Heat dissipation structure of heat exchanger and heat exchanger applying same

Abstract

The utility model discloses a heat radiator structure of heat exchanger and apply its heat exchanger, heat radiator structure of heat exchanger includes a plurality of for heat exchange fin group, and the fin group is equipped with the pipe body of required heat exchange in wear and tear. In the first direction along the pipe body axis direction, single fin group is provided with a plurality of evenly distributed heat exchange fins, and in the second direction along the heat exchange airflow flow path direction, the interval of adjacent heat exchange fins in the rear end fin group in the adjacent fin group, greater than the interval of adjacent heat exchange fins in the fin group of front end. Wherein, in the second direction, at least on the heat exchange fin in the foremost fin group, set up the first turbulence structure that can make heat exchange airflow turbulent, and at least on the heat exchange fin in the last end fin group, set up the second turbulence structure that can strip the condensate water on the heat exchange fin through heat exchange airflow. The utility model discloses can effectively improve the problem that the heat exchange effect of current heat exchanger is poor.

Description

Technical Field

[0001] This application relates to the field of heat dissipation structure technology for heat exchangers, and more particularly to a heat dissipation structure for a heat exchanger and a heat exchanger using the same. Background Technology

[0002] Finned heat exchangers, as core devices that enhance heat transfer efficiency by expanding the heat transfer surface area, play a crucial role in many fields such as heat pumps, air conditioning, automobiles, aerospace, and chemicals. Their core working principle is to significantly expand the heat transfer area through the finned structure, accelerating the heat transfer process between fluids (air, liquids, etc.) and solid surfaces.

[0003] However, under the existing technological system, the conventional path to improve heat exchange performance has significant technical bottlenecks:

[0004] Firstly, while traditional optimization methods such as increasing fin density or expanding equipment volume can increase the heat exchange area, they also lead to a non-linear increase in fluid flow resistance (pressure drop). This directly causes the fan's energy consumption to rise, which in turn leads to a decrease in the overall energy efficiency of the unit system.

[0005] Secondly, due to the complex and diverse unit structure design, it is difficult to effectively control the uniformity of fluid distribution in the fin gaps. The existence of local flow dead zones or high-speed scouring areas will significantly reduce the overall heat transfer performance of the heat exchanger.

[0006] Third, under low-temperature operating conditions, the higher the fin density, the exponentially higher the risk of surface frosting. Frosting not only clogs the air ducts and increases airflow resistance, but also forms a thermal resistance layer, severely weakening heat transfer efficiency and causing a significant decrease in the overall operating efficiency of the unit. Utility Model Content

[0007] The purpose of this utility model embodiment is to provide a heat dissipation structure for a heat exchanger and a heat exchanger using the same, which can solve the above-mentioned problems existing in the prior art.

[0008] To achieve the above objectives, this application adopts the following technical solution:

[0009] This invention provides a heat dissipation structure for a heat exchanger, comprising multiple fin assemblies for heat exchange. The fin assemblies are arranged in the flow path of the heat exchange airflow in the heat exchanger, and tubes for the required heat exchange are inserted through the fin assemblies.

[0010] In a first direction along the axis of the tube body, a single fin group is provided with a plurality of uniformly distributed heat exchange fins; and

[0011] In the second direction along the heat exchange airflow path, the spacing between adjacent heat exchange fins in the rear fin group of adjacent fin groups is greater than the spacing between adjacent heat exchange fins in the front fin group.

[0012] In the second direction, at least the heat exchange fins in the foremost fin group are provided with a first turbulence structure that can generate turbulence in the heat exchange airflow, and at least the heat exchange fins in the endmost fin group are provided with a second turbulence structure that can strip condensate from the heat exchange fins by the heat exchange airflow.

[0013] On the one hand, in adjacent fin groups, the spacing between adjacent heat exchange fins in the rear fin group is an integer multiple of the spacing between adjacent heat exchange fins in the front fin group.

