Heat exchanger and air conditioner with good comprehensive performance

Abstract

This utility model belongs to the field of air conditioning technology, specifically providing a heat exchanger and air conditioner with better overall performance. This utility model aims to solve the problem of poor overall performance in existing heat exchangers. To this end, the heat exchanger of this utility model includes refrigerant pipes and multiple fins. The diameter d of the refrigerant pipe is selected from any value between 5.8mm and 6.5mm, and the refrigerant pipe includes multiple pipe segments. The distance H between two adjacent pipe segments is selected from any value between 17.1mm and 22.5mm. Multiple fins are penetrated by the multiple pipe segments, and the width W of the fins is selected from any value between 18mm and 23mm. The distance L between two adjacent fins is selected from any value between 0.8mm and 1.5mm. This utility model effectively avoids increased air resistance while ensuring heat exchange, thus improving the overall performance of the heat exchanger.

Description

Technical Field

[0001] This utility model belongs to the field of air conditioning technology, specifically providing a heat exchanger and air conditioner with better overall performance. Background Technology

[0002] A heat exchanger is a major component of an air conditioner, used to heat or cool the air flowing through the air conditioner, thereby heating or cooling the environment in which the air conditioner is located.

[0003] Existing heat exchangers often struggle to simultaneously balance heat exchange efficiency and air resistance in their structural parameter selection. On one hand, increasing fin density or refrigerant pipe density solely to improve heat exchange efficiency can significantly increase air resistance, leading to increased fan energy consumption and higher system operating costs. On the other hand, increasing fin spacing or refrigerant pipe spacing to reduce air resistance sacrifices some heat exchange area, thereby reducing heat exchange efficiency.

[0004] Therefore, the overall performance of existing heat exchangers is poor and needs further improvement. Utility Model Content

[0005] One objective of this invention is to solve the problem of poor overall performance of existing heat exchangers.

[0006] To achieve the above objectives, the present invention provides a heat exchanger in a first aspect, comprising:

[0007] The refrigerant pipe has a diameter d selected from any value between 5.8 mm and 6.5 mm, and the refrigerant pipe includes multiple pipe segments, with the pipe spacing H between two adjacent pipe segments selected from any value between 17.1 mm and 22.5 mm.

[0008] Multiple fins are penetrated by the multiple tube segments, the width W of the fins is selected from any value from 18mm to 23mm, and the fin spacing L between two adjacent fins is selected from any value from 0.8mm to 1.5mm.

[0009] Those skilled in the art have creatively discovered that by selecting the tube spacing H between two adjacent tube sections from any value between 17.1 mm and 22.5 mm, the fin width W from any value between 18 mm and 23 mm, and the fin spacing L between two adjacent fins from any value between 0.8 mm and 1.5 mm, the heat exchanger can effectively avoid increasing wind resistance while maintaining heat exchange efficiency, achieving two goals at once. This solves the problem of poor overall performance of existing heat exchangers and achieves unexpected technical results.

[0010] Optionally, the fin spacing L between two adjacent fins is determined based on the tube spacing H between two adjacent tube segments and the fin width W, in order to balance the heat exchange efficiency and air resistance of the heat exchanger.

[0011]

[0012] Where a is a correction coefficient, selected from any value between 0.5 and 1; b is a correction variable, selected from any value between 0.1 and 0.6.

[0013] Optionally, the pipe diameter d of each of the pipe sections, where 0.743≤H / W≤1.25, is selected from any value between 5.9 mm and 6.2 mm.

[0014] Optionally, the pipe diameter d of each of the pipe segments is selected from any value from 5.9 mm to 6.2 mm; and / or, the fin spacing L between two adjacent fins is selected from any value from 1.1 mm to 1.5 mm.

[0015] Optionally, the length direction of the tube spacing H is perpendicular to the width direction of the fin.

[0016] Optionally, each fin includes a fin body and a plurality of tube clamps disposed on the fin body, wherein the tube clamps are provided with through holes through which the tube segment passes; the height of the tube clamps protruding from the fin body is less than or equal to the fin spacing L between two adjacent fins.

[0017] Optionally, the clamp portion abuts against the adjacent fin; and / or, a plurality of clamp portions are respectively provided on opposite sides of the fin portion.

[0018] Optionally, the windward side and / or the windward side of the sheet portion are provided with a concave-convex structure extending along the length direction of the sheet portion to increase the structural strength of the sheet portion; the ratio of the height of the protrusion of the concave-convex structure protruding from the sheet portion to the thickness of the sheet portion is selected from any value from 1 to 3.5 to avoid excessive wind resistance of the protrusion.

[0019] Optionally, the ratio of the height of the protrusion of the protrusion of the concave-convex structure from the sheet portion to the thickness of the sheet portion is selected from any value between 2 and 3; and / or, the tangent line between the windward end of the sheet portion and the protrusion closest to the windward end on the windward side is denoted as the windward tangent line, and the angle between the windward tangent line and the sheet portion is denoted as α; the tangent line between the windward end of the sheet portion and the side of the clamp portion away from the sheet portion is denoted as the clamp tangent line, and the angle between the clamp tangent line and the sheet portion is denoted as β, where α > 0.7β.

