Efficient heat exchange M corrugated fin

Abstract

The utility model discloses an efficient heat exchange M corrugated fin which comprises a starting section, a first isosceles triangle small corrugated section, a second isosceles triangle small corrugated section, a first isosceles trapezoid large corrugated section, a second isosceles trapezoid large corrugated section, a plane wave trough section and a tail end section. The first isosceles triangle small corrugated section is connected with the first isosceles trapezoid large corrugated section, the first isosceles trapezoid large corrugated section is connected with the plane trough section, the plane trough section is connected with the second isosceles trapezoid large corrugated section, and the second isosceles trapezoid large corrugated section is connected with the second isosceles triangle small corrugated section. The second isosceles triangle small corrugated section is connected with the tail end section, and pipe holes are formed in the first isosceles trapezoid large corrugated section and the second isosceles trapezoid large corrugated section. According to the structural design, the air flow resistance is reduced while the heat exchange capacity is guaranteed.

Description

Technical Field

[0001] The utility model belongs to the technical field of heat exchange equipment, and in particular relates to a high-efficiency heat exchange M-shaped corrugated fin. Background Art

[0002] Fin-tube heat exchanger is a widely used heat exchanger. It has the advantages of compact structure, easy processing, light weight and good economic benefits, so it has been widely used in aviation, air conditioning, petrochemical and other fields. Fin-tube heat exchangers have straight fins, corrugated fins, perforated fins and louvered fins. Corrugated fins disturb the air to make it fully turbulent, which improves the heat exchange and heat transfer efficiency, but also increases the air flow resistance, which increases the energy consumption of the system. Summary of the invention

[0003] The utility model provides a high-efficiency heat-exchange M-corrugated fin, which ensures that the fin has a high heat-exchange capacity under a specific air flow rate while reducing flow resistance to achieve the optimal performance of the entire system.

[0004] To achieve the above-mentioned purpose, the utility model provides the following technical solutions: a high-efficiency heat exchange M-shaped corrugated fin, comprising a starting section, a first isosceles triangle small corrugated section, a second isosceles triangle small corrugated section, a first isosceles trapezoidal large corrugated section, a second isosceles trapezoidal large corrugated section, a plane trough section, and an end section, wherein the starting section is connected to the first isosceles triangle small corrugated section, the first isosceles triangle small corrugated section is connected to the first isosceles trapezoidal large corrugated section, the first isosceles trapezoidal large corrugated section is connected to the plane trough section, the plane trough section is connected to the second isosceles trapezoidal large corrugated section, the second isosceles trapezoidal large corrugated section is connected to the second isosceles triangle small corrugated section, the second isosceles triangle small corrugated section is connected to the end section, and tube holes are opened on the first isosceles trapezoidal large corrugated section and the second isosceles trapezoidal large corrugated section.

[0005] Preferably, the heights of the first isosceles trapezoidal large corrugation section and the second isosceles trapezoidal large corrugation section are both h1, and the size range of h1 is 0.6-0.8 mm.

[0006] Preferably, the heights of the first isosceles triangle small corrugation segment and the second isosceles triangle small corrugation segment are both h2, and the size range of h2 is 0.2-0.5 mm.

[0007] Preferably, the projection lengths of the first isosceles trapezoidal large corrugation segment and the second isosceles trapezoidal large corrugation segment along the air flow direction are L1 respectively, and the size range of L1 is 1.5-2.5 mm.

[0008] Preferably, the projection lengths of the first isosceles triangle small corrugation segment and the second isosceles triangle small corrugation segment along the air flow direction are L2 respectively, and the size range of L2 is 6-8 mm.

[0009] Preferably, the angle formed between the starting section and the air flow direction is α, and the angle range of α is -60°-60°.

[0010] Preferably, fillets R1 are provided at the crests of the first isosceles trapezoidal large corrugation segment and the second isosceles trapezoidal large corrugation segment, and the size range of R1 is 1-3 mm.

[0011] Preferably, rounded corners R2 are provided at the crests of the first isosceles triangle small corrugation segment and the second isosceles triangle small corrugation segment, and the size range of R2 is 0.5-1 mm.

[0012] Preferably, the axis of the tube hole for installing the heat exchange tube coincides with the perpendicular bisector of the plane wave valley section.

[0013] Preferably, the spacing d between the fins arranged along the axis of the tube hole is 1.55-1.65 mm.

