a smoother flow in the airflow. Thus, as a result of an increase in flow speed inside the heat exchanger, the heat exchange efficiency of the heat exchanger is improved.

Description

Technical Field

[0001] The present invention relates to the technical field of air treatment and conditioning, and particularly to an air treatment device using a heat exchanger.

Background Art

[0002] Conventional air treatment devices generally include a heat exchanger, which is configured to allow indoor exhaust air and fresh air to flow through the heat exchanger so that they cross each other. When the airflows in the two paths cross and flow, a heat transfer phenomenon occurs, causing a total heat exchange process. In a general heat exchanger, a core with a hexagonal structure in which core fins and membranes are alternately laminated is used, and it is provided with two sets of port parts. One set of port parts is usually used for flowing indoor exhaust air, and the other set of port parts is used for flowing fresh air. The airflows in the two paths perform heat exchange through the membrane in the heat exchanger.

Summary of the Invention

Problems to be Solved by the Invention

[0003] Each core fin is integrally formed of a resin material, and the membrane can be a paper membrane or a plastic membrane. However, in the process of using a conventional heat exchanger, it has been found that the conventional heat exchanger has a large pressure loss and it is difficult to effectively increase the intake air volume, thereby restricting the heat exchange efficiency of the heat exchanger.

[0004] In addition, the inventor has found that due to the action of the airflow, the membrane in the conventional heat exchanger deforms into a concave or convex shape between two adjacent partition ribs, further increasing the ventilation resistance, reducing the heat exchange efficiency of the heat exchanger, and when the membrane deforms over a long period of time, it causes damage to the membrane, and thus affects the life of the heat exchanger.

[0005] Therefore, it is necessary to improve the conventional heat exchanger.

Means for Solving the Problems

[0006] In order to overcome the deficiencies of the prior art, the present invention includes a plurality of core fins and a plurality of membranes. The plurality of membranes are respectively attached to one side surface of one core fin. The core fin and the membrane are alternately laminated to form an air flow passage. The plurality of core fins include a first core fin and a second core fin. The first core fin and the second core fin are laminated with each other to form an air flow passage therebetween. The air flow passage is provided with two port portions arranged opposite to each other. One of the port portions is an inlet portion, and the other is an outlet portion. The air flow is a heat exchanger that flows from the inlet portion to the outlet portion along the air flow direction. The first core fin and the second core fin respectively have a port side portion that laminates to form the port portion. In the lamination direction of the first core fin and the second core fin, at least the outermost fin layer distance of at least one of the port portions is larger than the fin layer distance at other positions between the inlet portion and the outlet portion of the air flow passage, and / or a port portion partition rib is provided on the port side portion of the second core fin. The port side portion of the first core fin has a surface that abuts against the port portion partition rib, and the width of the port portion partition rib is smaller than the width of the main partition rib extending between the port side portion of the port portion that is the inlet portion and the port side portion of the port portion that is the outlet portion.

[0007] According to the above technical solution, by expanding the fin layer distance at the port portion of the core fin or narrowing the width of the port portion partition rib, the area of the port portion can be increased, the pressure loss can be reduced, which helps to improve the air volume flowing through the port portion, and further helps to improve the heat exchange effect of the heat exchanger.

[0008] According to one aspect of the present invention, the first core fin and the second core fin respectively have a port side portion that laminates to form a port portion. The port side portion of the first core fin tapers outwardly in a cross-section parallel to the air flow direction.

[0009] When the above-described heat exchanger is used, the port portion of the air flow forms a flare shape toward the outermost side, reducing the resistance when the air flow enters or exits the heat exchanger, making the air flow smoother, and at the same time increasing the air volume. As a result, the flow velocity inside the heat exchanger is improved, thereby improving the heat exchange efficiency of the heat exchanger.

[0010] According to still another aspect of the present invention, a plurality of port portion partition ribs are provided on the surface of the port side edge of the second core fin facing the first core fin. The plurality of port portion partition ribs cooperate with the tapered port side edge of the first core fin to avoid the cross-flow of the air flow in adjacent flow paths, making the air flow distribution inside the heat exchanger uniform. Further, the port side edge can be supported by using the port portion partition ribs, which helps to improve the core fin strength.

[0011] According to still another aspect of the present invention, the surface of the port side edge of the first core fin facing the air flow path includes any one of an inclined surface, a curved surface, and a stepped surface, increasing the port area and at the same time guiding the air flow entering or exiting the heat exchanger, and reducing the air flow resistance.

[0012] According to still another aspect of the present invention, the outermost fin layer spacing at the inlet portion of the air flow path is larger than the fin layer spacing perpendicular to the air flow direction at other positions between the inlet portion and the outlet portion of the air flow path. The height of the inlet portion is the largest throughout the air flow path. As a result, the intake air volume of the heat exchanger can be increased, which helps to improve the overall heat exchange efficiency of the heat exchanger.

[0013] According to still another aspect of the present invention, the port portion includes a first end and a second end along the extending direction of the port side portion, and the length of the port portion partition rib closest to the first end among the plurality of port portion partition ribs of the second core fin is smaller than the lengths of the other port portion partition ribs. Thereby, it facilitates the smooth inflow or outflow of the air flow into or from the flow path near the first end, ensures that there is sufficient air volume in the flow path near the first end, makes the air flow inside the heat exchanger more uniform, and as a result, improves the heat exchange efficiency of the heat exchanger.

[0014] According to still another aspect of the present invention, the heat exchanger further includes a shell that houses a plurality of core fins and a plurality of membranes, the air flow path includes intersecting first and second flow paths, the first and second flow paths each have an inlet portion and an outlet portion, the inlet portion of the first flow path is adjacent to the outlet portion of the second flow path, while the inlet portion of the second flow path is adjacent to the outlet portion of the first flow path, and the shell is provided with baffles at positions adjacent to the inlet and outlet portions, and the baffles are folded back to form filter guide rails, and the length of the port portion partition rib at the position corresponding to the guide rail is smaller than the lengths of the remaining port portion partition ribs.

