Fin structure and heat exchanger

Abstract

The utility model relates to the technical field of heat exchangers, and discloses a fin structure and a heat exchanger, the fin structure comprises fin units distributed in a plurality of rows, any fin unit comprises a bottom plate and a guide shell formed on the upper side of the bottom plate, the interior of the guide shell is hollow, and the inner side of the guide shell is hollow. The guide shell is provided with a plurality of first openings formed in the first direction, a plurality of second openings formed in the direction opposite to the first direction, a plurality of third openings formed in the second direction and a plurality of fourth openings formed in the direction opposite to the second direction, and the four openings communicate with the interior of the guide shell. The straight line of the first direction intersects with the straight line of the second direction. Liquid can enter the fin units from any direction, namely, the fin can be selected as an inlet and an outlet from any direction, the fin can normally flow no matter which angle is selected, flowing dead zones in the heat exchanger can be reduced, the effective heat exchange area and the heat exchange efficiency are improved, and the plate-fin heat exchanger is more convenient to design.

Description

Technical Field

[0001] This utility model relates to the field of heat exchanger technology, specifically to a finned structure and a heat exchanger. Background Technology

[0002] In the field of heat exchange equipment, plate-fin heat exchangers are widely used due to their high heat exchange efficiency and compact structural design. A plate-fin heat exchanger typically consists of side plates, baffles, fins, and seals. The interlayer formed by fins, guide vanes, and seals between adjacent baffles is called a channel. These interlayers are stacked and welded together according to different fluid flow patterns to form a plate bundle, which is the core component of the plate-fin heat exchanger. Based on this, necessary end caps, nozzles, supports, and other components are added to ultimately assemble a complete plate-fin heat exchanger.

[0003] Currently, the two main types of guide plates commonly used in plate-fin heat exchangers are straight-wave fins and serrated-wave fins. Straight-wave fins have a smaller pressure drop when fluid flows through them, effectively reducing energy loss during fluid transport; serrated-wave fins, on the other hand, exhibit excellent heat transfer performance, achieving more efficient heat transfer. However, serrated-wave fins have relatively higher resistance, 2-3 times that of straight-wave fins. Furthermore, both types of fins are directional, meaning that only a single direction can serve as the inlet and outlet within the entire heat exchanger. This characteristic leads to flow dead zones within the heat exchanger, preventing some areas from fully participating in heat exchange, thus reducing the overall heat transfer efficiency and energy utilization efficiency of the heat exchanger. This limits the application of plate-fin heat exchangers in scenarios requiring high heat transfer efficiency and uniform fluid distribution.

[0004] Therefore, developing a plate-fin heat exchanger structure that can improve fluid distribution, reduce flow dead zones, and also has good heat exchange performance is of great practical significance. Utility Model Content

[0005] In view of this, the present invention provides a finned structure and heat exchanger to solve the problem of flow dead zones that easily occur inside traditional heat exchangers.

[0006] In a first aspect, the present invention provides a fin structure comprising a plurality of fin units arranged in a plurality of rows, all of which are connected to form a plate-shaped fin. Each fin unit includes a base plate and a guide shell formed on the upper side of the base plate. The guide shell is hollow inside and has a plurality of first openings arranged in a first direction, a plurality of second openings arranged in the opposite direction to the first direction, a plurality of third openings arranged in a second direction, and a plurality of fourth openings arranged in the opposite direction to the second direction. All four openings communicate with the interior of the guide shell, and the straight line of the first direction intersects the straight line of the second direction.

