Heat exchanger fin, heat exchanger and refrigeration equipment

Abstract

The invention discloses a heat exchanger fin, a heat exchanger and refrigeration equipment, and relates to the technical field of heat exchangers, and the heat exchanger fin (1) comprises a wave structure extending in the transverse direction of the heat exchanger fin (1); the wave structure comprises a plurality of alternately distributed wave crest sections (11), wave trough sections (12) and side walls (13) for connecting the adjacent wave crest sections (11) and wave trough sections (12), first side wall structures (131) of the side walls (13) are connected with the wave crest sections (11), second side wall structures (132) of the side walls (13) are connected with the wave trough sections (12), and the length of the first side wall structures (131) in the longitudinal direction is equal to the length of the second side wall structures (132) in the longitudinal direction; the curvature of the first side wall structure (131) in the longitudinal direction is gradually reduced, and the curvature of the second side wall structure (132) in the longitudinal direction is gradually increased. Through the heat exchanger fin, the heat exchange efficiency of the heat exchanger fin can be improved.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of heat exchangers, in particular to a heat exchanger fin, a heat exchanger and a refrigeration equipment. BACKGROUND

[0002] The heat exchanger fin is a functional component for strengthening the heat exchange performance of the heat exchanger, and its structure directly affects the air flow disturbance effect, the utilization rate of the heat exchange area and the air flow resistance, thereby determining the energy efficiency level of the heat exchanger. Among them, the corrugated fin is one of the widely used fin forms in the current heat exchanger field, because it can disturb the air flow through the undulating structure of the wave crest and wave trough, and destroy the air boundary layer, while expanding the effective heat exchange area.

[0003] At present, the curve structure of the corrugated heat exchanger fin in the industry is mainly the sinusoidal fin with uniform curvature. Although the sinusoidal fin has the characteristics of simple processing technology and low forming difficulty, since the curvature changes uniformly throughout the process, the disturbance intensity of each region of the fin to the air flow is always consistent, which cannot adapt to the dynamic state change during the air flow through the fin. When the air flow interacts with the surface of the fin, a thermal boundary layer will be gradually formed and thickened along the flow direction, at this time, stronger disturbance is needed to break the thick boundary layer to maintain efficient heat exchange. Further, the heat exchange efficiency of the sinusoidal fin with uniform curvature is limited. SUMMARY

[0004] The present application provides a heat exchanger fin, a heat exchanger and a refrigeration equipment, which can improve the heat exchange efficiency of the heat exchanger fin.

[0005] In a first aspect, a heat exchanger fin is provided, comprising: a wave structure extending in a transverse direction of the heat exchanger fin; The wave structure comprises a plurality of alternating wave crest segments, wave trough segments, and side walls connecting adjacent wave crest segments and wave trough segments, the wave crest segments are convexly arranged along a longitudinal direction of the heat exchanger fin, and the wave trough segments are concavely arranged along the longitudinal direction of the heat exchanger fin; The side wall comprises a first side wall structure and a second side wall structure connected to each other, the first side wall structure is connected to the wave crest segment, the second side wall structure is connected to the wave trough segment, and the length of the first side wall structure along the longitudinal direction is equal to the length of the second side wall structure along the longitudinal direction; The curvature of the first side wall structure along the longitudinal direction gradually decreases, and the curvature of the second side wall structure along the longitudinal direction gradually increases; The curvature is used to quantify the bending degree at the corresponding position in the wave structure, and the curvature and the bending degree are in a positive correlation.

[0006] In the technical solution, the heat exchanger fin can realize precise adaptation of heat exchange efficiency and flow resistance through the transversely extended wave structure, the sectional side wall design and the structure design with different curvature gradient changes. Specifically, the wave crest section is protrusively arranged along the longitudinal direction of the heat exchanger fin, and the wave trough section is recessively arranged along the longitudinal direction of the heat exchanger fin. Therefore, the longitudinal direction can be considered as the direction from the wave trough to the wave crest. At this time, in combination with the characteristic that the curvature is positively correlated with the bending degree, the first side wall structure is connected with the wave crest section and gradually decreases in longitudinal curvature, indicating that the bending degree gradually decreases along the longitudinal direction. That is, the other end of the first side wall structure (the connection between the first side wall structure and the second side wall structure) reaches the peak of the bending degree, and gradually decreases until the curvature at the wave crest section is at the minimum value. Based on this, it can be considered that the disturbance intensity of the gas flow gradually increases from the gentle disturbance intensity corresponding to the small curvature of the wave crest section to the strongest disturbance state at the other end of the first side wall structure in the process of flowing along the first side wall structure from the wave crest section. This change makes the gas flow along the first curve structure, and the sharp flow direction change is formed at the connection of the side wall structure due to the sharp bending, and the sharp flow direction change can directly strengthen the disturbance of the gas flow, effectively break the thermal boundary layer formed on the surface of the fin, and reduce the accumulation of thermal resistance. Further, the heat exchange efficiency of the heat exchanger fin and the gas flow is significantly improved, and the problem of poor heat exchange effect caused by insufficient local disturbance of the traditional fin is solved. At the same time, the second side wall structure is connected with the wave trough section and gradually increases in longitudinal curvature, indicating that the bending degree is enhanced along the longitudinal direction. That is, the curvature corresponding to the wave trough section connected with the other end of the second side wall structure is the minimum, and the curvature at the end of the second side wall structure (the connection between the first side wall structure and the second side wall structure) is the maximum. Based on this, when the gas flow flows along the second side wall structure to the wave trough section, the curvature of the second side wall structure gradually decreases from the end of the second side wall structure until the bending degree reaches the minimum value at the wave trough section connected with the other end of the second side wall structure, and the flow direction of the gas flow also gradually tends to be relatively gentle at the wave trough section. This gentle design can not only stabilize the slow flow of the gas flow at the wave trough section and avoid additional flow resistance caused by excessive bending of the wave trough section, but also prolong the residence time of the fluid on the surface of the fin, promote more sufficient heat exchange, and guide the gas flow to smoothly transition to the next wave fin, ensuring the continuity and stability of the gas flow.

[0007] In an embodiment, the end point curvatures of the wave structure at the wave crest section and the wave trough section are less than a first preset curvature, and the curvature at the boundary between the first side wall structure and the second side wall structure is greater than a second preset curvature.

[0008] In the technical solution, the constraint that the end-point curvatures of the crest and trough sections are less than the first preset curvature and the curvatures at the junctions of the first and second side wall structures are greater than the second preset curvature can achieve an optimal balance between efficient heat exchange and flow resistance. Specifically, the design that the curvatures at the junctions are greater than the second preset curvature can form steep side wall sections, which can generate a strong local acceleration effect, effectively enhance the near-wall turbulent intensity, and excite stronger turbulent vortices. These vortices have excellent penetration and destruction capabilities for the thermal boundary layer formed during the airflow process, which can greatly improve the heat exchange efficiency. Moreover, the design that the end-point curvatures of the crest and trough sections are less than the first preset curvature can form quasi-platform regions at the end points, which can provide a stable recovery section for the airflow and can cleverly convert the airflow kinetic energy into turbulent energy rather than pure pressure loss, thereby avoiding excessive bending at the end points and generating additional resistance. Ultimately, the design can achieve an optimal balance between efficient heat exchange and flow resistance while enhancing the heat exchange effect.

[0009] In an embodiment, the ratio of the end-point curvature to the curvature at the junction is between 0.2 and 1.

[0010] In the technical solution, the ratio less than 1 can reflect that the bending degree of the side wall is much greater than that of the crest and trough sections. Moreover, the range of 0.2-1 further ensures the difference in curvatures. Specifically, the steep sections formed at the junctions of the side wall due to the greater curvature can produce a more drastic flow direction change, generate a strong local acceleration effect, effectively enhance the near-wall turbulent intensity, and excite stronger turbulent vortices. These vortices have excellent penetration and destruction capabilities for the thickened thermal boundary layer, which can greatly improve the heat exchange efficiency. Meanwhile, the quasi-platform regions formed at the crest and trough sections due to the smaller curvature can provide a stable recovery section for the airflow, which can cleverly convert the airflow kinetic energy into turbulent energy rather than pure pressure loss, thereby avoiding excessive bending at the end points and generating additional resistance, and achieving a smooth transition of the flow state.