[0015] Providing a filter at the inlet portion helps to improve the cleanliness of the air flow entering the heat exchanger. The baffle can fix the core fins laminated as a part of the shell, improve the strength of the heat exchanger, and when the baffle is folded back to form a filter guide rail, it is easy to process, has a simple structure, and the filter is easy to attach and detach. The air flow rate at the end of the port portion is small with respect to the intermediate member of the port portion depending on the mounting structure or the arrangement position of the heat exchanger. Therefore, by providing the length of at least one end partition rib shorter than the other partition ribs in particular, it avoids the obstruction to the air flow caused by the baffle or the like, improves the intake air volume and the air supply volume of the port at the end portion, and in addition, can make the air flow inhaled and discharged from the port portion more uniform, which helps to improve the heat exchange efficiency of the heat exchanger.

[0016] According to another aspect of the present invention, a flow guiding portion having a shape for guiding the airflow along the advancing direction of the airflow is provided at the end of the partition rib. By providing the flow guiding portion, the airflow flowing into or out of the heat exchanger can be guided. As a result, the airflow resistance at the port portion is reduced, which helps to improve the air volume.

[0017] According to still another aspect of the present invention, the plurality of port portion partition ribs of the second core fin include alternately provided relatively short first port portion partition ribs and relatively long second port portion partition ribs. The port portion includes a first end and a second end along the extending direction of the port side portion. The port portion partition rib closest to the first end is the first port portion partition rib, which can further increase the area of the port portion and helps to increase the intake air volume and the air supply volume.

[0018] According to still another aspect of the present invention, the first core fin includes a first frame, the second core fin includes a second frame, and each of the first frame and the second frame includes a hexagonal outer frame, a main partition rib that basically extends from the inlet portion to the outlet portion along the airflow direction of the airflow passage, and two longitudinal ribs that extend across the airflow direction in the airflow passage and partition the outer frame into two triangular regions and a rectangular region located between the two triangular regions, and further includes auxiliary partition ribs that are basically parallel to the main partition rib within the rectangular region.

[0019] By providing the auxiliary partition ribs, an auxiliary protection effect can be exerted on the membrane, and it is possible to prevent the membrane from deforming under the action of the airflow, especially when the flow rate of the airflow increases. Thereby, the airflow resistance inside the heat exchanger is reduced.

[0020] According to still another aspect of the present invention, the distances between the auxiliary partition ribs and the adjacent main partition ribs on both sides are equal. Thereby, the airflow in the airflow passage becomes more uniform, and at the same time, it helps to improve the strength of the heat exchanger and the heat exchange efficiency.

[0021] According to yet another aspect of the present invention, the height of the secondary partition rib in the stacking direction is equal to or less than the height of the main partition rib. This prevents the film from deforming under the action of the air flow, while at the same time minimizing the extent to which the secondary partition rib occupies the air flow path, ensuring the air volume flowing through the heat exchanger.

[0022] According to yet another aspect of the present invention, the width of the main partition rib extending between the port side of the port portion serving as the inlet and the port side of the port portion serving as the outlet, on the side where the film is attached, is smaller than the width on the side away from the film. If the side of the partition rib close to the film is wider, the adhesion between the partition rib and the film is better. This not only helps to increase the sealing performance of the heat exchanger and reduce the risk of air flow leakage, but also minimizes the extent to which the secondary partition rib occupies the air flow path.

[0023] According to yet another aspect of the present invention, openings for the air flow to pass through are provided on the side of the main partition rib extending between the port side of the port portion serving as the inlet and the port side of the port portion serving as the outlet, away from the attached film. By providing the openings, it helps to increase the flow area of the air flow, resulting in an improvement in the air volume.

[0024] According to still another aspect of the present invention, the first core fin has a first frame, the second core fin has a second frame, the first frame and the second frame have the same contour shape laminated on each other, the port side edges of the first core fin and the port side edges of the second core fin are provided along a first portion and a second portion respectively arranged at the diagonals of each of the first frame and the second frame, the first frame and the second frame further each include a third portion and a fourth portion arranged diagonally, an intersecting port side edge is formed along the third portion and the fourth portion, a plurality of partition ribs are provided on the surface of the intersecting port side edge of the first frame opposite to the second core fin, the intersecting port side edge of the second frame tapers outward in a cross section parallel to the air flow direction, or the width of the port portion partition rib of the intersecting port side edge of the first frame is smaller than the width of the main partition rib extending between the port side edge of the port portion which is the inlet portion and the port side edge of the port portion which is the outlet portion. The intersecting port side edge of the second frame includes a contour shape of any one of an inclined surface, a curved surface, and a stepped surface, and the contour shape and the partition rib of the port side edge of the second core fin are respectively formed on two side surfaces of the second frame, with a simple structure, which helps the processing efficiency of the heat exchanger by facilitating the lamination of the first core fin and the second core fin with each other.

[0025] The present invention includes a plurality of core fins and a plurality of membranes. The plurality of membranes are respectively attached to one side surface of one of the core fins. The core fins and the membranes are alternately laminated to form an air flow passage. The plurality of core fins include a first core fin and a second core fin. The first core fin and the second core fin are laminated with each other to form the air flow passage therebetween. The air flow passage is provided with two port portions arranged opposite to each other. One of the port portions is an inlet portion, and the other is an outlet portion. An air flow flows from the inlet portion to the outlet portion along the air flow direction. The heat exchanger is such that the first core fin and the second core fin each have a main partition rib extending between the two opposite port portions. The first core fin and the second core fin each have a port side portion that is laminated to form the port portion. A port portion partition rib is provided on the port side portion of the first core fin or the second core fin. The width of the port portion partition rib is smaller than the width of the main partition rib, thereby further providing a heat exchanger that increases the flow rate of the air flow entering the port portion.