[0007] Beneficial effects: The fins are composed of several rows of interconnected fin units, each of which mainly consists of a base plate and a guide shell firmly formed on the upper side of the base plate. The guide shell has a hollow structure, and this hollow space is designed specifically for the smooth flow of liquid, serving as a key channel for achieving efficient heat exchange. The guide shell is provided with a first opening, a second opening, a third opening, and a fourth opening, all of which communicate with the interior of the guide shell. In actual use, liquid can flexibly flow into or out of the guide shell through these four openings according to heat exchange requirements. Since most conventional fins are directional, only a single direction can be used as the inlet and outlet in the entire heat exchanger. In this invention, the first opening is set along the first direction, the second opening is set in the opposite direction of the first direction, the third opening is set along the second direction, and the fourth opening is set in the opposite direction of the second direction. Moreover, the straight line containing the first direction intersects the straight line containing the second direction. Therefore, the liquid can enter the fin unit from at least the first direction, the opposite direction of the first direction, the second direction, and the reverse direction of the second direction. This means that the fin can be selected as the inlet and outlet from multiple directions. No matter which direction is selected, the flow can proceed normally. This can reduce the flow dead zone in the heat exchanger, increase the effective heat exchange area and heat exchange efficiency, and make the design of plate-fin heat exchangers more convenient.

[0008] In one optional embodiment, the first opening and the second opening are located on the same side of the fin unit, and the cross-sections of the first opening and the second opening are parallel.

[0009] Beneficial effects: The first opening and the second opening are located on the left side of the fin unit, and the first opening and the second opening can be considered as two opposite openings of the same cavity. Liquid entering this cavity through the first opening can flow directly out through the second opening, or liquid entering this cavity through the second opening can also flow directly out through the first opening. Of course, this does not limit the liquid entering the guide housing through the first opening to only flowing out through the second opening; all four openings are interconnected. This is merely to describe one liquid flow method.

[0010] In one alternative implementation, the cross-sectional area of ​​the first opening is larger than the cross-sectional area of ​​the second opening.

[0011] In one alternative embodiment, the first opening and the second opening are staggered. As described above, the first opening and the second opening can be considered as openings on two opposite sides of the same cavity. There are multiple such cavities along the length of the fin unit, thus causing the first opening and the second opening to be staggered.

[0012] In one optional embodiment, the third opening and the fourth opening are located on the same side of the fin unit, and the first opening and the third opening are located on opposite sides of the fin unit.

[0013] Beneficial effects: Similar to the first and second openings, the third and fourth openings are located on the left side of the fin unit, and the third and fourth openings can be regarded as two opposite openings of the same cavity. Liquid entering this cavity through the third opening can flow out directly through the fourth opening, or liquid entering this cavity through the fourth opening can also flow out directly through the third opening.

[0014] In one optional embodiment, the first integral formed by the first opening and the second opening has the same structure as the second integral formed by the third opening and the fourth opening. The two integrals are staggered in the length direction of the fin unit, and the first opening in the first integral is located in the middle of the third opening and the fourth opening in the second integral.

[0015] Beneficial effects: The first integral refers to the first opening, the second opening, and the sidewall connecting the first and second openings; similarly, the second integral refers to the third opening, the fourth opening, and the sidewall connecting the third and fourth openings. By staggering the two integrals along the length of the fin unit, with the first opening in the first integral positioned between the third and fourth openings in the second integral, in adjacent fin units, the first opening in one fin unit is positioned between the third and fourth openings in the other fin unit. This allows liquid flowing out of the first opening in one fin unit to quickly pass through the third and fourth openings of the other fin unit and enter that fin unit. Furthermore, if adjacent fin units are perfectly aligned, the distance between the first and third openings in the two fin units becomes too small, affecting the flow of liquid.

[0016] In one optional implementation, the angle between the first direction and the horizontal direction is α, and 0° < α < 90°.

[0017] Beneficial effect: By setting 0° < α < 90°, and ensuring that the first and second directions are symmetrical about the midline of the length direction of the fin unit, it can be guaranteed that the four opening directions of the fin unit are different.

[0018] In one alternative implementation, a gap is provided between two adjacent rows of fin units.

[0019] Beneficial effects: The gap between two adjacent rows of fin units also serves as a liquid flow channel on the fin. In addition, by providing a gap between two adjacent rows of fin units, in addition to using this gap as a liquid flow channel, it can also prevent the distance between two adjacent rows of fin units from being too close, thereby restricting the flow of liquid on the fin.