[0014] On the one hand, in adjacent fin groups, the first heat exchange fin in the rear fin group is spaced apart from the first heat exchange fin in the front fin group.

[0015] On the one hand, the first turbulence structure includes corrugated grooves disposed on the surface of the heat exchange fins.

[0016] On the one hand, the corrugated grooves are arranged concentrically with the pipe body, and multiple corrugated grooves extend outward along the center of the pipe body.

[0017] On one hand, the second turbulence structure includes turbulence protrusions disposed on the surface of the heat exchange fins.

[0018] On one hand, the turbulence protrusion includes a plurality of parallel elongated protrusions, and the protrusions are arranged at an angle to the second direction.

[0019] On the one hand, the length of the protrusion increases sequentially in the second direction, and an opening is provided at the middle position of the outermost protrusion to allow heat exchange airflow to pass through.

[0020] On the one hand, when the number of tubes in a single fin group is multiple, the multiple tubes are spaced apart on the heat exchange fins.

[0021] This utility model also provides a heat exchanger, which includes the heat dissipation structure of any of the heat exchangers described above.

[0022] The beneficial effects of this application are as follows:

[0023] This utility model provides a heat dissipation structure for a heat exchanger and a heat exchanger using the same, wherein the spacing of the heat exchange fins in the fin assembly is gradually increased from dense to sparse along the direction of airflow.

[0024] Increase the density of heat exchange fins at the front end to improve heat exchange efficiency. Increase the spacing of the heat exchange fins at the rear end to reduce wind resistance and improve defrosting efficiency.

[0025] Meanwhile, the staggered arrangement and gradient protrusion structure break the airflow inertia, reduce the flow dead zone and high-speed scouring, and improve the surface temperature uniformity of the heat exchange fins and the utilization rate of the heat exchange area.

[0026] In low-temperature environments, the large spacing and staggered gap at the rear end effectively reduce the risk of frosting and extend the frosting cycle. Furthermore, in high-humidity scenarios, the end-effector structure can quickly remove condensate, thus effectively preventing channel blockage and corrosion. Attached Figure Description

[0027] The present application will now be described in further detail with reference to the accompanying drawings and embodiments.

[0028] Figure 1 This is a schematic diagram of the overall structure of a heat exchanger for the present invention.

[0029] Figure 2 This is a schematic diagram of the heat dissipation structure of a heat exchanger according to this utility model from another perspective.

[0030] Figure 3 This is a schematic diagram of the fin arrangement structure of a heat exchanger heat dissipation structure according to the present invention.

[0031] Figure 4 This is a schematic diagram of the first turbulence structure of the heat dissipation structure of a heat exchanger according to the present invention;

[0032] Figure 5 This is a schematic diagram of the second turbulence structure of a heat exchanger according to the present invention.

[0033] In the picture:

[0034] 100. Fin assembly; 110. Heat exchange fins; 111. First flow-around structure; 112. Second flow-around structure; 1120. Protrusion; 1121. Opening;

[0035] 200. Pipe body. Detailed Implementation

[0036] To make the technical problems solved by this application, the technical solutions adopted, and the technical effects achieved clearer, the technical solutions of the embodiments of this application are further described in detail below. Obviously, the described embodiments are only some embodiments of this application, and not all embodiments. Based on the embodiments in this application, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this application.

[0037] In the description of this application, unless otherwise expressly specified and limited, the terms "connected," "linked," and "fixed" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components. Those skilled in the art can understand the specific meaning of the above terms in this utility model based on the specific circumstances.

[0038] In this application, unless otherwise expressly specified and limited, "above" or "below" the second feature can include direct contact between the first and second features, or contact between the first and second features through another feature between them. Furthermore, "above," "over," and "on top" of the second feature includes the first feature being directly above or diagonally above the second feature, or simply indicates that the first feature is at a higher horizontal level than the second feature. "Below," "below," and "under" the second feature includes the first feature being directly below or diagonally below the second feature, or simply indicates that the first feature is at a lower horizontal level than the second feature.