[0026] Moreover, the present invention is an air treatment device including a fresh air inlet, an air supply port, a return air port, and an exhaust port, and further includes the heat exchanger according to the above-described solution. The port portion of the heat exchanger includes a first inlet portion, a first outlet portion, a second inlet portion, and a second outlet portion. The fresh air inlet communicates with the first inlet portion to introduce fresh air flow. The air supply port communicates with the first outlet portion to send out fresh air flow. The return air port communicates with the second inlet portion to introduce indoor air flow. The exhaust port communicates with the second outlet portion to send out indoor air flow. The fresh air flow and the indoor air flow cross each other and flow through the heat exchanger to perform heat exchange, further providing an air treatment device. The heat exchanger is one of the core components of the air treatment device. When the heat exchanger according to the present invention is used, the overall processing efficiency of the air treatment device is improved.

[0027] When the above-described heat exchanger is used, the port portion of the air flow forms a flare shape toward the outermost side or the partition ribs of the port portion are narrowed, so that the resistance when the air flow enters the heat exchanger is reduced, the flow of the air flow becomes smoother, and at the same time, the amount of air flowing into or out of the heat exchanger is improved. By improving the flow velocity inside the heat exchanger, the heat exchange efficiency of the heat exchanger is improved.

[0028] When the frame structure of the core fin according to the present invention is used, the film in the heat exchanger can be reliably protected and supported, and by preventing the film from deforming under the action of the air flow, it is avoided that the flow of the air flow inside the heat exchanger is inhibited due to the deformation of the film, and it is avoided that the film is damaged due to the long-term deformation of the film, which helps to extend the service life of the heat exchanger.

Brief Description of the Drawings

[0029]

Figure 1

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Figure 19

Mode for Carrying Out the Invention

[0030] Hereinafter, the present invention will be further described with reference to specific examples and drawings. In the following description, although the present invention is easy to understand with more details for explanation, it is obvious that the present invention can be implemented in various other forms different from the description here. Since those skilled in the art can perform similar promotion and deduction according to the actual application situation without departing from the content of the present invention, the protection scope of the present invention should not be limited by the content of this specific example.

[0031] As shown in FIG. 19, two heat exchangers 1 are attached to the middle part of the air treatment apparatus 100. According to the size of the air treatment apparatus, one heat exchanger 1 may be provided, or a plurality of heat exchangers 1 may be provided. Usually, for an air treatment apparatus provided with one heat exchanger 1 in the machine, in order to facilitate the attachment and detachment of the heat exchanger 1, a maintenance port can be provided on the side surface of the equipment case. For an air treatment apparatus provided with a plurality of heat exchangers 1 in the machine, in order to attach and detach the heat exchanger 1, a maintenance port can also be provided on the side surface of the equipment case, or a maintenance port can be provided on the bottom plate of the apparatus to attach and detach the heat exchanger 1 from below. For the air treatment apparatus 100 provided with a plurality of heat exchangers 1, the adjacent heat exchangers 1 are connected by a sealing material, so that the leakage of the air flow in the apparatus can be reduced.

[0032] FIG. 1 shows a perspective view of a heat exchanger 1 according to a preferred embodiment of the present invention applicable to an air treatment apparatus 100. The heat exchanger 1 is formed by laminating a plurality of core fins and a plurality of membranes. Each core fin and each membrane have the same shape. After the core fins and the membranes are laminated, the heat exchanger 1 forms a hexagonal prism shape as shown in FIGS. 1 and 19. Since one membrane is interposed between two adjacent core fins, the space between the two membranes constitutes an air flow passage that allows air flow to pass through. The shapes of the core fins and the membranes may also be any of rectangular, square, and rhombic shapes.

[0033] In a preferred embodiment, the heat exchanger 1 is a heat exchanger 1 having intersecting air flow passages. That is, the heat exchanger 1 has two sets of inlet and outlet portions so as to form two different air flow paths. Specifically, the hexagonal column-shaped heat exchanger 1 shown in FIG. 1 has two long side surfaces and four short side surfaces. Here, by providing inlet and outlet portions on two pairs of short opposing side surfaces, respectively, two different air flow paths are constituted. One air flow path extends from the upper left corner to the lower right corner of the heat exchanger 1 shown in FIG. 1, and the other air flow path extends from the lower left corner to the upper right corner of the heat exchanger 1 shown in FIG. 1.

[0034] As shown in FIGS. 3 and 4 respectively, the core fins of the heat exchanger 1 forming intersecting air flow passages include a first core fin 10 and a second core fin 20 arranged adjacent to each other. As can be clearly seen from FIG. 14, a layer of membrane 30 is interposed between the two core fins 10 and 20.

[0035] The first core fin 10 and the second core fin 20 both have a hexagonal outer peripheral contour shape. As shown in FIGS. 3 and 4, in a preferred embodiment, each of the core fins 10, 20 has two opposite side surfaces, and has two long side edges 105, 106 and 205, 206, and four short side edges 101, 102, 103, 104 and 201, 202, 203, 204. For the sake of clarity, as shown in FIGS. 3 and 4, the four short side edges of the first core fin 10 are shown as the first short side edge 101, the second short side edge 102, the third short side edge 103, and the fourth short side edge 104, and the four short side edges of the second core fin 20 are shown as the first short side edge 201, the second short side edge 202, the third short side edge 203, and the fourth short side edge 204. One of the two opposite side surfaces of each of the first core fin and the second core fin constitutes a surface to which the film 30 is attached.

[0036] When the first core fin 10 and the second core fin 20 are integrally laminated, the four short side edges 101, 102, 103, 104 and 201, 202, 203, 204 face each other in pairs, thereby forming two sets of port portions 50. Specifically, the first short side edges 101, 201 and the second short side edges 102, 202 of the two core fins 10, 20 form the first set of port portions 50, and the third short side edges 103, 203 and the fourth short side edges 104, 204 of the two core fins 10, 20 form the second set of port portions 50. Each set of port portions 50 has both an inlet portion and an outlet portion. Thus, in the heat exchanger 1 in which a plurality of first core fins 10 and a plurality of second core fins 20 are alternately laminated and a film 30 is interposed between the first core fin 10 and the second core fin 20, two paths of air flow channels can be formed. The air flow channel of the first path communicates from the first short side edges 101, 201 to the second short side edges 102, 202, and the air flow channel of the second path communicates from the third short side edges 103, 203 to the fourth short side edges 104, 204.