[0020] In one alternative implementation, the fin units on the fins are aligned in both the vertical and horizontal directions to ensure that the liquid inlet direction of the liquid-filled housing at the same position on each pair of fin units in the same row is the same. This arrangement can avoid the occurrence of blocked openings for liquid inlet between adjacent fin units due to staggered arrangement.

[0021] Secondly, this utility model also provides a heat exchanger, comprising:

[0022] Two partitions;

[0023] A finned structure positioned between two partitions;

[0024] Two side strips are connected to opposite sides of the fin structure, and the other two sides of the fin structure are located for liquid inflow or outflow.

[0025] Beneficial effects: The liquid flow inside the heat exchanger using the above-mentioned finned structure is more uniform, which can reduce the flow dead zone within the heat exchanger, increase the effective heat exchange area and heat exchange efficiency, and make the design of plate-fin heat exchangers more convenient. Furthermore, since there is no flow dead zone, the fins can enter from any direction, and can be used as a single unit in the heat exchanger, eliminating the need for multiple fin sections. Attached Figure Description

[0026] To more clearly illustrate the specific embodiments of this utility model or the technical solutions in the prior art, the drawings used in the description of the specific embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are some embodiments of this utility model. For those skilled in the art, other drawings can be obtained from these drawings without creative effort.

[0027] Figure 1 This is a schematic diagram of a fin structure in one embodiment of the present utility model;

[0028] Figure 2 This is a top view of a fin structure in an embodiment of the present utility model;

[0029] Figure 3 This is a schematic diagram of the structure of a heat exchanger in an embodiment of this utility model.

[0030] Explanation of reference numerals in the attached figures:

[0031] 1. Base plate; 2. Guide housing; 3. First opening; 4. Second opening; 5. Third opening; 6. Fourth opening; 7. Partition; 8. Side strip. Detailed Implementation

[0032] To make the objectives, technical solutions, and advantages of the embodiments of this utility model clearer, the technical solutions of the embodiments of this utility model will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this utility model, not all embodiments. Based on the embodiments of this utility model, all other embodiments obtained by those skilled in the art without creative effort are within the protection scope of this utility model.

[0033] In the field of heat exchange equipment, plate-fin heat exchangers are widely used due to their high heat exchange efficiency and compact structural design. A plate-fin heat exchanger typically consists of side plates, baffles, fins, and seals. The interlayer formed by fins, guide vanes, and seals between adjacent baffles is called a channel. These interlayers are stacked and welded together according to different fluid flow patterns to form a plate bundle, which is the core component of the plate-fin heat exchanger. Based on this, necessary end caps, nozzles, supports, and other components are added to ultimately assemble a complete plate-fin heat exchanger.

[0034] Currently, the two main types of guide plates commonly used in plate-fin heat exchangers are straight-wave fins and serrated-wave fins. Straight-wave fins have a smaller pressure drop when fluid flows through them, effectively reducing energy loss during fluid transport; serrated-wave fins, on the other hand, exhibit excellent heat transfer performance, achieving more efficient heat transfer. However, serrated-wave fins have relatively higher resistance, 2-3 times that of straight-wave fins. Furthermore, both types of fins are directional, meaning that only a single direction can serve as the inlet and outlet within the entire heat exchanger. This characteristic leads to flow dead zones within the heat exchanger, preventing some areas from fully participating in heat exchange, thus reducing the overall heat transfer efficiency and energy utilization efficiency of the heat exchanger. This limits the application of plate-fin heat exchangers in scenarios requiring high heat transfer efficiency and uniform fluid distribution.

[0035] The following is combined with Figures 1 to 3 The following describes embodiments of the present invention.