[0011] In an embodiment, the wave structure exhibits a curve characteristic in the transverse direction that satisfies the curve characteristic of an inverse trigonometric function. The expression of the inverse trigonometric function is: ; where A is a preset wave amplitude, k is a preset shape control factor, x represents a transverse coordinate in the transverse direction of the heat exchanger fin, and y(x) represents a longitudinal coordinate in the longitudinal direction of the heat exchanger fin.

[0012] In the technical solution, the characteristics of the inverse trigonometric function (arctan) are used in combination with the shape control factor k to achieve the curvature distribution of steep side walls and gentle wave peaks and wave troughs. Specifically, when the value of sin(x) changes, the gradient of the curve of arctan(k*sin(x)) changes, thereby forming more acute bending in the side wall area (corresponding to the section with a large curve slope), which meets the design of large curvature at the boundary. At the same time, the curve slope of the wave peak section and the wave trough section is gentler (which meets the design of small curvature at the end point). Finally, through the above inverse trigonometric function, the design of strong disturbance of the side wall to enhance heat exchange and stable flow control resistance of the wave peak and wave trough is achieved, and the ratio of the end point curvature to the boundary curvature is constrained to be between 0.2 and 1.

[0013] In an embodiment, the value of the shape control factor k ranges from 1 to 5.

[0014] In the technical solution, when k is greater than or equal to 1, the arctan(k*sin(x)) in the inverse trigonometric function expression produces obvious gradient fluctuations with the change of sin(x), thereby forming a steep bending shape in the side wall area of the wave structure, achieving a sharp change in the flow direction of the side wall and strengthening the near-wall turbulent intensity. If k<1, the curve structure of the side wall will be too gentle, the steepness of the side wall will be insufficient, and the disturbance effect will be weak compared to the traditional sine curve, which cannot break through the original heat exchange bottleneck. Moreover, k less than or equal to 5 can avoid excessive steepness of the curve. It prevents the side wall from bending too much to cause additional vortex or blockage when the gas flow flows, and avoids excessive mutation amplitude of the curve to increase the difficulty of cutting processing, ensuring the processing feasibility and stability of the fin structure.

[0015] In an embodiment, the curve characteristic of the wave structure in the transverse direction satisfies the curve characteristic of the hyperbolic tangent function, and the expression of the hyperbolic tangent function is: ; wherein A is a preset wave amplitude, k is a preset shape control factor, x represents a transverse coordinate in the transverse direction of the heat exchanger fin, and y(x) represents a longitudinal coordinate in the longitudinal direction of the heat exchanger fin.

[0016] In the technical solution, the characteristics of the hyperbolic tangent function (tanh) are utilized in combination with the shape control factor k to achieve the curvature distribution of steep side walls and gentle wave peaks and wave troughs. The hyperbolic tangent function changes in an S-shaped manner, and when the value of sin(x) changes, the curve slope of tanh(k*sin(x)) will produce gradient fluctuations. In the vicinity of the extreme points of sin(x) corresponding to the wave peak and wave trough, the absolute value of k*sin(x) is large, and the curve slope of tanh tends to be gentle, and the curve slope corresponding to the wave peak or wave trough is softer, which meets the design of small end-point curvature. Moreover, in the transition section of sin(x) corresponding to the side wall, the absolute value of k*sin(x) is in the middle range, and the curve slope of tanh will increase, forming a more steep curve in the side wall area, which meets the design of large curvature at the boundary. Finally, through the hyperbolic tangent function, the design logic of strong disturbance of the side wall and stable flow control resistance of the wave peak and wave trough can be achieved, while ensuring that the ratio of the end-point curvature to the boundary curvature is between 0.2 and 1.

[0017] In an embodiment, the shape control factor k has a value range of 1-5.

[0018] In the technical solution, k≥1 can make the S-shaped curve of the hyperbolic tangent function have sufficient slope gradient in the side wall, so that the side wall maintains appropriate steepness, thereby producing a significant air flow velocity gradient, strengthening the near-wall turbulent intensity to destroy the thermal boundary layer, fully utilizing the advantages of heat transfer enhancement, and avoiding the problem that k is too small, which causes the curve to be too gentle and the side wall disturbance to be insufficient, thereby failing to break through the traditional heat transfer bottleneck. When k is less than or equal to 5, the curve can be prevented from being too steep, which prevents the generation of additional vortex and resistance when the air flow passes through the side wall, and avoids the problems of out-of-control processing precision, stress concentration of the fin structure, and the like caused by excessive mutation amplitude of the curve, thereby ensuring the processing feasibility and structural stability, and finally making the design logic of strong disturbance of the side wall and stable flow of the wave peak and wave trough efficient, and realizing the optimal adaptation of the comprehensive performance of the fin and the engineering practicability.

[0019] In an embodiment, the curve characteristic of the wave structure in the transverse direction satisfies the curve characteristic of the gradually expanding amplitude function, and the expression of the gradually expanding amplitude function is: wherein A is a preset wave amplitude, is a preset amplitude adjustment coefficient, x represents a transverse coordinate in the transverse direction of the heat exchanger fin, L is the total length of the heat exchanger fin in the transverse direction, and y(x) represents a longitudinal coordinate in the longitudinal direction of the heat exchanger fin.

[0020] ​In the technical solution, the streamline form of the heat exchanger fin is constructed by using a gradually expanding wave amplitude function. By introducing a wave amplitude function that monotonically increases along the flow direction, a small initial wave amplitude is adapted to the thin thermal boundary layer at the beginning of the flow passage (when x is small), which not only provides moderate disturbance to ensure heat exchange efficiency, but also maximizes the initial flow pressure loss. As the airflow advances downstream (in the transverse direction, x gradually increases), the thermal boundary layer gradually thickens and becomes the dominant thermal resistance, and the simultaneously increasing wave amplitude strengthens the contraction effect of the flow passage. Furthermore, not only can the strength of the flow field turbulence be significantly improved, but also the turbulent disturbance can be deep into the thickened boundary layer, continuously and powerfully destroying the stable laminar bottom layer. This dynamic disturbance strategy of weak in front and strong in back can break the heat exchange attenuation problem caused by insufficient disturbance of the airflow along the transverse flow in traditional design, ensure the efficient and uniform heat transfer intensity of the entire heat exchange surface, and realize the design from passive adaptation of flow field to active matching of thermal resistance change.

[0021] In a second aspect, a heat exchanger is provided, comprising the heat exchanger fin according to any one of the first aspect, and further comprising: A refrigerant passage component, a target outer surface of the refrigerant passage component is connected with the heat exchanger fin; the target outer surface is parallel to the flow direction of the refrigerant in the refrigerant passage component.

[0022] In a third aspect, a refrigeration equipment is further provided, comprising the heat exchanger according to the second aspect.

[0023] It can be understood that the beneficial effects of the second aspect to the fourth aspect can be referred to the related description in the first aspect, which will not be repeated here. BRIEF DESCRIPTION OF DRAWINGS

[0024] Figure 1 is a velocity field distribution diagram of airflow flowing through the heat exchanger fin with the curve characteristics conforming to the traditional sine function in an embodiment of the present application; Figure 2 is a structural schematic diagram of a heat exchanger fin in an embodiment of the present application; Figure 3 is a structural schematic diagram of a heat exchanger fin in another embodiment of the present application; Figure 4 is a visualization presentation diagram of the curve characteristics of the inverse trigonometric function under different shape control factors k in an embodiment of the present application; Figure 5 is a top view corresponding to the curve characteristics of the wave structure of the heat exchanger fin under different shape control factors k of the inverse trigonometric function in an embodiment of the present application; Figure 6is a velocity field distribution diagram of airflow when the airflow flows through the heat exchanger fin with the curve characteristic conforming to the inverse trigonometric function, provided in an embodiment of the present application; Figure 7 is a visual presentation diagram corresponding to the curve characteristic of the hyperbolic tangent function, provided in an embodiment of the present application; Figure 8 is a visual presentation diagram corresponding to the curve characteristic of the gradual expansion wave amplitude function, provided in an embodiment of the present application; Figure 9 is a top view of the curve characteristic of the wave structure of the heat exchanger fin under the curve characteristic of the gradual expansion wave amplitude function, provided in an embodiment of the present application; Figure 10 is a structural schematic diagram of a heat exchanger, provided in an embodiment of the present application.