[0037] When the above heat exchanger 1 is used in the air handling unit 100, the air flow path of the first path may be an air flow path for guiding fresh air, and the second air flow path is an air flow path for guiding indoor air. Usually, by the fresh air fan provided in the air handling unit 100, the fresh air flow is guided from the fresh air inlet 110 of the air handling unit along the first air flow path through the heat exchanger 1 to the air supply port 120, and at the same time, by the exhaust fan provided in the air handling unit 100, the indoor air flow is guided from the return air inlet 130 of the air handling unit 100 along the second air flow path through the heat exchanger 1 to the exhaust port 140. The fresh air flow and the exhaust air flow flow through the heat exchanger 1 between the core fins 10 and 20 along paths that cross each other, so as to effect heat exchange between the fresh air flow and the indoor air flow in the heat exchanger 1.

[0038] Each short side of the first core fin 10 and the second core fin 20 has either the port side portion 51 or the corresponding port side portion 52. When the first core fin 10 and the second core fin 20 are stacked, the corresponding port side portions 51 and 52 can form the port portion 50 used as the air flow path together, and only a pair of opposing short side port side portions 51 and 52 between two adjacent first core fins and the second core fin 21 are arranged facing each other, whereby the port portion 50 can be formed. The other opposing short side port side portions are provided back to back with each other, so they do not form the port portion 50, but are sealed and bonded to form a seal portion.

[0039] FIG. 2 shows a single port portion 50 formed by laminating two core fins 10 and 20 facing each other. During use, the port portion 50 may serve as an inlet portion of the air flow or an outlet portion of the air flow. In particular, in the lamination direction of the first core fin 10 and the second core fin 20 (i.e., the thickness direction of the first core fin 10 and the second core fin 20), the fin layer spacing of at least the outermost fins of the port portion 50 is larger than the fin layer spacing at other positions of the air flow passage between two port portions 50 used in pairs. The fin layer spacing between the first core fin 10 and the second core fin 20 refers to the height distance through which the air flow can flow between the two core fins 10 and 20 in the lamination direction of both the first core fin 10 and the second core fin 20. That is, as a cross section perpendicular to the air flow direction, the portion with the largest height dimension of the cross section is located on the outermost side of the port portion 50. The port portion 50 that expands toward the outermost side can minimize the resistance for the air flow to enter the heat exchanger 1 and improve the flow rate of the air flow entering the air flow passage. Thereby, the operating efficiency of the heat exchanger 1 is improved.

[0040] FIG. 14 shows a schematic cross-sectional view of the port portion 50 formed by the port side portions 51 and 52 of the pair of the first core fin 10 and the second core fin 20, and the cross section is cut basically parallel to the air flow direction of the air flow passage. As can be seen from FIG. 14, the inclined surface 510 of the port side portion of the first core fin 10 and the parallel surface 520 of the port side portion of the second core fin 20 surround to form the port portion 50. The port portion 50 has the largest height dimension h on the outermost side, preferably, for example, 2 mm to 4 mm, more preferably 3 mm. In the middle portion of the air flow passage at the rear side of the port portion 50, the height dimension of the air flow passage is 1 to 2 mm, preferably 1.5 mm. In this way, the air flow in the air flow passage can perform full-surface heat exchange with the air flow passages on both sides of the air flow passage through the films on both sides of the air flow passage, and the performance of the heat exchanger is high.

[0041] As shown in FIG. 5, the first core fin 10 has a port side portion 51 that forms the port portion 50, and the port side portion 51 tapers toward the outermost side in a cross section parallel to the air flow direction. That is, the two surfaces of the port side portion 51 of the first core fin 10 are not parallel, and one of the surfaces that face each other to form the port portion 50 is disposed obliquely. In other words, at the port side portion 51 of the first core fin 10, the surface that forms the port portion 50 is inclined with respect to the plane direction in which the first core fin 10 is located. In this way, while increasing the cross section of the port portion 50, the angle between the port side portion 51 and the air flow flowing in from the ventilation opening of the air treatment device can be decreased, and the obstruction of the air flow can be reduced. As shown in FIG. 6, the second core fin 20 has a port side portion 52 that forms the port portion 50, and a plurality of partition ribs 521 are provided on the surface of the port side portion 52 that forms the port portion 50. Among them, the surface of the port side portion 52 that forms the port portion 50 is basically parallel to the plane in which the second core fin 20 is located. When the first core fin 10 and the second core fin 20 are stacked, the partition rib 521 abuts against the inclined surface 510 of the first core fin 10, and the inclined surface 510 of the first core fin 10 and the parallel surface 520 of the second core fin surround to form the port portion 50. The partition rib 521 is supported between the inclined surface 510 and the parallel surface 520. The partition rib 521' partitions the air flow path together with the partition rib 521, improves the uniformity of the air flow, and at the same time, can be used to support the port side portion 51, which helps to improve the strength of the heat exchanger 1.

[0042] As shown in FIG. 5, the surface of the port side portion 51 of the first core fin 10 facing the air flow path includes an inclined slope contour shape and has a tapered cross section toward the outermost side of the port portion 50. It should be understood that the inclined surface can alternatively use a curved surface or a stepped surface, as long as it has the largest height dimension at the outermost side of the port portion 50.

[0043] As shown in FIG. 1, a heat exchanger 1 formed by laminating a first core fin 10, a second core fin 20, and a film 30 further includes a shell, and the core fins 10, 20, and the film 30 are accommodated in the shell 70. The shell 70 of the heat exchanger 1 is attached, for example, in an air conditioning device via a guide rail formed by folding back a baffle plate 60. Preferably, the length of one partition rib closest to the guide rail in the port portion 50 is smaller than the lengths of the remaining partition ribs in the port portion 50. In this way, the air flow can smoothly flow into the flow path close to the guide rail. Thereby, the influence on the intake and exhaust flow rates at the local position of the port portion 50 by the guide rail can be minimized. As shown in FIG. 6, the leftmost partition rib 521' slightly extends on the parallel surface 520 of the port portion 50, and the remaining partition ribs basically extend over the entire parallel surface 520 of the port portion 50.