[0036] According to embodiments of the present invention, in one aspect, a fin structure is provided, such as... Figure 1 As shown, it includes several rows of finned units, all of which are connected to form a plate-shaped fin. Each finned unit includes a base plate 1 and a guide housing 2 formed on the upper side of the base plate 1. The guide housing 2 is hollow inside and has several guides arranged along a first direction ( Figure 2The first opening 3 is set in the direction indicated by the middle arrow c; several second openings 4 are set in the opposite direction to the first direction; and several openings 5 ​​are set in the direction of the second direction. Figure 2 The third opening 5 (in the direction indicated by the middle arrow d) and several fourth openings 6 in the opposite direction to the second direction are all connected to the interior of the guide housing 2, and the straight line in the first direction intersects the straight line in the second direction.

[0037] In this embodiment, the fins are composed of several rows of interconnected fin units. Each fin unit mainly consists of a base plate 1 and a guide shell 2 firmly formed on the upper side of the base plate 1. The guide shell 2 has a hollow structure inside, and this hollow space is designed specifically for the smooth flow of liquids, serving as a key channel for achieving efficient heat exchange. Figure 1 As shown, the guide housing 2 is provided with a first opening 3, a second opening 4, a third opening 5, and a fourth opening 6. All four openings are connected to the interior of the guide housing 2. In actual use, liquid can flow into or out of the guide housing 2 flexibly according to heat exchange requirements through these four openings. Since most conventional fins are directional, only a single direction can be used as the inlet and outlet in the entire heat exchanger. In this embodiment, the first opening 3 is set along the first direction, the second opening 4 is set in the opposite direction of the first direction, the third opening 5 is set along the second direction, and the fourth opening 6 is set in the opposite direction of the second direction. The straight line containing the first direction intersects the straight line containing the second direction. Therefore, liquid can enter the fin unit from at least the first direction, the opposite direction of the first direction, the second direction, and the reverse direction of the second direction. This means that the fin can be selected as the inlet and outlet from multiple directions. No matter which direction is selected, normal flow can be carried out. This can reduce the flow dead zone in the heat exchanger, improve the effective heat exchange area and heat exchange efficiency, and make the design of plate-fin heat exchangers more convenient.

[0038] Of course, such as Figure 1 As shown, the four opening directions mentioned in this embodiment are not absolutely precise directional limitations, but rather approximate extension directions of the opening sidewalls. In actual fluid dynamic environments, liquid flow is influenced by a combination of factors, such as the initial flow velocity, convection caused by temperature differences, and pressure distribution within the heat exchanger. Therefore, the liquid inlet direction is not necessarily strictly along the extension direction of the opening sidewall. When the angle between the liquid inlet direction and the opening cross-section is acute, the liquid can still smoothly enter the finned unit along this opening. Thus, in practical use, the liquid inlet direction of the finned unit in this embodiment is highly flexible, far exceeding the limitations of the extension directions of the sidewalls of the first opening 3, second opening 4, third opening 5, and fourth opening 6. It can adapt to more inlet directions, providing a wide variety of possibilities for fluid flow during heat exchange and further enhancing the performance advantages of the plate-fin heat exchanger.

[0039] In one embodiment, the first opening 3 and the second opening 4 are located on the same side of the fin unit, and the cross-sections of the first opening 3 and the second opening 4 are parallel.

[0040] like Figure 1 As shown, the first opening 3 and the second opening 4 are located on the left side of the fin unit, and the first opening 3 and the second opening 4 can be regarded as two opposite openings of the same cavity. Liquid entering this cavity through the first opening 3 can flow directly out through the second opening 4, or liquid entering this cavity through the second opening 4 can also flow directly out through the first opening 3. Of course, this does not mean that liquid entering the guide housing 2 through the first opening 3 can only flow out through the second opening 4. All four openings are interconnected; this is just to describe one liquid flow mode.

[0041] like Figure 1 As shown, a guide housing 2 sidewall a is provided between two adjacent first openings 3 and second openings 4. This sidewall a smoothly transitions directly with the sidewalls of the first opening 3 and the second opening 4. When the liquid flows to this sidewall a, the liquid is blocked by this sidewall a and can flow directly through the first opening 3 and the second opening 4 into the interior of the guide housing 2, reducing the flow dead zone.

[0042] In one embodiment, the cross-sectional area of ​​the first opening 3 is larger than the cross-sectional area of ​​the second opening 4.