[0025] Reference signs Heat exchanger fin-1, wave crest section-11, wave trough section-12, side wall-13, first side wall structure-131, second side wall structure-132, boundary-133, refrigerant passage component-2, support partition-21, refrigerant flow passage-22. DETAILED DESCRIPTION

[0026] The technical solutions in the embodiments of the present application will be described below with reference to the drawings in the embodiments of the present application. In the description of the embodiments of the present application, unless otherwise specified, “ / ” represents or, for example, A / B can represent A or B; “and / or” in this document only represents a description of the association relationship of the associated objects, which means that there can be three relationships, for example, A and / or B, which means that there are three cases of A alone, A and B together, and B alone. In addition, in the description of the embodiments of the present application, “multiple” means two or more than two.

[0027] Hereinafter, the terms “first”, “second”, “third” are only for descriptive purposes, and cannot be understood as indicating or implying relative importance or implicitly indicating the number of indicated technical features. Therefore, the features defined with “first”, “second”, “third” can explicitly or implicitly include one or more features.

[0028] For the purpose of illustration and not for limitation, specific details such as specific system structures, technologies, etc. are presented in order to thoroughly understand the embodiments of the present application. However, it should be clear to those skilled in the art that the present application can also be implemented in other embodiments without these specific details. In other cases, detailed descriptions of well-known systems, devices, circuits and methods are omitted to avoid unnecessary details that hinder the description of the present application.

[0029] The heat exchanger fin (1) is a functional component for enhancing the heat exchange performance of the heat exchanger, and its structure directly affects the air flow disturbance effect, the utilization rate of the heat exchange area and the air flow resistance, thereby determining the energy efficiency level of the heat exchanger. Among them, the corrugated fin can disturb the air flow and destroy the air boundary layer through the undulating structure of the wave crest and wave trough, and at the same time expand the effective heat exchange area, so it becomes one of the widely used fin forms in the current heat exchanger field.

[0030] At present, the curve structure of the corrugated heat exchanger fin (1) in the industry is mostly a sinusoidal fin with uniform curvature change. Although the sinusoidal fin has the characteristics of simple processing technology and low forming difficulty, due to the uniform curvature change throughout the process, the disturbance intensity of each region of the fin to the air flow is always consistent, which cannot adapt to the dynamic state change of the air flow during the process of flowing through the fin. When the air flow interacts with the surface of the fin, a hot boundary layer will gradually form and thicken along the flow direction, at this time, stronger disturbance is needed to break the thick boundary layer to maintain efficient heat exchange. Further, the heat exchange efficiency of the sinusoidal fin with uniform curvature change is limited.

[0031] Specifically, referring to Figure 1 , Figure 1 is a velocity field distribution diagram of the air flow when flowing through the heat exchanger fin conforming to the curve characteristics of the traditional sine function. As shown in Figure 1 , the white curve represents the wave profile of the fin with a traditional trigonometric function (sine) streamline type. That is, the surface shape of the heat exchanger fin (1) corresponding to y=A·sin(kx) has smooth and symmetrical curvature, and the curvature changes uniformly, which is a commonly used fin structure form in the industry. The colored area represents the thickness distribution of the hot boundary layer when the air flow flows through the fin, and the color gradient (blue→green→yellow→orange) corresponds to the speed change. Among them, the arrow indicates the direction of speed increase. Specifically, blue represents the low-speed area, and orange represents the high-speed area. The hot boundary layer is thick in the low-speed area, and the hot boundary layer is thin in the high-speed area due to the faster fluid scouring speed.

[0032] Among them, the color change along the way (from left to right, gradually from blue to yellow / orange) in Figure 1 can directly reflect the core defect of the traditional sine function fin. Specifically, since the white fin profile is a sinusoidal curve with uniform curvature, the disturbance intensity to the air flow is constant amplitude, which cannot adapt to the dynamic change of the hot boundary layer. In the inlet area (blue thin boundary layer area on the left side of the figure), the boundary layer is thin at this time, and only a small disturbance is needed for efficient heat exchange, but the fixed amplitude of the sine function will bring excessive disturbance, resulting in unnecessary flow resistance. In the downstream area, the area of the blue area gradually increases, which can be considered that the boundary layer is thickening at this time. However, the constant amplitude disturbance intensity of the sine function is insufficient to effectively break the thick hot boundary layer, which ultimately reflects the heat resistance accumulation in the thick boundary layer area (blue area) in Figure 1 , directly leading to the decay of the heat exchange capacity along the flow direction.

[0033] Based on the above description, Figure 1 Through the color gradient of the thermal boundary layer thickness, the problem of mismatching between the disturbance intensity of the traditional sinusoidal streamline fin and the boundary layer change is intuitively presented. The smooth sinusoidal profile (white curve) cannot adjust the disturbance in a targeted manner, ultimately causing the performance bottleneck of excessive resistance consumption at the inlet and heat exchange attenuation downstream.

[0034] Therefore, in order to provide the heat exchange effect of the heat exchanger fin, with reference to Figure 2 and Figure 3 A heat exchanger fin (1) comprises: A wave structure extending in the transverse direction of the heat exchanger fin (1); The wave structure comprises a plurality of alternating wave peak segments (11), wave valley segments (12), and side walls (13) connecting adjacent wave peak segments (11) and wave valley segments (12). The wave peak segment (11) is convexly arranged along the longitudinal direction of the heat exchanger fin (1), and the wave valley segment (12) is concavely arranged along the longitudinal direction of the heat exchanger fin (1); The side wall (13) comprises a first side wall structure (131) and a second side wall structure (132) connected to each other. The first side wall structure (131) is connected to the wave peak segment (11), and the second side wall structure (132) is connected to the wave valley segment (12). The length of the first side wall structure (131) in the longitudinal direction is equal to the length of the second side wall structure (132) in the longitudinal direction; The curvature of the first side wall structure (131) in the longitudinal direction gradually decreases, and the curvature of the second side wall structure (132) in the longitudinal direction gradually increases; Wherein, the curvature is used to quantify the bending degree at the corresponding position in the wave structure, and the curvature and the bending degree are in a positive correlation.

[0035] In an embodiment, the heat exchanger fin (1) is a sheet structure covering the outer surface of the refrigerant channel, which is also a component for realizing heat exchange. As Figure 2 shown, the surface structure of the heat exchanger fin (1) has a continuous wave structure. Among them, the wave structure is the overall undulating form on the heat exchanger fin (1), which extends in the transverse direction and is composed of a plurality of alternating wave peak segments (11), wave valley segments (12), and side walls (13).

[0036] Among them, the above transverse direction is the direction in which the wave structure extends and arranges on the heat exchanger fin (1) (i.e. Figure 2 the horizontal direction in which the waves are arranged row by row). In this embodiment, the transverse direction can be Figure 2 the arrow X direction from left to right.

[0037] The aforementioned longitudinal direction refers to the direction of the convex or concave features of the wave structure (perpendicular to the transverse direction), and is also the orientation of the convex / concave features of the crest segment (11) and trough segment (12). In this embodiment, the aforementioned longitudinal direction can be... Figure 2 The direction from the trough to the crest. That is, Figure 2 The arrow Y points from the trough to the crest of the wave.

[0038] Among them, the crest segment (11) is the sidewall (13) corresponding to the crest in the wave structure, which is the part that protrudes outward in the longitudinal direction of the wave structure. Correspondingly, the trough segment (12) is the sidewall (13) corresponding to the trough in the wave structure, which is the part that is concave in the longitudinal direction of the wave structure.

[0039] Furthermore, the sidewall (13) connecting the adjacent crest segment (11) and trough segment (12) is the transition area between the adjacent crest segment (11) and trough segment (12). The sidewall (13) can be divided into a first sidewall structure (131) and a second sidewall structure (132).

[0040] The first sidewall structure (131) is the part of the sidewall (13) that connects to the crest section (11), and its length in the longitudinal direction is equal to that of the second sidewall structure (132). The second sidewall structure (132) is the part of the sidewall (13) that connects to the trough section (12), and is the connecting section of the first sidewall structure (131).

[0041] In one embodiment, the heat exchanger fins (1) can be integrally formed fin structures, and their number can be one set or multiple sets, which is not limited. Among them, the number of corresponding crest segments (11) and trough segments (12) in one set of heat exchanger fins (1) can be preset, which is not limited.