[0044] In one alternative embodiment, the short partition ribs 521' and the long partition ribs 521 are arranged alternately, and as shown in FIG. 8, among them, the partition rib at one end of the port portion 50 closest to the guide rail is the short partition rib 521'. In this way, the flow area of the port portion can be further increased.

[0045] According to a preferred embodiment of the present invention, as shown in FIG. 9, flow guiding portions 523 and 523' can be provided on the partition ribs 521 and 521' at the port side portion 52, and the flow guiding portions 523 and 523' have a shape that guides the air flow along the advancing direction of the air flow. When the heat exchanger 1 is arranged in an air treatment device 100 as shown in FIG. 19, the air flow enters from the fresh air inlet 110 or the return air inlet 130 along a substantially parallel direction. Usually, the direction in which the air flow enters is substantially parallel to the upper plate and the bottom plate of the housing of the device 100. At this time, the flow guiding portions 523 and 523' of the partition ribs 521 and 521' are formed to have a shape that guides the air flow along the parallel air flow direction.

[0046] Regarding the short partition rib 521’, the air guiding part 523’ includes an inclined surface provided at the tip of the partition rib 521’, is arranged inclined to the parallel surface of the port side part 52, and compared with the tip being a vertical surface, the inclined surface can reduce the angle with the airflow flowing in parallel to the ventilation opening of the air treatment device, further reduce the interference of the airflow, and reduce the pressure loss. Regarding the long partition rib 521, the air guiding part 523 thereon includes a curved part that makes the tip of the partition rib 521 face the airflow entering direction, guides the airflow flowing in parallel to the ventilation opening of the air treatment device, reduces the interference of the airflow, and can reduce the pressure loss.

[0047] In a preferred embodiment, the outermost height of the inlet part of the air flow passage formed by laminating the first core fin 10 and the second core fin 20 is configured to be larger than the fin layer spacing in the direction perpendicular to the air flow direction at other positions between the inlet part and the outlet part of the air flow passage. Thereby, by improving the flow rate flowing into the air flow passage of the heat exchanger, the heat exchange efficiency of the heat exchanger is improved.

[0048] Regarding the first and second core fins 10 and 20 having hexagons shown in FIGS. 3 and 4, the first core fin 10 and the second core fin 20 each have first, second, third, and fourth short sides 101, 102, 103, 104 and 201, 202, 203, 204. In a preferred embodiment, the port side portions of the first and second short sides 101 and 102 of the first core fin 10 are port side portions 51 having inclined surfaces, and the port side portions of the first and second short sides 201 and 202 of the second core fin 20 are port side portions 52 having partition ribs. When the partition ribs 521 of the first and second short sides 201 and 203 of the second core fin 20 contact the inclined surfaces 510 of the first and second short sides 101 and 102 of the first core fin 10, a port portion 50 is formed by the first and second short sides 101, 201, 102, and 202. When forming the port portion 50 by the first short side and the second short side, the port side portions 51 and 52 of the third short sides 102 and 202 and the fourth short sides 104 and 204 of the first core fin 10 and the second core fin 20 are abutted and joined by the parallel surfaces on the back, and as shown in FIG. 14, the film 30 can be interposed between the two parallel surfaces, so that air flow does not flow through the third short side and the fourth short side.

[0049] In addition, port side portions 52 with partition ribs 521 are provided on the third and fourth short sides 103 and 104 of the first core fin 10, that is, they have the same structure as the port side portions 52 on the first and second short sides 201 and 202 of the second core fin 20, but the partition ribs 521 of the port side portions 52 on the third and fourth short sides 103 and 104 of the first core fin 10 are formed on the surface opposite to the inclined surface 510 where the first and second short sides 101 and 102 of the first core fin 10 are formed.

[0050] Correspondingly, port side portions 51 with inclined surfaces 510 are provided on the third and fourth short side edges 203 and 204 of the second core fin 20. That is, the port side portions 51 at the third and fourth short side edges 203 and 204 of the second core fin 20 have inclined surfaces 510, so that the port side portions 51 taper toward the outermost side of the port portion 50 in a cross section parallel to the air flow direction. However, the inclined surfaces are located on the surfaces opposite to the side surfaces where the partition ribs 521 of the second core fin 20 are formed.

[0051] In this way, when the inclined surfaces 510 of the port side portions 51 of the third and fourth short side edges 203 and 204 of the second core fin 20 face and abut against the partition ribs 521 of the port side portions 52 of the third and fourth short side edges 103 and 104 of the first core fin 10, port portions 50 of the cross-flow channels can be formed at the third and fourth short side edges.

[0052] Also, as can be seen from FIGS. 3 and 4, the frames of the hexagonal first core fin 10 and second core fin 20 include a hexagonal outer frame, and main partition ribs 15, 25 and vertical ribs 17, 27 located inside the outer frame. The main partition ribs 15, 25 extend between the side portions 51, 51 or 52, 52 of a set of two port portions along the air flow direction of the air flow passage. Preferably, the partition ribs 521 on the port side portions 52 of the first core fin 10 and the second core fin 20 and the main partition ribs 15, 25 are formed continuously. The vertical ribs 17, 27 are formed across the air flow direction in the air flow passage, so as to partition the hexagonal outer frame into two triangular regions and a rectangular region located between the two triangular regions. The vertical ribs connect the main partition ribs and the auxiliary partition ribs, help to improve the strength of the core fin, and further can prevent the film from deforming in the flow direction of the air flow.

[0053] According to a preferred embodiment, the square region of the core fin frame further has auxiliary partition ribs 16 and 26 that are basically parallel to the main partition ribs. These auxiliary partition ribs 16 and 26 extend from the longitudinal ribs 17 and 27 on one side of the square region to the longitudinal ribs 17 and 27 on the other side. Preferably, the distance from the auxiliary partition ribs 16 and 26 to the adjacent main partition ribs 15 and 25 on both sides is equal, so as to guide the airflow to pass through the heat exchanger more uniformly and effectively avoid the deformation of the membrane.