[0043] In one embodiment, the first opening 3 and the second opening 4 are staggered. As mentioned above, the first opening 3 and the second opening 4 can be regarded as openings on two opposite sides of the same cavity. There are multiple such cavities in the length direction of the fin unit, thus making the first opening 3 and the second opening 4 staggered.

[0044] In one embodiment, the third opening 5 and the fourth opening 6 are located on the same side of the fin unit, and the first opening 3 and the third opening 5 are located on opposite sides of the fin unit. Similar to the first opening 3 and the second opening 4, the third opening 5 and the fourth opening 6 are located on the left side of the fin unit, and can be considered as two openings on opposite sides of the same cavity. Liquid entering this cavity through the third opening 5 can flow directly out through the fourth opening 6, or vice versa. Of course, this does not limit the liquid entering the guide housing 2 through the third opening 5 to only flowing out through the fourth opening 6; all four openings are interconnected. This is merely to describe one possible liquid flow pattern. Furthermore, the first opening 3 and the third opening 5 being located on opposite sides of the fin unit increases the liquid inlet direction of the guide housing 2. Similarly, a guide housing 2 sidewall b is provided between two adjacent third openings 5 ​​and fourth openings 6. This sidewall b smoothly transitions directly with the sidewalls of the third opening 5 and fourth opening 6. When the liquid flows to this sidewall b, it is blocked by this sidewall b and can flow directly through the third opening 5 and fourth opening 6 into the interior of the guide housing 2, reducing the flow dead zone.

[0045] In one embodiment, the first integral formed by the first opening 3 and the second opening 4 has the same structure as the second integral formed by the third opening 5 and the fourth opening 6. The two integrals are staggered along the length of the fin unit, and the first opening 3 in the first integral is located between the third opening 5 and the fourth opening 6 in the second integral. Figure 1 As shown, the first integral refers to the first opening 3 and the second opening 4, as well as the sidewall connecting the first opening 3 and the second opening 4; similarly, the second integral refers to the third opening 5 and the fourth opening 6, as well as the sidewall connecting the third opening 5 and the fourth opening 6. By staggering the two integrals along the length of the fin unit, with the first opening 3 in the first integral positioned between the third opening 5 and the fourth opening 6 in the second integral, as shown... Figure 1 As shown, in two adjacent fin units, the first opening 3 in one fin unit is located between the third opening 5 and the fourth opening 6 in the other fin unit. This allows the liquid flowing out of the first opening 3 in one fin unit to quickly pass through the third opening 5 and the fourth opening 6 in the other fin unit and enter that fin unit. Furthermore, if two adjacent fin units are perfectly aligned, the distance between the first opening 3 and the third opening 5 in the two fin units becomes too small, affecting the flow of the liquid.

[0046] In one embodiment, the angle between the first direction and the horizontal direction is α, and 0° < α < 90°. By setting 0° < α < 90°, and ensuring that the first and second directions are symmetrical about the centerline of the fin unit's length direction, it can be guaranteed that the four opening directions of the fin unit are all different.

[0047] In one embodiment, the angle between the first direction and the horizontal direction is 45°. Alternatively, in another embodiment, the angle between the first direction and the horizontal direction is 67.5°. Furthermore, in yet another embodiment, the angle between the first direction and the horizontal direction is 75°.

[0048] In one embodiment, a gap is provided between two adjacent rows of fin units. The gap between two adjacent rows of fin units also serves as a liquid flow channel on the fin. In addition to serving this gap as a liquid flow channel, the gap between two adjacent rows of fin units can also prevent the distance between them from being too close, thereby restricting the flow of liquid on the fin.

[0049] In one embodiment, such as Figure 1 As shown, the fin units on the fins are aligned in both the vertical and horizontal directions to ensure that the liquid inlet direction of the liquid-filled housing at the same position on each pair of fin units in the same row is the same. This arrangement can avoid the occurrence of blocked openings for liquid inlet between adjacent fin units due to staggered arrangement.