[0042] The curvature of the first sidewall structure (131) gradually decreases along the longitudinal direction, while the curvature of the second sidewall structure (132) gradually increases along the longitudinal direction. The curvature is used to quantify the degree of bending at the corresponding position in the wave structure, and the curvature is positively correlated with the degree of bending.

[0043] Based on the above explanation, it can be considered that in the structure from the trough to the crest, the curvature gradually increases from the lowest curvature of the trough segment (12), and reaches its maximum at the boundary (133) between the second sidewall structure (132) and the first sidewall structure (131). Finally, the maximum curvature gradually decreases from the boundary (133) until it reaches the lowest curvature of the trough segment (12).

[0044] In one embodiment, the aforementioned dividing point (133) can be considered as the intersection point where a single sidewall (13) is divided into a first sidewall structure (131) and a second sidewall structure (132), and is the connecting boundary of the two sidewall (13) structures. The dividing point (133) can be considered as the longitudinal midpoint of the sidewall (13), such that the length of the first sidewall structure (131) along the longitudinal direction is equal to the length of the second sidewall structure (132) along the longitudinal direction.

[0045] It should be noted that the first sidewall structure (131) is a curved structure connecting the crest section (11) and the boundary (133). The first sidewall structure (131) extends longitudinally towards the crest section (11), and the curvature gradually decreases, indicating that the degree of curvature of the structure will gradually become gentler from the relatively severe curvature at the boundary (133) between the first sidewall structure (131) and the second sidewall structure (132) (the closer to the crest section (11), the gentler the curvature). At this time, when the airflow enters the first sidewall structure (131) after passing through the relatively gentle crest section (11), the design based on the gradually increasing curvature of the first sidewall (131) can gradually enhance the airflow disturbance. At the boundary (133) between the first sidewall structure (131) and the second sidewall structure (132), a more abrupt flow direction change is formed due to the severe curvature. The abrupt flow direction change can directly enhance the airflow disturbance, effectively break the thermal boundary layer formed by the airflow on the fin surface, and reduce the accumulation of thermal resistance.

[0046] Furthermore, the second sidewall structure (132) is a curved structure connecting the boundary (133) and the trough section (12), and the curvature of the second sidewall structure (132) gradually increases along the longitudinal direction. Therefore, it can be considered that the curvature of the second sidewall structure (132) will be gentler from the relatively severe area at the boundary (133) to the gentler the curvature as it approaches the trough section (12). At this time, when the airflow reaches the second sidewall structure (132) after passing through the first sidewall structure (131), the thermal boundary layer has gradually thickened with the flow direction (thermal resistance increases synchronously). However, as explained above, the boundary (133) between the first sidewall structure (131) and the second sidewall structure (132) forms a more abrupt flow direction change due to the severe curvature, and the abrupt flow direction change can directly enhance the airflow disturbance, effectively break the thermal boundary layer formed by the airflow on the fin surface, and reduce thermal resistance accumulation. Furthermore, as the airflow flows along the second sidewall structure (132) towards the trough section (12), the curvature of the second sidewall structure (132) gradually decreases from the boundary (133) until it reaches the minimum value of curvature in the trough section (12), and the change in airflow direction also becomes relatively gentle in the trough section (12). This gentle design can stabilize the slow flow of air in the trough section (12), avoid the additional flow resistance caused by excessive curvature in the trough section (12), and promote more sufficient heat exchange by extending the residence time of the fluid on the fin surface. At the same time, it guides the airflow to smoothly transition to the next corrugated fin, ensuring the continuity and stability of the airflow.

[0047] Based on this, the heat exchange effect of the airflow when it exchanges heat along the heat exchanger fins (1) can be improved by using the alternating distribution of the crest section (11), trough section (12) and the sidewall (13) connecting the adjacent crest section (11) and trough section (12).

[0048] In this embodiment, the heat exchanger fins (1) achieve precise matching between heat exchange efficiency and flow resistance through a transversely extending wave structure, segmented sidewall (13) design, and a structural design with differentiated curvature gradient changes. Specifically, the crest section (11) protrudes along the longitudinal direction of the heat exchanger fins (1), and the trough section (12) is recessed along the longitudinal direction of the heat exchanger fins (1). Therefore, the longitudinal direction can be considered as the direction from the trough to the crest. At this time, combined with the characteristic that curvature and bending degree are positively correlated, the first sidewall structure (131) is connected to the crest section (11) and the curvature gradually decreases along the longitudinal direction, indicating that the bending degree gradually decreases with the longitudinal direction. That is, the other end of the first sidewall structure (131) (the connection between the first sidewall structure (131) and the second sidewall structure (132)) reaches the peak of the bending degree and gradually decreases until the curvature at the crest section (11) is at its lowest value. Based on this, it can be considered that during the flow of air from the crest section (11) along the first sidewall structure (131), the intensity of the disturbance will gradually increase from the gentle disturbance intensity corresponding to the smaller curvature of the crest section (11) to the strongest disturbance state at the other end of the first sidewall structure (131). This change causes the airflow to form a more abrupt flow direction change at the connection of the sidewall (13) structure due to the severe bending when flowing along the first curved structure. The abrupt flow direction change can directly enhance the airflow disturbance, effectively break the thermal boundary layer formed by the airflow on the fin surface, and reduce the accumulation of thermal resistance. In turn, it significantly improves the heat exchange efficiency between the heat exchanger fins (1) and the airflow, and solves the problem of poor heat exchange effect caused by insufficient local disturbance of traditional fins. At the same time, the second sidewall structure (132) is connected to the trough section (12) and the curvature gradually increases along the longitudinal direction, indicating that the degree of bending increases synchronously with the longitudinal direction. That is, the curvature of the trough section (12) connected to the other end of the second sidewall structure (132) is the smallest, and the curvature of the end of the second sidewall structure (132) (the connection between the first sidewall structure (131) and the second sidewall structure (132)) is the largest. Based on this, when the airflow flows along the second sidewall structure (132) to the trough section (12), the curvature of the second sidewall structure (132) gradually decreases from the end of the second sidewall structure (132) until it reaches the minimum value of curvature in the trough section (12) connected to the other end of the second sidewall structure (132), and the change in airflow direction also tends to be relatively gentle in the trough section (12). This gentle design can stabilize the airflow in the trough section (12) and prevent the trough section (12) from generating additional flow resistance due to excessive bending. It can also promote more sufficient heat exchange by extending the residence time of the fluid on the fin surface, and at the same time guide the airflow to smoothly transition to the next corrugated fin, ensuring the continuity and stability of the airflow.

[0049] In one embodiment, the curvature of the wave structure at the crest (11) and trough (12) is less than the first preset curvature, and the curvature at the boundary (133) between the first sidewall structure (131) and the second sidewall structure (132) is greater than the second preset curvature.

[0050] Among them, reference Figure 2 and Figure 3 The endpoint curvature can be considered as the curvature at the crest (11) (the endpoint of the crest) and the trough (12) (the endpoint of the trough). As can be seen from the above explanation, the endpoint curvature is the smallest at the endpoint.

[0051] The aforementioned first preset curvature is a pre-set, relatively small curvature threshold, used as a reference value to limit the degree of curvature at the peaks and troughs. The first preset curvature constrains the curvature at the peaks and troughs to remain relatively gentle (because the smaller the curvature, the gentler the curvature).

[0052] The second preset curvature is similar to the first preset curvature. The second preset curvature is a reference value for limiting the degree of bending at the boundary (133), which is used to constrain the bending at the boundary (133) to remain relatively severe (because the greater the curvature, the more severe the bending).

[0053] As an example, the first preset curvature can be 0.2, and the second preset curvature can be 0.5.