[0054] In order to better guide the airflow, a flow guiding portion 161 may be provided at the tips of the auxiliary partition ribs 16 and 26 adjacent to the longitudinal ribs 17 and 27. Taking the first core fin 10 as an example, as shown in FIGS. 10 and 11, the flow guiding portion 161 includes an end curved shape that curves along the bending direction of the longitudinal ribs 17 and 27, which helps to guide the airflow and reduce the obstruction of the airflow.

[0055] In order to better guide the airflow, as shown in FIGS. 3 and 4, the long sides 205 and 206 of the second core fin 20 and the long sides 105 and 106 of the first core fin 10 are each formed with curved surfaces 2051, 2061, 1051, and 1061 that are substantially parallel to the main partition ribs 15 and 25 near the port portion. In this way, the airflow in the flow path near the long side can be guided, the pressure loss can be reduced, and the obstruction of the airflow can be reduced.

[0056] In order to further improve the sealing performance of the heat exchanger 1, the membrane 30 may further be attached to the front side edges or partition ribs of adjacent core fins.

[0057] Pin holes 18 and 28 are further provided on the long sides of the first core fin 10 and the second core fin 20. The heat exchanger further includes a fixing column (not shown). In the processing process, the fixing column is fixed to a jig. First, the film is attached to the core fin, and then a plurality of first core fins 10 with the film 30 attached and second core fins 20 with the film 30 attached are alternately inserted into the fixing column through the pin holes 18 and 28 and tightly pressed together to form a core. It is also possible to alternately insert them into the fixing column in the way of one layer of film for one layer of core fin and tightly press them together to form a core.

[0058] Preferably, the contour shape of the film 30 is substantially the same as the contour shapes of the core fins 10 and 20, and the film 30 is also provided with through holes that fit with the fixing column. In this way, positioning can be performed using the fixing column to ensure alignment between the film 30 and the frames of the core fins 10 and 20, specifically, the convex surface 41 for film attachment, and avoid air flow leakage caused by the film being bent and attached.

[0059] Preferably, as shown in FIG. 17, in order to prevent air flow leakage in the pin holes 18 and 28 of the film 30, extension surfaces 181 and 281 can be provided at the edges of the pin holes of the core fin to ensure that the film is also in close contact with the core fin at the through holes.

[0060] Preferably, in order to improve the convenience of laminating the first core fin 10 and the second core fin 20, markers for the first core fin 10 and markers for the second core fin 20 can be provided on the front surface of the core fin respectively. The markers are, for example, numbers, figures, etc. Providing the markers not only helps to distinguish the first core fin 10 from the second core fin 20, but also helps to distinguish the front and back surfaces of the core fin, improving the convenience of processing.

[0061] Preferably, in order to improve the convenience of laminating the first core fin 10 and the second core fin 20, as shown in FIG. 18, positioning portions 14 and 24 that fit into each other can be provided on the frames of the first core fin 10 and the second core fin 20. By providing the positioning portions 14 and 24, the convenience of assembly can be improved. At the same time, by fitting the positioning portions 14 and 24 into each other, the sealing performance of the core can be improved.

[0062] Notches 19 and 29 are further provided at the edges of the first core fin 10 and the second core fin 20 (specifically, at the corner positions of the frame). After a plurality of core fins 10 and core fins 20 are tightly crimped by fixing posts, an adhesive (such as silica gel) can be injected into the notches 19 and 29 to further seal the core.

[0063] Next, as shown in FIG. 1, a shell 70 is provided around the core. In order to ensure the sealing performance of the heat exchanger and prevent air leakage, a sealing material is provided between the core and the shell 70.

[0064] Preferably, the longitudinal ribs 17 and 27, the main partition ribs 15 and 25, and the hexagonal outer frames of the first core fin 10 and the second core fin 20 have continuous and flat surfaces, which are usually called the back surfaces of the core fins. The film 30 is attached to the back surface by, for example, adhesion with an adhesive or hot melt. The front surfaces of the core fins 10 and 20 fit with the back surfaces of adjacent core fins. In an alternative embodiment, as shown in FIGS. 16A and 16B, a convex surface 41 can be formed on the back surface of the first core fin 10 and the second core fin 20 where the film 30 is attached, and a concave surface 42 is formed on the front surfaces of the first core fin 10 and the second core fin 20. After the film 30 is attached to the back surface by adhesion with an adhesive or hot melt and the core fin and the film are laminated integrally, the concave surface 42 and the convex surface 41 can fit with each other, thereby improving the sealing performance between the adjacent core fins 10 and 20 and the film 30.

[0065] The height dimensions of the vertical ribs 17 and 27 in the core fin stacking direction may be equal to or less than the height dimensions of the main and auxiliary partition ribs 16 and 26 in the core fin stacking direction.

[0066] In addition, pin holes 18 and 28 are further provided in the outer frames of the first core fin 10 and the second core fin 20. After stacking and assembling a plurality of core fins, fixing columns (not shown) can be drilled in the pin holes to fix the plurality of core fins. And, the sealing performance of the heat exchanger can be further improved. In addition, the pin holes can be further used to accurately position the core fins 10 and 20 relative to each other when installing. The partition ribs 15, 16, 25, and 26 in the air flow path between the first core fin 10 and the second core fin 20 may have a plurality of arrangement forms.

[0067] As shown in FIG. 12A, taking the first core fin 10 as an example, the heights of all the main and auxiliary partition ribs 15 and 16 in the core fin stacking direction of the core fin 10 are the same. In the installed state, one side of the main and auxiliary partition ribs is in contact with the film 30.

[0068] As shown in FIG. 12B, the height of the main partition rib 15' of the first core fin 10 in the core fin stacking direction is higher than the height of the auxiliary partition rib 16'. One ends of all the partition ribs are flush in a cross section perpendicular to the air flow direction, so that they are bonded to the film 30, and the other ends are alternately arranged with height differences. Thereby, deformation of the film can be effectively prevented, and at the same time, the area of the air flow path can be increased.