[0050] The fin structure provided in this embodiment is formed by bending the base plate 1 upwards. Furthermore, the entire plate-like fin can be a single piece, with the upper part of the fin bending upwards to form all the guide shells 2. The fins can be made of stainless steel, titanium, copper, or other materials.

[0051] The fin structure provided in this embodiment has a resistance that is 1.2-1.3 times that of a straight-wave fin, while still retaining the structural characteristics of an intermittent fin. This structure can periodically disrupt the fluid boundary layer within the fin channel, keeping the velocity and temperature boundary layers in a state of continuous development. It has a high heat transfer coefficient and is a high-efficiency fin, enriching the types of fins that can be used in plate-fin heat exchangers.

[0052] According to an embodiment of the present invention, another aspect, a heat exchanger is also provided, such as... Figure 3 As shown, the heat exchanger includes two partitions 7, a finned structure disposed between the two partitions 7, and two side strips 8. The two partitions 7 and the two side strips 8 form a cavity for housing the finned structure. After the above components are installed, the finned structure serves as the liquid inlet and outlet on both sides of the side strips 8. Using the above-mentioned finned structure results in more uniform liquid flow inside the heat exchanger, reduces flow dead zones within the heat exchanger, increases the effective heat exchange area and heat exchange efficiency, and makes the design of plate-fin heat exchangers more convenient. Furthermore, the fins do not have flow dead zones and can enter from any direction. They can be used as a single unit in the heat exchanger without needing to be divided into multiple fin sections for use.

[0053] Although embodiments of the present invention have been described in conjunction with the accompanying drawings, those skilled in the art can make various modifications and variations without departing from the spirit and scope of the present invention, and such modifications and variations all fall within the scope defined by the appended claims.

Claims

1. A fin structure, characterized by, The fin structure comprises fin units arranged in several columns, all the fin units being connected to form a plate-shaped fin: Any of the fin units comprises a bottom plate (1) and a guide shell (2) formed on the upper side of the bottom plate (1), the guide shell (2) being hollow inside, the guide shell (2) being provided with a plurality of first openings (3) arranged in a first direction, a plurality of second openings (4) arranged in the reverse direction of the first direction, a plurality of third openings (5) arranged in a second direction, and a plurality of fourth openings (6) arranged in the reverse direction of the second direction, the four openings all being in communication with the inside of the guide shell (2), and the straight line in the first direction intersecting the straight line in the second direction.

2. The fin structure of claim 1, wherein The first openings (3) and the second openings (4) are arranged on the same side of the fin unit, and the cross sections of the first openings (3) and the second openings (4) are parallel.

3. The fin structure of claim 2, wherein, The first openings (3) and the second openings (4) are arranged alternately.

4. The fin structure of claim 3, wherein The cross-sectional area of the first openings (3) is larger than that of the second openings (4).

5. The fin structure according to any one of claims 2-4, characterized in that, The third openings (5) and the fourth openings (6) are arranged on the same side of the fin unit, and the first openings (3) and the third openings (5) are located on opposite sides of the fin unit.

6. The fin structure of claim 5, wherein The first whole formed by the first openings (3) and the second openings (4) has the same structure as the second whole formed by the third openings (5) and the fourth openings (6), the two wholes being arranged alternately in the length direction of the fin unit, and the first openings (3) in the first whole being located in the middle of the third openings (5) and the fourth openings (6) in the second whole.

7. The fin structure of claim 6, wherein The angle between the first direction and the horizontal direction is α, and 0°<α<90°.

8. The fin structure of claim 7, wherein, α is 45° or 67.5° or 75°.

9. The fin structure of any one of claims 1-4, wherein, A space is arranged between two adjacent columns of fin units.

10. A heat exchanger, characterized by The fin structure comprises: Two partitions (7); The fin structure according to any of claims 1 to 9 is arranged between the two partitions (7); Two edge strips (8) are connected to the opposite sides of the fin structure, and the other two sides of the fin structure are arranged at the inflow or outflow of liquid.

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