[0054] It is understandable that by constraining the curvature of the endpoints of the crest section (11) and the trough section (12) to be less than the first preset curvature, and the curvature of the boundary (133) between the first sidewall structure (131) and the second sidewall structure (132) to be greater than the second preset curvature, an optimized balance between efficient heat transfer and flow resistance can be achieved. Specifically, the design of the boundary (133) to be greater than the second preset curvature can form a steep sidewall (13) section, which can generate a strong local acceleration effect, effectively enhance the turbulence intensity near the sidewall (13), and generate stronger turbulent vortices. These vortices have excellent penetration and destruction capabilities on the thermal boundary layer formed during the airflow process, greatly improving heat transfer efficiency. Furthermore, the design that the endpoints of the crest section (11) and the trough section (12) are smaller than the first preset curvature can form a quasi-platform area at the endpoints, providing a stable recovery section for the airflow. This can cleverly convert the airflow kinetic energy into turbulent energy rather than simply pressure loss, avoiding the additional resistance caused by excessive bending at the endpoints. Ultimately, while enhancing the heat exchange effect, it achieves a precise match between efficient heat exchange and flow resistance.

[0055] In one embodiment, the ratio of the endpoint curvature to the curvature at the boundary (133) is between 0.2 and 1.

[0056] In this embodiment, a ratio less than 1 indicates that the curvature of the sidewall (13) is much greater than that of the crest section (11) and trough section (12). Furthermore, the range of 0.2-1 further ensures the difference in curvature. Among them, the boundary (133) of the sidewall (13) forms a steep section due to its greater curvature, which can create a more rapid change in flow direction, generate a strong local acceleration effect, effectively enhance the intensity of near-wall turbulence, and stimulate stronger turbulent vortices. These vortices have excellent penetration and destruction capabilities on the thickened thermal boundary layer, greatly improving heat transfer efficiency. At the same time, the crest section (11) and trough section (12) form a gentler quasi-plateau region due to their smaller curvature, providing a stable recovery section for the airflow. This can cleverly convert the kinetic energy of the airflow into turbulent energy rather than simple pressure loss, avoid excessive curvature at the endpoints to generate additional resistance, and achieve a smooth transition of the flow state.

[0057] As an example, the wave structure exhibits a curve characteristic in the lateral direction that satisfies the curve characteristic of an inverse trigonometric function; the expression for the inverse trigonometric function is: ; Where A is the preset amplitude, k is the preset shape control factor, x represents the transverse coordinate of the heat exchanger fin (1) along the transverse direction, and y(x) represents the longitudinal coordinate of the heat exchanger fin (1) along the longitudinal direction.

[0058] In one embodiment, by utilizing the properties of the inverse trigonometric function (arctan) in conjunction with the shape control factor k, a curvature distribution with steep sidewalls (13) and gentle peaks / troughs can be achieved. Specifically, when the value of sin(x) changes, the slope of the arctan(k*sin(x)) curve will change gradient, thereby forming a more abrupt bend in the sidewall (13) region (corresponding to the section with a large curve slope) (satisfying the design of a large curvature at the boundary (133)). At the same time, the curve slopes of the peak section (11) and the trough section (12) are gentler (satisfying the design of a small curvature at the endpoint). Finally, through the above inverse trigonometric function, a design of strong disturbance-enhanced heat transfer and gentle peaks and troughs with stable flow and resistance can be achieved, ensuring that the ratio of the curvature at the endpoint to the curvature at the boundary (133) is between 0.2 and 1.

[0059] In one embodiment, the amplitude and shape control factor can be set according to actual conditions, and there is no limitation thereto. For example, the amplitude can be 0.5-1, for example, 0.6. The value range of the shape control factor k can be 1-5, for example, 1.

[0060] It should be noted that when k is small (e.g., k=1), the inverse trigonometric function curve fluctuates more gently, corresponding to a flatter fin sidewall (13), a more uniform airflow velocity distribution, and a weaker velocity gradient on the sidewall (13). Although the flow resistance is low, the thermal boundary layer disruption effect is limited, the heat exchange in the troughs is insufficient, and the improvement in heat transfer efficiency is weak. When k increases (e.g., k=2), the curve fluctuates more violently, the fin sidewall (13) becomes steeper, and the airflow exhibits a distribution with concentrated high-speed areas at the peaks and expanded low-speed areas at the troughs. The velocity gradient on the sidewall (13) is significantly enhanced, which can both disrupt the thermal boundary layer and prolong the fluid residence time, resulting in a significant improvement in heat transfer efficiency. However, when k is greater than 5, the excessive steepness of the sidewall (13) will lead to an increase in airflow vortices and a surge in resistance, while also increasing the processing difficulty. Therefore, the value of k can be considered as a parameter that balances the fin structure morphology, airflow characteristics, and heat transfer performance.

[0061] In this embodiment, when k is greater than or equal to 1, the arctan(k*sin(x)) in the inverse trigonometric function expression can generate a significant gradient fluctuation as sin(x) changes, thereby forming a sufficiently steep curvature in the sidewall (13) region of the wave structure, achieving a rapid change in flow direction of the sidewall (13) and enhancing the turbulence intensity near the wall. If k<1, the curve structure change of the sidewall (13) will be too gentle, the steepness of the sidewall (13) will be insufficient, and the difference in disturbance effect from the traditional sine curve will be slight, failing to break through the original heat exchange bottleneck. Furthermore, k less than or equal to 5 can avoid the curve from being too steep. This prevents the sidewall (13) from being too curved, which would cause additional vortices or blockages during airflow, and also avoids the curve from changing too abruptly, increasing the difficulty of the cutting process, thus ensuring the feasibility of processing and the stability of the fin structure.

[0062] As a specific example, refer to Figure 4 and Figure 5 , Figure 4 This is a visualization of the curve characteristics of an inverse trigonometric function under different shape control factors k, provided in one embodiment of this application. Figure 5 This is a top view of the curve features of a wave structure of a heat exchanger fin provided in one embodiment of this application, under different shape control factors k of an inverse trigonometric function. Wherein, Figure 4 The horizontal axis in the figure represents the horizontal coordinate of the heat exchanger fin (1) along the horizontal direction, and y(x) represents the vertical coordinate of the heat exchanger fin (1) along the vertical direction.

[0063] like Figure 4 As shown, in Figure 4 In (a), when k=1, the variation of arctan(1*sin(x)) is relatively mild, resulting in a smoother fluctuation in the function curve. The transitions between the curve's peaks (11), sidewalls (13), and troughs (12) are gentler, corresponding to a weaker degree of bending in the fin's wave structure.Figure 4 In (b), when k=2, the range of values ​​for arctan(2*sin(x)) expands, and the output of arctan(2*sin(x)) changes more significantly, so the function curve fluctuates more violently. The curve has a greater slope connecting the peak (11) and trough (12) with the sidewall (13), corresponding to a stronger degree of bending of the fin wave structure (the sidewall (13) is steeper).

[0064] And, such as Figure 5 As shown, in Figure 5 In (a), when k=1, the corresponding Figure 5 (a) shows a gentler function curve, with the sidewall (13) region of the fin wave structure being gentler and the overall undulation transition being softer. In Figure 5 (b), when k=2, the undulation of the function curve is more intense, the sidewall (13) region of the fin wave structure is steeper, and the transitions between the peak (11), sidewall (13), and trough (12) are more obvious.

[0065] Based on the above, Figure 4 and Figure 5 The explanation shows that by adjusting the value of k, the curvature of the inverse trigonometric function curve can be precisely controlled, thereby changing the shape of the fin wave structure. Furthermore, this provides a visual support for the morphological differences of the constraint of k values ​​1-5, enabling the design logic of defining fin curve characteristics based on inverse trigonometric functions to be implemented. In addition, the value of k is positively correlated with the curvature of the sidewall (13). The larger the value of k, the steeper the sidewall (13) is, and the more it can enhance airflow disturbance.

[0066] In another embodiment, reference Figure 1 and Figure 6 , Figure 6 This is a velocity field distribution diagram of the airflow as it flows through heat exchanger fins conforming to an inverse trigonometric function curve, according to one embodiment of this application. Figure 6 In the diagram, the white curve represents the waveform profile of the heat exchanger fins (1) when k is 2. The colored areas represent the velocity field distribution as the airflow passes through the heat exchanger fins. The color gradient corresponds to the velocity magnitude, with blue typically representing the low-speed region and yellow or orange representing the high-speed region.

[0067] for Figure 6In the heat exchanger fins (1) corresponding to the inverse trigonometric function, the blue low-speed zone has a wider coverage and a darker color in the trough section (12) (the concave part of the white curve). It can be considered that the trough section (12) forms a more significant low-speed flow zone, with a decrease in absolute velocity value and an expansion of the low-speed zone coverage. In the crest section (11) (the convex part of the white curve), the yellow / orange high-speed zone is more concentrated. The boundary between the high-speed zone and the low-speed zone in the sidewall (13) structure is clearer, showing a strong division from high speed to low speed, resulting in a very significant velocity gradient in the sidewall (13) region between the crest section (11) and the trough section (12).