[0069] As shown in FIG. 12C, the height of the main partition rib 15'' is higher than the height of the auxiliary partition rib 16''. One ends of all the main partition ribs 15'' are flush for bonding to the film. However, the height position of the auxiliary partition rib 16'' is between the two ends of the main partition rib 15'', that is, in the installed state, the auxiliary partition rib 16'' is between two adjacent films 30, but does not directly contact either film 30. Deformation of the film can be effectively prevented, and at the same time, the area of the air flow path can be increased.

[0070] Also, as shown in FIGS. 13A and 13B, in a preferred embodiment, the width of the side end of the partition ribs 15, 16, 25, and 26 where the film is attached is smaller than the width of the side end of the partition ribs away from the film. Here, the width of the side end of the partition rib generally refers to the cross-sectional width in a plane perpendicular to the air flow direction of the partition ribs 15, 16, 25, and 26. Thereby, deformation of the film can be effectively prevented while increasing the area of the air flow path.

[0071] Furthermore, as shown in FIG. 13B, taking the first core fin 10 as an example, an opening 525 is provided on the side away from the film to which the partition rib 15 is attached for air flow to pass through. The opening 525 on the partition rib 15 may be serrated or wavy. Thereby, deformation of the film can be effectively prevented while increasing the area of the air flow path.

[0072] In a preferred embodiment of the present invention, the film 30 is preferably made of a plastic such as a polymer material. The film made of plastic is easy to clean and has a long service life. When the heat exchanger uses a plastic film, the heat exchanger is easy to clean with a liquid (for example, water). At this time, the structure of the enlarged port portion according to the present invention helps the cleaning liquid to enter deep into the heat exchanger and also helps to discharge the liquid from the heat exchanger. In particular, when the core fin has a tapered cross-sectional port side portion, the inclined surface of the port side portion helps to guide the cleaning liquid to flow into or out of the heat exchanger, thereby improving the cleaning effect and efficiently drying the heat exchanger. However, in an alternative embodiment, the material of the film may be paper.

[0073] In a preferred embodiment, the core fins 10, 20 have a hexagonal shape, and a port portion 50 is formed on the short side thereof. It should be understood that in other alternative embodiments, the hexagonal core fins may have equal-length sides. Also, in another alternative embodiment, the core fin may have other shapes, such as a quadrilateral, and the opposing sides of the quadrilateral form an air flow path in pairs.

[0074] FIG. 15 shows a schematic plan view of a core fin in a heat exchanger according to another preferred embodiment of the present invention. The core fin 10' schematically shows a port portion. The port portion 50' on one side of the core fin 10' can be used as an inlet portion, and the port portion 50' on the opposite side can be used as an outlet portion, and the air flow can flow from the inlet portion to the outlet portion. The port portion 50' is also formed at the port side portions of two adjacent laminated core fins. The port side portion of one of the core fins has a plane forming the port portion, and the other core fin is provided with a port partition rib 501' at its port side portion. When forming the port portion, the port partition rib 501' abuts on the plane. Further, the core fin includes a main partition rib 502' extending from one port portion to another port portion, and the side of the main partition rib 502' is used for attaching a film. In particular, since the width of the port partition rib 501' of the core fin is smaller than the width of the main partition rib 502', the length of the space between the adjacent port partition ribs 501' of the port portion of the core fin 10' is made smaller than the length of the space between the adjacent main partition ribs 502'. By providing such a port portion, the flow rate of the air flow entering and leaving the port portion can be increased as well.

[0075] As shown in FIG. 15, the number of the port partition ribs 501' in the core fin corresponds to the number of the main partition ribs 502', and preferably, the main partition ribs 502' are formed integrally with the corresponding port partition ribs 501' and extend in alignment.

[0076] The port side portion having a narrow port portion partition rib as shown in FIG. 15 may be used with a horizontally arranged port side portion, or it should be understood that it may be used in cooperation with a port side portion having a cross-section that tapers towards the outermost side. When the port side portion having a narrow port portion partition rib forms a port portion in cooperation with a port side portion having a cross-section that tapers towards the outermost side, the inlet area of the port portion can be further increased, thereby improving the flow rate of the airflow entering and leaving the port portion.

[0077] When using the heat exchanger described above, the port portion of the airflow forms a flare shape towards the outermost side or narrows the width of the port portion partition rib, reducing the resistance when the airflow enters the heat exchanger, making the airflow smoother, and improving the internal flow velocity of the heat exchanger, thereby improving the heat exchange efficiency of the heat exchanger.

[0078] When using the frame structure of the core fin according to the present invention, the film in the heat exchanger can be reliably protected and supported, the film is less likely to obstruct the airflow, and the service life is extended.

[0079] The present invention is disclosed as above as a preferred embodiment, but it does not limit the present invention. Those skilled in the art can make possible changes and corrections without departing from the spirit and scope of the present invention. Therefore, any corrections, equivalent changes, and modifications made to the above embodiments based on the technical essence of the present invention without departing from the content of the technical solution of the present invention all fall within the protection scope defined by the claims of the present invention.

Explanation of Reference Numerals

[0080] 1 Heat exchanger 10 First core fin 20 Second core fin 10’ Core fin 101,201 First short side 102,202 Second short side 103,203 Third short side 104,204 Fourth short side 105, 106, 205, 206 long sides 1051, 1061, 2051, 2061 curved surfaces 14, 24 positioning parts 15, 25 main partition ribs 16, 26 secondary partition ribs 17, 27 vertical ribs 18, 28 pin holes 181, 281 extended surfaces 19, 29 notches 30 film 41 convex surface 42 concave surface 50, 50’ port parts 51 port side parts 510 inclined surfaces 52 port side parts 520 parallel surfaces 521, 521’ partition ribs 523, 523’ main partition rib flow guiding parts 525 openings 161 secondary partition rib flow guiding parts 60 baffles 70 shells 501’ port part partition ribs 502’ main partition ribs 100 air treatment device 110 fresh air inlets 120 air supply outlets 130 return air inlets 140 exhaust outlets