[0039] In the description herein, it should be understood that the terms "upper," "lower," "left," "right," and other orientations or positional relationships are used only for ease of description and simplification of operation, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this application. Furthermore, the terms "first" and "second" are used merely for descriptive distinction and have no special meaning.

[0040] Furthermore, it should be understood that although this specification describes embodiments, not every embodiment contains only one independent technical solution. This narrative style of the specification is merely for clarity. Those skilled in the art should consider the specification as a whole, and the technical solutions in each embodiment can also be appropriately combined to form other embodiments that can be understood by those skilled in the art.

[0041] Please see Figure 1 and Figure 3 This utility model discloses a heat dissipation structure for a heat exchanger, which can be used to improve the problem of poor heat exchange performance in current heat exchangers. Specifically, the heat dissipation structure of the heat exchanger disclosed in this utility model includes multiple fin groups 100 for heat exchange. The fin groups 100 are arranged in the flow path of the heat exchange airflow in the heat exchanger, and the tubes for the required heat exchange are inserted through the fin groups 100.

[0042] It should be noted that when multiple tubes are installed in a single fin assembly 100, these tubes are spaced apart on the heat exchange fins 110. When heat is transferred from the tubes to the fin assembly 100, and when the airflow passes through the heat exchange fin assembly 100, heat exchange can be achieved efficiently between the tubes and the heat exchange fins 110, further removing heat from the fin assembly 100.

[0043] Specifically, it is permissible to define the direction along the tube axis as the first direction and the direction along the heat exchange airflow path as the second direction. In the first direction, a single fin group 100 is provided with a plurality of uniformly distributed heat exchange fins 110, and in the second direction, the spacing between adjacent heat exchange fins 110 in the rear fin group 100 of adjacent fin groups 100 is greater than the spacing between adjacent heat exchange fins 110 in the front fin group 100.

[0044] Understandably, in the second direction of airflow, the use of a gradually varying spacing structure for the heat exchange fins 110 (dense at the front, sparse at the back) can significantly reduce the flow resistance at the rear while ensuring efficient heat exchange at the front end. Compared to traditional evenly spaced heat exchange fins 110, this design effectively suppresses the nonlinear increase in pressure drop caused by the increased density of the heat exchange fins 110, thereby reducing fan energy consumption and improving the overall energy efficiency of the unit system. Simultaneously, the uniform layout of the heat exchange fins 110 in the first direction ensures a stable heat exchange foundation for the single-row tube body, while the gradually varying spacing design in the second direction guides the airflow to be more evenly distributed across the gaps between the heat exchange fins 110 by dynamically adjusting the flow channel cross-sectional area. This effectively eliminates local flow dead zones and high-speed scouring areas caused by abrupt changes in the flow channel in traditional structures, reduces heat transfer blind zones, and improves the overall utilization efficiency of the heat exchanger surface.

[0045] Furthermore, under low-temperature conditions, the denser heat exchange fins 110 at the front end achieve rapid heat exchange through a large heat exchange area, while the increased spacing of the heat exchange fins 110 at the rear end reduces the risk of frosting. Specifically, on the one hand, the airflow at the rear end experiences a relatively higher temperature after passing through the front end for heat exchange, thus raising the frosting threshold. On the other hand, the larger spacing reduces the blockage effect of frost accumulation on the air duct, maintaining a smoother airflow path even if frosting occurs, avoiding the attenuation of heat transfer efficiency due to frost thermal resistance, and significantly improving operational stability in low-temperature environments.

[0046] Please see Figure 1 and Figure 3 In one embodiment, in adjacent fin groups 100, the spacing between adjacent heat exchange fins 110 in the rear fin group 100 is an integer multiple of the spacing between adjacent heat exchange fins 110 in the front fin group 100. Simultaneously, in adjacent fin groups 100, the first heat exchange fin 110 in the rear fin group 100 is spaced apart from the first heat exchange fin 110 in the front fin group 100.