[0068] However, based on Figure 1 It can be seen that in the heat exchange fins corresponding to the traditional trigonometric function, the blue low-speed zone of the trough section (12) is narrower and lighter in color. Furthermore, the high-speed zone of the crest section (11) is more dispersed and does not have obvious concentrated features. Moreover, the velocity gradient of the sidewall (13) structure is gentler, and the boundary between high and low speeds is not prominent, making it impossible to generate a very significant velocity gradient in the sidewall (13) region between the crest section (11) and the trough section (12).

[0069] Based on this, it can be assumed that the velocity field distribution of the heat exchange fins corresponding to the inverse trigonometric function k=2 can enhance the renewal of the thermal boundary layer based on the strong velocity gradient of the sidewall (13), thereby disrupting the stable development of the thermal boundary layer. At the same time, in the trough section (12), the low-velocity zone can be expanded to prolong the fluid residence time and promote sufficient heat exchange. Ultimately, the heat exchange efficiency is improved, and it has a greater performance advantage compared to the heat exchanger fins (1) corresponding to the traditional trigonometric function.

[0070] As a specific example, curvature can be calculated using the following formula: ; in, and These represent the first and second derivatives of the function corresponding to the heat exchanger fins (1) at a certain point, respectively. Specifically, the first derivative... It can quantify the slope (inclination) of a function at a certain point, the second derivative. It can quantify how quickly the slope changes at a point. The curvature corresponding to Z can be used to quantify the actual degree of bending of the function at a point.

[0071] For the above inverse trigonometric functions, let the normalization coefficients... ,but .

[0072] First derivative : ; Second derivative : ; For example, with parameter A=0.6mm and k=2: At the peak , , , ; At the trough , , , ; At the side wall point , , , .

[0073] For the traditional sine function ; First derivative ; Second derivative ; Taking parameter A=0.6mm as an example At the peak , , , ; At the trough , , , ; At point (13) on the side wall , , , .

[0074] Based on the above examples, the curvatures of the heat exchanger fins (1) corresponding to the inverse trigonometric function and the traditional sine function are shown in Table 1 below: Table 1

[0075] Based on Table 1 above, it can be seen that in the heat exchanger fins (1) corresponding to the traditional sine function, the curvature of the peaks and troughs is relatively large (0.600), while the curvature of the sidewall (13) is relatively small (0.331), and its geometry is symmetrical and smoothly changing.

[0076] In the heat exchanger chip corresponding to the inverse trigonometric function, the curvature of the peaks and valleys is significantly reduced (0.2167), forming an obvious plateau region, while the sidewall (13) region is increased (0.542), verifying the design feature of peak / valley plateauing.

[0077] Furthermore, the curvature ratio of the traditional sine function is 1.813, indicating that the curvature of its sidewall (13) is less than that of the crest / trough. The curvature ratio of the inverse trigonometric function is 0.400, indicating that the curvature of its sidewall (13) is much greater than that of the crest / trough. Among them, the ratio less than 1 can intuitively reflect the advantage of the inverse trigonometric function in creating a more abrupt change in flow direction at the sidewall (13) to enhance the disturbance, while providing a smoother area at the crest / trough to stabilize the flow and control the resistance.

[0078] In one embodiment, simulation calculations show that when k is 1, the heat exchanger fins (1) with inverse trigonometric functions have a 0.7% increase in the j-factor and a 2.1% increase in heat transfer per unit volume compared to the traditional heat exchanger fins (1) with sine functions; when k is 2, the heat exchanger fins (1) with inverse trigonometric functions have a 2.9% increase in the j-factor and a 4.9% increase in heat transfer per unit volume compared to the traditional heat exchanger fins (1) with sine functions. Here, j is the heat transfer factor, a dimensionless performance parameter in the heat exchanger used to characterize its heat transfer performance.

[0079] Based on this, it can be argued that the use of inverse trigonometric function fin streamlines to improve heat transfer and heat exchange per unit volume indicates that a larger heat exchange can be achieved with the same volume, or a smaller volume is required to achieve the same heat exchange, thus reducing costs and increasing efficiency. Furthermore, while increasing k improves heat transfer efficiency, it also increases resistance. Therefore, in practical production applications, a suitable k-factor must be selected to achieve a balance between heat transfer and resistance.

[0080] In another embodiment, the lateral curve characteristics of the wave structure can also satisfy the curve characteristics of the hyperbolic tangent function; the expression of the hyperbolic tangent function is: ; Where A is the preset amplitude, k is the preset shape control factor, x represents the transverse coordinate of the heat exchanger fin (1) along the transverse direction, and y(x) represents the longitudinal coordinate of the heat exchanger fin (1) along the longitudinal direction.

[0081] It should be noted that the amplitude and shape control factors mentioned above are similar to the amplitude and shape control factors in inverse trigonometric functions, and will not be explained further.

[0082] In one embodiment, by utilizing the properties of the hyperbolic tangent function (tanh) and combining it with the shape control factor k, a curvature distribution with steep sidewalls (13) and gentle peaks / troughs can also be achieved. The hyperbolic tangent function exhibits an S-shaped change, and when the value of sin(x) changes, the slope of the tanh(k*sin(x)) curve will fluctuate with a gradient. Near the extreme points of sin(x) corresponding to the peak segment (11) and the trough segment (12), the absolute value of k*sin(x) is relatively large, and the slope of the tanh curve tends to be gentler, resulting in a softer curve slope corresponding to the peak or trough, which satisfies the design of small end-point curvature.

[0083] Furthermore, in the sin(x) transition section corresponding to the sidewall (13), the absolute value of k*sin(x) is in the middle range, and the slope of the tanh curve will increase, resulting in a more abrupt bend in the sidewall (13) region, satisfying the design of a large curvature at the boundary (133). Finally, through this hyperbolic tangent function, the design logic of strong disturbance to enhance heat transfer in the sidewall (13) and smooth flow control with gentle peaks and troughs can be realized, while ensuring that the ratio of the curvature at the endpoint to the curvature at the boundary (133) is between 0.2 and 1.

[0084] In one embodiment, the amplitude and shape control factor in the hyperbolic tangent function described above can be similar to the amplitude in the inverse trigonometric function, and will not be described in detail here. For example, the shape control factor k ranges from 1 to 5.

[0085] In this embodiment, k is limited to 1-5, which can accurately balance the heat transfer performance, flow resistance and processing feasibility of the hyperbolic tangent function fin. k≥1 can make the S-curve of the hyperbolic tangent function form a sufficient slope gradient on the sidewall (13), so that the sidewall (13) maintains a suitable steepness, thereby generating a significant airflow velocity gradient, strengthening the near-wall turbulence intensity to destroy the thermal boundary layer, giving full play to its heat transfer enhancement advantage, and avoiding the curve being too flat and the sidewall (13) being too disturbed due to k being too small, thus failing to break through the traditional heat transfer bottleneck; k less than or equal to 5 can avoid the curve being too steep, preventing the airflow from generating additional vortices and resistance when flowing through the sidewall (13), while avoiding the problems of uncontrolled processing accuracy and stress concentration in the fin structure caused by excessive curve abrupt change, ensuring processing feasibility and structural stability, and finally making the design logic of strong disturbance heat transfer on the sidewall (13) and smooth flow at the peak and trough efficiently implemented, achieving the optimal matching of fin comprehensive performance and engineering practicality.

[0086] As a specific example, refer to Figure 7 , Figure 7 This is a visualization of the curve characteristics of a hyperbolic tangent function provided in one embodiment of this application. For example... Figure 7As shown, taking A=0.6 and k=1 as an example, the corresponding specific function is y(x) = 0.6*tanh(1*sin(x)). The hyperbolic tangent function tanh exhibits an S-shaped variation. When sin(x) takes ±1 (corresponding to the endpoints of the peaks / troughs), the slope of the tanh function curve with ±1 tends to be gentler (as shown in the image). Figure 7 The curve trend is gentler at the ends of the peaks and troughs of the heat exchanger fins (1). The curves at the ends of the peaks (11) and troughs (12) of the heat exchanger fins (1) are relatively small, which satisfies the design of smooth flow and resistance control.