[0014] Compared with the prior art, the beneficial effects of the utility model are:

[0015] The structural design of the utility model reduces the air flow resistance while ensuring the heat exchange capacity. The plane trough section between the two isosceles trapezoidal large corrugated sections can enable the fins to have good drainage capacity under wet conditions, reduce the residence time of condensed water and defrost water on the fin surface, thereby reducing thermal resistance and improving the heat exchange capacity of the fins under wet conditions; the inclined setting of the starting section increases the effective air inlet area and improves the heat exchange capacity of the fins in a non-uniformly distributed wind field. BRIEF DESCRIPTION OF THE DRAWINGS

[0016] Figure 1 This is a schematic diagram of the dimensions of the corrugated fins of the embodiment of the utility model;

[0017] Figure 2 This is a schematic diagram of the three-dimensional structure of the corrugated fin of the embodiment of the utility model;

[0018] Figure 3 This is a diagram showing the change of the equal pump work evaluation factor with the height of the isosceles trapezoidal large corrugation at different wind speeds;

[0019] Figure 4 This is a graph showing how the equal pump power evaluation factor changes with the fin spacing at different wind speeds.

[0020] In the figure: starting section 1, first isosceles triangle small corrugation section 2, second isosceles triangle small corrugation section 3, first isosceles trapezoidal large corrugation section 4, second isosceles trapezoidal large corrugation section 5, plane trough section 6, end section 7, and tube hole 8. DETAILED DESCRIPTION

[0021] The following will be combined with the drawings in the embodiments of the utility model to clearly and completely describe the technical solutions in the embodiments of the utility model. Obviously, the described embodiments are only part of the embodiments of the utility model, not all of the embodiments. Based on the embodiments in the utility model, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the utility model.

[0022] See also Figure 1-4 The utility model provides the following technical solutions: a high-efficiency heat exchange M-shaped corrugated fin, comprising a starting section 1, a first isosceles triangle small corrugated section 2, a second isosceles triangle small corrugated section 3, a first isosceles trapezoidal large corrugated section 4, a second isosceles trapezoidal large corrugated section 5, a plane trough section 6, and an end section 7, wherein the starting section 1 is connected to the first isosceles triangle small corrugated section 2, the first isosceles triangle small corrugated section 2 is connected to the first isosceles trapezoidal large corrugated section 4, the first isosceles trapezoidal large corrugated section 4 is connected to the plane trough section 6, the plane trough section 6 is connected to the second isosceles trapezoidal large corrugated section 5, the second isosceles trapezoidal large corrugated section 5 is connected to the second isosceles triangle small corrugated section 3, the second isosceles triangle small corrugated section 3 is connected to the end section 7, and the first isosceles trapezoidal large corrugated section 4 and the second isosceles trapezoidal large corrugated section 5 are provided with tube holes 8 for connecting heat exchange tubes.

[0023] As a preferred implementation of this embodiment, the heights of the first isosceles trapezoidal large corrugation section 4 and the second isosceles trapezoidal large corrugation section 5 are both h1, and the size range of h1 is 0.6-0.8 mm. The heights of the first isosceles triangle small corrugation section 2 and the second isosceles triangle small corrugation section 3 are both h2, and the size range of h2 is 0.2-0.5 mm. The increase in the corrugation height will increase the heat transfer coefficient and the air resistance loss at the same time, see Figure 3 Analyzing from the perspective of equal pump work evaluation factors, and comprehensively considering the fin frosting and drainage problems faced under low-temperature heating conditions, the fins have optimal performance when the height of the isosceles trapezoidal large corrugations is within the above-mentioned size range.

[0024] As a preferred implementation of this embodiment, the projection lengths of the first isosceles trapezoidal large corrugated section 4 and the second isosceles trapezoidal large corrugated section 5 along the air flow direction are L1, and the size range of L1 is 1.5-2.5 mm. The projection lengths of the first isosceles triangle small corrugated section 2 and the second isosceles triangle small corrugated section 3 along the air flow direction are L2, and the size range of L2 is 6-8 mm.

[0025] As a preferred implementation of this embodiment, the angle between the starting section 1 and the air flow direction is α, and the angle range of α is -60°-60°. A suitable inclination angle is selected according to the distribution of wind speed in the wind field. This inclination of the starting section increases the effective air inlet area and improves the heat exchange capacity of the fin in a non-uniformly distributed wind field.