Claims

1. Comprising a plurality of core fins and a plurality of membranes, wherein the plurality of membranes are respectively attached to one side surface of one of the core fins, and the core fins and the membranes are alternately laminated to form an air flow passage, The plurality of core fins include a first core fin and a second core fin, and the first core fin and the second core fin are laminated with each other to form the air flow passage therebetween, The air flow passage is provided with two port portions arranged opposite to each other, one of the port portions is an inlet portion, and the other is an outlet portion, and the air flow is a heat exchanger that flows from the inlet portion to the outlet portion along the air flow direction, The first core fin and the second core fin respectively include port side portions that are laminated to form the port portion, In the lamination direction of the first core fin and the second core fin, at least the outermost fin layer distance of at least one of the port portions is larger than the fin layer distance at other positions between the inlet portion and the outlet portion of the air flow passage, and / or Port portion partition ribs are provided on the port side portion of the second core fin, the port side portion of the first core fin has a surface that abuts against the port portion partition ribs, and the width of the port portion partition ribs is smaller than the width of the main partition rib extending between the port side portion of the port portion that is the inlet portion and the port side portion of the port portion that is the outlet portion, An opening for the air flow to pass through is provided on the side of the main partition rib extending between the port side portion of the port portion that is the inlet portion and the port side portion of the port portion that is the outlet portion, away from the attached membrane, The opening is wavy, A heat exchanger characterized by the above.

2. The port side portion of the first core fin tapers towards the outermost side in a cross-section parallel to the air flow direction, The heat exchanger according to claim 1, characterized by the above.

3. A plurality of port portion partition ribs are provided on the surface of the port side portion of the second core fin facing the first core fin, The heat exchanger according to claim 2, characterized by the above.

4. The surface of the port side portion of the first core fin facing the air flow passage includes a contour shape of any one of an inclined surface, a curved surface, and a stepped surface, The heat exchanger according to claim 2, characterized by the above.

5. The outermost fin layer spacing at the inlet of the air flow path is larger than the fin layer spacing perpendicular to the air flow direction at other positions between the inlet and the outlet of the air flow path. The heat exchanger according to claim 1, characterized in that.

6. The port portion includes a first end and a second end along the extending direction of the port side portion. The length of the partition rib closest to the first end among the plurality of port portion partition ribs of the second core fin is smaller than the lengths of the other partition ribs. The heat exchanger according to claim 3, characterized in that.

7. The heat exchanger further includes a shell that houses the plurality of core fins and the plurality of membranes. The air flow path includes an intersecting first flow path and a second flow path. The first flow path and the second flow path each have an inlet and an outlet. The inlet of the first flow path is adjacent to the outlet of the second flow path, while the inlet of the second flow path is adjacent to the outlet of the first flow path. The shell is provided with baffles at positions adjacent to the inlet and the outlet, and the baffles are folded back to form filter guide rails. The length of the port portion partition rib at the position corresponding to the guide rail is smaller than the lengths of the remaining port portion partition ribs. The heat exchanger according to claim 3, characterized in that.

8. A flow guiding portion having a shape for guiding the air flow along the advancing direction of the air flow is provided at the end of the port portion partition rib. The heat exchanger according to claim 3 or 6, characterized in that.

9. The plurality of port portion partition ribs of the second core fin include alternately provided, relatively short first port portion partition ribs and relatively long second port portion partition ribs. The port portion includes a first end and a second end along the extending direction of the port side portion. The port portion partition rib closest to the first end is the first port portion partition rib. The heat exchanger according to claim 3, characterized in that.

10. The first core fin includes a first frame, and the second core fin includes a second frame. Each of the first frame and the second frame has a hexagonal outer frame, a main partition rib that basically extends from the inlet to the outlet along the air flow direction of the air flow path, and two vertical ribs that extend across the air flow direction in the air flow path and partition the outer frame into two triangular regions and a rectangular region located between the two triangular regions. The square region further includes auxiliary partition ribs that are basically parallel to the main partition ribs. The heat exchanger according to claim 1, characterized in that.

11. The auxiliary partition ribs have equal distances from the adjacent main partition ribs on both sides. The heat exchanger according to claim 10, characterized in that.

12. The height of the auxiliary partition ribs in the stacking direction is less than or equal to the height of the main partition ribs. The heat exchanger according to claim 10, characterized in that.

13. The width of the main partition rib extending between the port side of the port part that is the inlet part and the port side of the port part that is the outlet part, on the side where the film is attached, is smaller than the width on the side away from the film. The heat exchanger according to claim 1, characterized in that.

14. The first core fin has a first frame, the second core fin has a second frame, the first frame and the second frame have the same contour shape stacked on each other. The port side of the first core fin and the port side of the second core fin are provided along the first part and the second part respectively arranged at the diagonals of the first frame and the second frame. The first frame and the second frame further each include a third part and a fourth part arranged diagonally, and an intersecting port side is formed along the third part and the fourth part. The intersecting port side of the first frame is provided with a plurality of port part partition ribs on the surface opposite to the second core fin. The intersecting port side of the second frame tapers towards the outermost side in a cross-section parallel to the air flow direction, or the width of the port part partition ribs of the intersecting port side of the first frame is smaller than the width of the main partition rib extending between the port side of the port part that is the inlet part and the port side of the port part that is the outlet part. The heat exchanger according to claim 1, characterized in that.

15. The intersecting port side of the second frame includes a contour shape of any one of an inclined surface, a curved surface, and a stepped surface, and the contour shape and the partition ribs of the port side of the second core fin are respectively formed on two side surfaces of the second frame. The heat exchanger according to claim 14, characterized in that.

16. The heat exchanger according to any one of claims 1 to 15, wherein the port part includes a first inlet part, a first outlet part, a second inlet part, and a second outlet part, a fresh air inlet for introducing a fresh air flow in communication with the first inlet part and a air outlet for sending out the fresh air flow in communication with the first outlet part. An air return opening that communicates with the second inlet portion to introduce indoor air flow and an exhaust opening that communicates with the second outlet portion to send out indoor air flow, and the fresh air flow and the indoor air flow cross each other and flow through the heat exchanger to perform heat exchange, an air treatment device.

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