[0087] Furthermore, sin(x) is in the middle interval between -1 and 1 (corresponding to the sidewall between the peak and the trough (13)), the absolute value of k*sin(x) is small, and at this time the slope of the tanh(1*sin(x)) curve is large (e.g. Figure 7 The curve corresponding to the sidewall (13) between the mid-wave peak and the trough is steeper, which corresponds to the larger curvature of the sidewall (13) of the heat exchanger fin (1), satisfying the design of strong disturbance to enhance heat transfer.

[0088] In another embodiment, the wave structure exhibits a curved characteristic in the lateral direction that satisfies the curve characteristic of the gradually expanding amplitude function; the expression for the gradually expanding amplitude function is: ; Among them, the amplitude preset by A, The preset amplitude adjustment coefficient is denoted by x, which represents the lateral coordinate of the heat exchanger fin (1) in the lateral direction. L is the total length of the heat exchanger fin (1) in the lateral direction, and y(x) represents the longitudinal coordinate of the heat exchanger fin (1) in the longitudinal direction.

[0089] In one embodiment, the amplitude, amplitude adjustment factor, and total length can all be preset and are not limited thereto. For example, L can be 25.4 mm; It can be 0.1, and A can be 0.6mm.

[0090] As an example, refer to Figure 8 and Figure 9 , Figure 8 This is a visualization of the curve characteristics of a gradually expanding amplitude function provided in one embodiment of this application; Figure 9 This is a top view of the curve characteristics of the wave structure of a heat exchanger fin provided in one embodiment of this application, corresponding to the curve characteristics under the condition of satisfying the gradually expanding wave amplitude function. For example... Figure 8 and Figure 9As shown, the periodic fluctuations of the gradually expanding amplitude function curve correspond to the wave structure of the fins, and the amplitude (the longitudinal bulge / depression amplitude) is not uniform, which is a characteristic of the gradually expanding amplitude function (distinguishing it from the previous constant amplitude function). Specifically, the gradually expanding amplitude function is a monotonically increasing amplitude function along the airflow direction. That is, the amplitude gradually increases along the airflow direction.

[0091] It should be noted that although each wave amplitude is not uniform, any sidewall (13) connecting adjacent wave crests (11) and troughs (12) also conforms to the structural characteristics of the first sidewall structure (131) connecting to the wave crest (11), the second sidewall structure (132) connecting to the wave trough (12), the length of the first sidewall structure (131) along the longitudinal direction being equal to the length of the second sidewall structure (132) along the longitudinal direction, the curvature of the first sidewall structure (131) gradually decreasing along the longitudinal direction, and the curvature of the second sidewall structure (132) gradually increasing along the longitudinal direction.

[0092] Among them, such as Figure 8 As shown, The value of varies with the horizontal coordinate x (decreasing from 1 to 0 and then increasing back to 1), therefore the amplitude exhibits a non-uniform distribution in the horizontal region. From Figure 8 It can be seen that when x is at one end of the horizontal direction (such as near x=-25), the vertical span of the curve's peaks / troughs is larger (larger amplitude). As x moves towards the other end of the horizontal direction (such as near x=0), the vertical span of the peaks / troughs gradually decreases (smaller amplitude).

[0093] It should be noted that for heat exchanger fins (1) whose wavy structure exhibits a curve characteristic that satisfies the gradually expanding amplitude function in the transverse direction, the airflow direction in the heat exchanger fins (1) is from low amplitude to high amplitude. For example, Figure 8 The arrows indicate the direction of airflow. When airflow passes through this wave structure with gradually increasing amplitude, the area with larger amplitude (the lateral end) generates stronger airflow disturbances, disrupting the thermal boundary layer. The area with smaller amplitude allows for smoother airflow and controls drag.

[0094] It should be noted that, referring to Figure 1When the airflow passes through the heat exchanger fins (1) corresponding to the sinusoidal function, the thermal boundary layer generated in the inlet region of the flow channel (the starting position where the airflow enters the heat exchanger fins (1)) is relatively thin. At this time, a small disturbance can enable the heat exchanger fins (1) to achieve efficient heat exchange with the airflow. However, the fixed amplitude of the sinusoidal function may cause excessive disturbance, resulting in unnecessary flow resistance. Furthermore, in the downstream region of the flow channel (where x gradually increases in the transverse direction), as the thermal boundary layer continues to thicken and the thermal resistance increases, the disturbance intensity of the constant amplitude cannot effectively destroy the boundary layer. Consequently, the traditional sinusoidal function heat exchanger fin (1) design arbitrarily causes the heat exchange capacity of the heat exchanger fin (1) surface to decrease along the flow direction, making it impossible for the overall heat exchange performance to reach the optimal state.

[0095] In this embodiment, the streamline shape of the heat exchanger fins (1) is constructed using a gradually expanding amplitude function. By introducing a monotonically increasing amplitude function along the flow direction, the smaller initial amplitude at the beginning of the flow channel (when x is small) adapts to the thinner thermal boundary layer at this time, providing appropriate disturbance to ensure heat transfer efficiency while minimizing unnecessary initial flow pressure loss. As the airflow moves downstream (along the lateral direction, x gradually increases), the thermal boundary layer gradually thickens and becomes the dominant thermal resistance. The synchronously increasing amplitude strengthens the contraction effect of the flow channel. Consequently, it can not only significantly improve the turbulence intensity of the flow field, but also penetrate the thickened boundary layer to continuously and forcefully disrupt its stable laminar sublayer. This dynamic disturbance strategy of weak at the beginning and strong at the end can overcome the heat transfer attenuation problem caused by insufficient disturbance after the airflow flows laterally in traditional designs, ensuring the high efficiency and uniformity of heat transfer intensity of the entire heat exchange surface, and realizing the design from passively adapting to the flow field to actively matching changes in thermal resistance.

[0096] In one embodiment, simulation calculations show that the heat exchanger fins (1) designed based on the gradually expanding amplitude function have an 8.0% increase in heat transfer factor and a 9.9% increase in heat transfer per unit volume. This result fully confirms that the heat exchanger fins (1) optimized by the gradually expanding amplitude function can achieve an improvement in heat transfer performance and heat transfer per unit volume, thus achieving the goal of significantly increasing heat transfer under the same equipment volume.

[0097] As a specific example, refer to Table 2, which shows the specific values ​​of heat exchanger fins (1), j, and heat exchange per unit volume of heat exchanger when the curve characteristics of the wave structure in the lateral direction satisfy the following functions respectively.

[0098] Table 2:

[0099] Since the visualizations of the inverse trigonometric function and the hyperbolic tangent function are similar, the trigonometric function will be used as an example for explanation. As shown in Table 2 above, Table 2 is a comparison of the performance of the heat exchanger fins (1) corresponding to different functions, covering the traditional sine function, as well as the improved inverse trigonometric function (k=1, k=2) and the gradually expanding amplitude function in this embodiment. The comparison dimensions include heat transfer, j heat transfer factor, and heat transfer per unit volume. As can be seen from the data, as the structure of the heat exchanger fins (1) iterates from the traditional sine function to the inverse trigonometric function (k increases) and the gradually expanding amplitude function, the heat transfer gradually increases from 0.2571W to 0.2824W, the j factor increases from 0.01234 to 0.01333, and the heat transfer per unit volume increases from 317629W / m 3 Increased to 348916W / m 3 This directly demonstrates the advantages of the new function-corresponding heat exchanger fins (1) in enhancing heat transfer, optimizing heat transfer and flow resistance compatibility (j-factor), and improving heat transfer efficiency per unit volume. For example, the j-factor is increased by 2% to 8%, and the heat transfer per unit volume is increased by about 10%.

[0100] In another embodiment, this embodiment also provides a design method for heat exchanger fins (1) based on a novel streamline function. Specifically, operating condition analysis and target setting can be performed in advance to clarify parameters such as air inlet velocity and temperature.

[0101] Taking the application scenario of refrigerator condenser as an example, the air inlet temperature (ambient temperature) is set at 32℃, the flow rate is controlled at 1-3m / s, and the design goal is to improve the heat exchange and heat exchange per unit volume, while maintaining the flow resistance unchanged or slightly increasing it while enhancing heat transfer.