[0047] Specifically, the spacing of the rear heat exchange fins 110 increases in integer multiples of the front end (e.g., 2 times, 3 times), forming a quantifiable flow channel expansion gradient. Compared to irregular gradual changes, this makes it easier to accurately calculate the pressure drop using a fluid dynamics model, avoiding local eddies caused by abrupt changes in spacing. Simultaneously, while ensuring efficient heat exchange with the high-density front heat exchange fins 110, the large-spacing flow channel at the rear significantly reduces overall airflow resistance, resulting in a stepwise decrease in fan energy consumption as the spacing increases.

[0048] Furthermore, by staggering the first and second heat exchange fins 110 of the front and rear fin groups 100, the inertial airflow path of the traditional aligned arrangement can be broken, forcibly guiding the airflow to form three-dimensional disturbances in the gaps between the heat exchange fins 110, increasing turbulence, and eliminating the flow dead zone and boundary layer separation phenomenon of a single row of heat exchange fins 110. At the same time, the staggered structure allows the airflow to more evenly scour the surface of each heat exchange fin 110, avoiding local heat exchange blind zones caused by airflow deviation in the traditional structure. The integer multiple spacing at the rear provides a wider defrosting channel, and even if frost forms, basic ventilation can be maintained through the staggered gaps, preventing frost layers from laterally bridging and blocking the air duct.

[0049] Please see Figures 1 to 5 In one embodiment, in order to improve the actual heat exchange effect of the device during actual use, in the second direction, at least on the heat exchange fins 110 in the foremost fin group 100, a first turbulence structure that can generate turbulence in the heat exchange airflow is provided, and at least on the heat exchange fins 110 in the last fin group 100, a second turbulence structure that can strip condensate from the heat exchange fins 110 by the heat exchange airflow is provided.

[0050] Specifically, the first turbulence structure includes corrugated grooves disposed on the surface of the heat exchange fins 110. The corrugated grooves are arranged concentrically with the tube body, and multiple corrugated grooves extend outward along the center of the tube body.

[0051] Understandably, by setting concentric radial corrugated grooves to forcibly cut the airflow boundary layer, the high-speed heat exchange airflow at the front end generates periodic disturbances, forming turbulent vortices. Compared to smooth heat exchange fins 110, this can effectively improve the local convective heat transfer coefficient.

[0052] Specifically, the second turbulence structure includes turbulence protrusions disposed on the surface of the heat exchange fins 110. The turbulence protrusions include a plurality of parallel elongated protrusions 1120, and the protrusions 1120 are disposed at an angle to the second direction.

[0053] Understandably, the second turbulence structure disrupts the surface tension of the liquid film, allowing condensate to quickly peel off the surface of the heat exchange fins 110 under the action of airflow, thus preventing droplets from coalescing and forming a water film that blocks the flow channel.

[0054] Based on this, the first turbulence structure in the front-end fin assembly 100 can improve heat exchange efficiency while increasing flow resistance slightly. And the second flow-around structure 112 in the rear-end fin assembly 100 can offset the additional pressure drop caused by condensate accumulation, maintaining the stability of the overall system resistance characteristics.

[0055] Please see Figure 5 In one embodiment, the length of the protrusion 1120 increases sequentially in the second direction, and an opening 1121 is provided at the middle position of the outermost protrusion 1120 to allow heat exchange airflow to pass through.

[0056] Specifically, by progressively increasing the length of the protrusion 1120 along the airflow direction, a "short at the front and long at the back" flow channel expansion gradient is formed, gradually increasing the cross-sectional area of ​​the airflow. This effectively reduces local turbulence losses and avoids vortex separation and additional pressure drop caused by sudden changes in the flow channel cross-sectional area.

[0057] Based on this, the present invention also provides a heat exchanger, which may include the heat dissipation structure of the heat exchanger provided in any of the above embodiments.