[0026] As a preferred implementation of this embodiment, fillets R1 are provided at the crests of the first isosceles trapezoidal large corrugation segment 4 and the second isosceles trapezoidal large corrugation segment 5, and the size range of R1 is 1-3 mm.

[0027] As a preferred implementation of this embodiment, rounded corners R2 are provided at the crests of the first isosceles triangle small corrugation segment 2 and the second isosceles triangle small corrugation segment 3, and the size range of R2 is 0.5-1 mm.

[0028] As a preferred implementation of this embodiment, the axis of the tube hole 8 for installing the heat exchange tube coincides with the perpendicular bisector of the plane wave valley section 6.

[0029] As a preferred implementation of this embodiment, the spacing d between the fins arranged along the axis of the tube hole 8 is 1.55-1.65 mm. The increase in the fin spacing has a small effect on the resistance, but under a certain wave height, appropriately increasing the fin spacing can make better use of the heat exchange performance of the corrugated fins, see Figure 4 The change of equal pump power evaluation factor with equal fin spacing at different wind speeds, and considering the frosting and drainage problems, this type of fin has better comprehensive performance when the fin spacing is between 1.55-1.65mm.

[0030] Although embodiments of the present invention have been shown and described, it will be appreciated by those skilled in the art that various changes, modifications, substitutions and variations may be made to the embodiments without departing from the principles and spirit of the present invention, and that the scope of the present invention is defined by the appended claims and their equivalents.

Claims

1. A high-efficiency heat exchange M corrugated fin, characterized in that: It includes a starting section, a first isosceles triangle small corrugation section, a second isosceles triangle small corrugation section, a first isosceles trapezoidal large corrugation section, a second isosceles trapezoidal large corrugation section, a plane trough section, and an end section. The starting section is connected to the first isosceles triangle small corrugation section, the first isosceles triangle small corrugation section is connected to the first isosceles trapezoidal large corrugation section, the first isosceles trapezoidal large corrugation section is connected to the plane trough section, the plane trough section is connected to the second isosceles trapezoidal large corrugation section, the second isosceles trapezoidal large corrugation section is connected to the second isosceles triangle small corrugation section, the second isosceles triangle small corrugation section is connected to the end section, and the first isosceles trapezoidal large corrugation section and the second isosceles trapezoidal large corrugation section are provided with tube holes.

2. The high-efficiency heat exchange M corrugated fin according to claim 1, characterized in that: The heights of the first isosceles trapezoidal large corrugation section and the second isosceles trapezoidal large corrugation section are both h1, and the size range of h1 is 0.6-0.8 mm.

3. The high-efficiency heat exchange M corrugated fin according to claim 1, characterized in that: The heights of the first isosceles triangle small corrugation segment and the second isosceles triangle small corrugation segment are both h2, and the size range of h2 is 0.2-0.5 mm.

4. The high-efficiency heat exchange M corrugated fin according to claim 1, characterized in that: The projection lengths of the first isosceles trapezoidal large corrugation segment and the second isosceles trapezoidal large corrugation segment along the air flow direction are L1, and the size range of L1 is 1.5-2.5 mm.

5. The high-efficiency heat exchange M corrugated fin according to claim 1, characterized in that: The projection lengths of the first isosceles triangle small corrugation segment and the second isosceles triangle small corrugation segment along the air flow direction are L2 respectively, and the size range of L2 is 6-8 mm.

6. The high-efficiency heat exchange M corrugated fin according to claim 1, characterized in that: The angle formed between the starting section and the air flow direction is α, and the angle range of α is -60°-60°.

7. The high-efficiency heat exchange M corrugated fin according to claim 1, characterized in that: The first isosceles trapezoidal large corrugation segment and the second isosceles trapezoidal large corrugation segment are provided with fillets R1 at their crests, and the size range of R1 is 1-3 mm.

8. The high-efficiency heat exchange M corrugated fin according to claim 1, characterized in that: The crests of the first isosceles triangle small corrugation segment and the second isosceles triangle small corrugation segment are provided with rounded corners R2, and the size range of R2 is 0.5-1 mm.

9. The high-efficiency heat exchange M corrugated fin according to claim 1, characterized in that: The axis of the tube hole for installing the heat exchange tube coincides with the perpendicular bisector of the plane wave valley section.

10. The high-efficiency heat exchange M corrugated fin according to claim 1, characterized in that: The spacing d between the fins arranged along the axis of the tube hole is 1.55-1.65 mm.

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