[0102] Afterwards, a parameterized model of the fin can be established. In the streamline function selection stage, the target function (e.g., inverse trigonometric function, hyperbolic tangent function, and gradually expanding amplitude function) is selected from the preset function library. The preset criteria are: when it is necessary to strengthen the disturbance throughout the process, the inverse trigonometric function or hyperbolic tangent function should be selected first; or, when it is necessary to match the boundary layer development law, the gradually expanding amplitude function should be selected first, and the initial parameters of the function are set.

[0103] Furthermore, flow and heat transfer simulations can be performed using computational fluid dynamics software. By selecting control parameters such as shape control factor k and amplitude gradient coefficient, and calculating heat transfer factor j and heat transfer per unit volume through simulation, control parameters that meet the above criteria and achieve the required heat transfer factor j and heat transfer per unit volume can be obtained.

[0104] Based on the above design method, a parametric model (such as a streamline function expression) can be used to flexibly and scientifically adjust the various control parameters in the function expression based on boundary layer theory, providing a data foundation for improving heat transfer performance.

[0105] In another embodiment, reference Figure 10 ,like Figure 10 As shown, this application embodiment also provides a heat exchanger comprising the heat exchanger fins (1) of the above examples, and including: The refrigerant channel component (2) has heat exchanger fins (1) connected to its outer target surface; the outer target surface is parallel to the flow direction of the refrigerant in the refrigerant channel component (2).

[0106] Among them, the heat exchanger fins (1) and the refrigerant channel components (2) can be integrally formed by shaving.

[0107] In one embodiment, the flow direction is the direction in which the refrigerant flows inside the refrigerant channel component (2). For example, when the refrigerant channel component (2) is a flat tube, it is the direction in which the refrigerant flows through the flat tube cavity.

[0108] The aforementioned target outer surface is the outer surface of the refrigerant channel component (2) used to connect the heat exchanger fins (1), and the extension direction of the target outer surface is parallel to the flow direction of the refrigerant within the refrigerant channel component (2). For example, the target outer surface is the outer wall surface of one side of a flat tube, and its length direction is consistent with the flow direction of the refrigerant within the flat tube. This design allows the heat exchanger fins (1) to be adapted to the flow direction of the refrigerant, thereby more efficiently transferring heat between the refrigerant and the external airflow.

[0109] As an example, the target outer surface can be a surface formed in both the transverse direction (width of the heat exchanger) and the longitudinal direction (length of the heat exchanger). In the refrigerant channel component (2), the ratio of the length of the long side to the length of the short side forming the target outer surface is between 6 and 13.

[0110] It should be noted that limiting the length-to-width ratio of the target outer surface of the refrigerant channel component (2) to 6 to 13 can make it into a flat structure that is compatible with fin connections, which can ensure the uniformity of refrigerant flow, maximize the heat exchange contact area of ​​the fins, balance the strength of the channel structure, and help the heat exchanger to take into account both high-efficiency heat exchange and compact layout.

[0111] In this embodiment, a structure is adopted in which the target outer surface (parallel to the refrigerant flow direction) of the refrigerant channel component (2) is connected to the fins to achieve synergistic optimization of heat transfer performance and structural adaptability. The special curve shape of the heat exchanger fins (1) can enhance airflow disturbance, destroy the thermal boundary layer, and control flow resistance, laying the foundation for efficient heat exchange. Furthermore, the arrangement of the target outer surface parallel to the refrigerant flow direction can make the extension direction of the heat exchanger fins (1) precisely match the heat exchange path of the refrigerant flow and the external airflow, reduce flow field interference, maximize the heat transfer contact area between the fins and the channel component, reduce contact thermal resistance, and make the heat transfer between the refrigerant and the external airflow more direct and efficient.

[0112] In one embodiment, such as Figure 10 As shown, the refrigerant channel component (2) is provided with multiple support partitions (21), which are perpendicular to the outer surface of the target and divide the internal space of the refrigerant channel component (2) into multiple refrigerant flow channels (22).

[0113] The number of support partitions (21) can be preset and is not limited. The support partitions (21) can be evenly spaced inside the refrigerant channel component (2). As an example, the number of refrigerant flow channels (22) can be 3-6, which ensures the rationality of the refrigerant flow path while maintaining a compact structure.

[0114] This application also provides a refrigeration device, including a heat exchanger as shown in the example above.

[0115] The above are merely specific embodiments of this application, but the scope of protection of this application is not limited thereto. Any variations or substitutions that can be easily conceived by those skilled in the art within the scope of the technology disclosed in this application should be included within the scope of protection of this application. Therefore, the scope of protection of this application should be determined by the scope of the claims.

Claims

1. A heat exchanger fin, characterized in that, include: A wave structure extending in the transverse direction of the heat exchanger fins (1); The wave structure includes multiple alternating crest segments (11) and trough segments (12), and a sidewall (13) connecting adjacent crest segments (11) and trough segments (12). The crest segments (11) are convex along the longitudinal direction of the heat exchanger fins (1), and the trough segments (12) are concave along the longitudinal direction of the heat exchanger fins (1). The sidewall (13) includes a first sidewall structure (131) and a second sidewall structure (132) connected to each other. The first sidewall structure (131) is connected to the crest segment (11), and the second sidewall structure (132) is connected to the trough segment (12). The length of the first sidewall structure (131) along the longitudinal direction is equal to the length of the second sidewall structure (132) along the longitudinal direction. The curvature of the first sidewall structure (131) gradually decreases along the longitudinal direction, while the curvature of the second sidewall structure (132) gradually increases along the longitudinal direction. The curvature is used to quantify the degree of bending at the corresponding position in the wave structure, and the curvature is positively correlated with the degree of bending.

2. The heat exchanger fins according to claim 1, characterized in that, The curvature of the wave structure at the crest (11) and trough (12) is less than the first preset curvature, and the curvature at the boundary (133) between the first sidewall structure (131) and the second sidewall structure (132) is greater than the second preset curvature.

3. The heat exchanger fins according to claim 2, characterized in that, The ratio of the curvature at the endpoint to the curvature at the boundary (133) is between 0.2 and 1.

4. The heat exchanger fins according to any one of claims 1-3, characterized in that, The wave structure exhibits a curve characteristic in the lateral direction that satisfies the curve characteristic of an inverse trigonometric function; the expression of the inverse trigonometric function is: ； Where A is the preset amplitude, k is the preset shape control factor, x represents the lateral coordinate of the heat exchanger fin (1) along the lateral direction, and y(x) represents the longitudinal coordinate of the heat exchanger fin (1) along the longitudinal direction.

5. The heat exchanger fins according to claim 4, characterized in that, The shape control factor k ranges from 1 to 5.

6. The heat exchanger fins according to any one of claims 1-3, characterized in that, The wave structure exhibits a curve characteristic in the lateral direction that satisfies the curve characteristic of the hyperbolic tangent function; the expression of the hyperbolic tangent function is: ； Where A is the preset amplitude, k is the preset shape control factor, x represents the lateral coordinate of the heat exchanger fin (1) along the lateral direction, and y(x) represents the longitudinal coordinate of the heat exchanger fin (1) along the longitudinal direction.

7. The heat exchanger fins according to claim 6, characterized in that, The shape control factor k ranges from 1 to 5.

8. The heat exchanger fins according to any one of claims 1-3, characterized in that, The wave structure exhibits a curve characteristic in the lateral direction that satisfies the curve characteristic of the gradually expanding amplitude function; the expression of the gradually expanding amplitude function is: ； Among them, the amplitude preset by A, The amplitude adjustment coefficient is preset, x represents the lateral coordinate of the heat exchanger fin (1) in the lateral direction, L is the total length of the heat exchanger fin (1) along the lateral direction, and y(x) represents the longitudinal coordinate of the heat exchanger fin (1) along the longitudinal direction.

9. A heat exchanger, characterized in that, Including the heat exchanger fins as described in any one of claims 1-8, further comprising: A refrigerant channel component (2) is provided, wherein the heat exchanger fins (1) are connected to the target outer surface of the refrigerant channel component (2); the target outer surface is parallel to the flow direction of the refrigerant in the refrigerant channel component (2).

10. A refrigeration device, characterized in that, Includes the heat exchanger as described in claim 9.

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