[0058] In summary, this utility model provides a heat dissipation structure for a heat exchanger and a heat exchanger using the same. By gradually increasing the spacing of the heat exchange fins 110 in the fin assembly 100 along the airflow direction, the heat exchange efficiency is improved by increasing the density of the heat exchange fins 110 at the front end. Increasing the spacing of the heat exchange fins 110 at the rear end reduces wind resistance and improves defrosting efficiency. Simultaneously, the staggered arrangement and gradient protrusion structure break the airflow inertia, reducing dead zones and high-speed scouring, thus improving the surface temperature uniformity of the heat exchange fins 110 and the utilization rate of the heat exchange area. In low-temperature environments, the large spacing and staggered gaps at the rear end reduce the risk of frosting and extend the frosting cycle; and in high-humidity scenarios, the end-stage turbulence structure quickly removes condensate, effectively preventing channel blockage and corrosion.

[0059] The technical principles of this application have been described above with reference to specific embodiments. These descriptions are merely for explaining the principles of this application and should not be construed as limiting the scope of protection of this application in any way. Based on this explanation, those skilled in the art can readily conceive of other specific embodiments of this application without inventive effort, and these embodiments will all fall within the scope of protection of this application.

Claims

1. A heat dissipation structure for a heat exchanger, comprising a plurality of fin groups (100) for heat exchange, wherein the fin groups (100) are disposed in the flow path of the heat exchange airflow in the heat exchanger, and wherein a tube for heat exchange is inserted through the fin group (100), characterized in that, In a first direction along the axis of the tube body, a single fin assembly (100) is provided with a plurality of uniformly distributed heat exchange fins (110); and In the second direction along the heat exchange airflow path, the spacing between adjacent heat exchange fins (110) in the rear fin group (100) of the adjacent fin group (100) is greater than the spacing between adjacent heat exchange fins (110) in the front fin group (100). In the second direction, at least on the heat exchange fins (110) of the foremost fin group (100), a first turbulence structure is provided that can generate turbulence in the heat exchange airflow, and at least on the heat exchange fins (110) of the end fin group (100), a second turbulence structure is provided that can strip condensate from the heat exchange fins (110) by the heat exchange airflow.

2. The heat dissipation structure of the heat exchanger according to claim 1, characterized in that, In adjacent fin groups (100), the spacing between adjacent heat exchange fins (110) in the rear fin group (100) is an integer multiple of the spacing between adjacent heat exchange fins (110) in the front fin group (100).

3. The heat dissipation structure of the heat exchanger according to claim 1, characterized in that, In adjacent fin groups (100), the first heat exchange fin (110) in the rear fin group (100) is spaced apart from the first heat exchange fin (110) in the front fin group (100).

4. The heat dissipation structure of the heat exchanger according to claim 1, characterized in that, The first turbulence structure includes corrugated grooves disposed on the surface of the heat exchange fins (110).

5. The heat dissipation structure of the heat exchanger according to claim 4, characterized in that, The corrugated grooves are arranged concentrically with the pipe body, and multiple corrugated grooves extend outward along the center of the pipe body.

6. The heat dissipation structure of the heat exchanger according to claim 1, characterized in that, The second turbulence structure includes turbulence protrusions disposed on the surface of the heat exchange fins (110).

7. The heat dissipation structure of the heat exchanger according to claim 6, characterized in that, The turbulence protrusion includes a plurality of parallel elongated protrusions (1120), and the protrusions (1120) are arranged at an angle to the second direction.

8. The heat dissipation structure of the heat exchanger according to claim 7, characterized in that, The length of the protrusion (1120) increases sequentially in the second direction, and an opening (1121) is provided at the middle position of the outermost protrusion (1120) to allow the heat exchange airflow to pass through.

9. The heat dissipation structure of the heat exchanger according to claim 1, characterized in that, When the number of tubes in a single fin group (100) is multiple, the multiple tubes are spaced apart on the heat exchange fins (110).

10. A heat exchanger, characterized in that, It includes the heat dissipation structure of the heat exchanger as described in any one of claims 1 to 9.

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