[0020] The present invention provides an air conditioner in a second aspect, comprising the heat exchanger described in any one of the first aspects.

[0021] Based on the foregoing description, those skilled in the art will understand that in the aforementioned technical solution of this utility model, by selecting the pipe spacing H between two adjacent pipe sections from any value between 17.1 mm and 22.5 mm, the fin width W from any value between 18 mm and 23 mm, and the fin spacing L between two adjacent fins from any value between 0.8 mm and 1.5 mm, the heat exchanger can effectively avoid increasing wind resistance while simultaneously ensuring heat exchange, achieving two goals at once. Therefore, this utility model solves a technical problem that people have long desired to solve but have been unable to achieve successfully, namely, the problem of poor overall performance of existing heat exchangers, and achieves unexpected technical results.

[0022] Furthermore, through extensive creative work and data verification, those skilled in the art have finally obtained a formula for determining the fin spacing L between two adjacent fins based on the pipe spacing H between two adjacent pipe sections and the fin width W. This greatly improves the design efficiency of heat exchangers for those skilled in the art and shortens the design time for heat exchangers.

[0023] Furthermore, by providing a concave-convex structure extending along the length of the plate on the windward side of the plate, not only is the structural strength of the plate increased, but the boundary layer adhering to the surface of the plate is also broken, allowing more air to contact and exchange heat with the plate, thereby further improving the heat exchanger's heat exchange efficiency. By making the ratio of the height of the protrusion of the concave-convex structure protruding from the plate to the thickness of the plate selected from any value from 1 to 3.5, especially any value selected from 2 to 3, excessive wind resistance of the protrusion is avoided, and wind noise when air flows through the protrusion is reduced.

[0024] Furthermore, by denoteing the tangent between the windward end of the fin and the protrusion closest to the windward end on the windward side as the windward tangent, and the angle between the windward tangent and the fin as α; and by denoteing the tangent between the windward end of the fin and the side of the clamp portion away from the fin as the clamp tangent, and the angle between the clamp tangent and the fin as β, and ensuring that α > 0.7β, the change in airflow direction when passing through the protrusion is sufficiently large, thereby disturbing the airflow. The disturbed airflow will generate certain fluctuations when flowing between two adjacent fins. This not only increases the airflow path compared to unfluctuated laminar flow, but also increases the heat exchange time between the air and the fins, thus improving the heat exchanger's heat exchange performance.

[0025] Other beneficial effects of this utility model will be described in detail below with reference to the accompanying drawings, so that those skilled in the art can more clearly understand the improvement purpose, features and advantages of this utility model. Attached Figure Description

[0026] To more clearly illustrate the technical solution of this utility model, some embodiments of this utility model will be described below with reference to the accompanying drawings. Those skilled in the art should understand that the same reference numerals may indicate the same or similar components or parts in different drawings; the drawings of this utility model are not necessarily drawn to scale. In the drawings:

[0027] Figure 1 This is a schematic diagram of the structure of a heat exchanger provided by this utility model;

[0028] Figure 2 This is a partial top view of the fins in some embodiments of this utility model;

[0029] Figure 3 yes Figure 2 A cross-sectional view of the middle fin along the AA direction (showing two fins);

[0030] Figure 4 yes Figure 2 A cross-sectional view of the middle fin along the AA direction (showing one fin);

[0031] Figure 5 yes Figure 4 An illustration of the angle markings on the left side of the dashed line on the median fin;

[0032] Figure 6 yes Figure 4 Another angle marking on the left side of the dotted line on the median fin;

[0033] Figure 7 This is a simulation diagram showing the effect of the ratio of the refrigerant pipe spacing H to the fin width W on the fin heat exchange efficiency provided by this utility model.

[0034] Figure 8 This is a wind speed field contour map when H / W = 0.97;

[0035] Figure 9 This is a wind speed field contour map when H / W = 0.7;

[0036] Figure 10 This is a simulation diagram showing the effect of the fin spacing L between fins on the fin heat transfer efficiency provided by this utility model.

[0037] Figure 11 This is a simulation diagram showing the effect of the fin spacing L between fins on the pressure drop efficiency between the inlet and outlet of the fins, provided by this utility model.

[0038] Figure 12 This is a schematic diagram of an air conditioner provided by this utility model.

[0039] Explanation of reference numerals in the attached figures:

[0040] 001. Heat exchanger;

[0041] 100. Refrigerant pipe; 110. Pipe section;

[0042] 200. Fin; 210. Fin body; 211. Concave-convex structure; 2111. Protrusion; 2112. Recess; 220. Tube clamp; 221. Through hole;

[0043] T1, windward tangent; T2, pipe clamp tangent;

[0044] 002, Air conditioner; 300, Indoor unit of air conditioner; 400, Outdoor unit of air conditioner. Detailed Implementation

[0045] Those skilled in the art should understand that the embodiments described below are merely some embodiments of the present invention, and not all embodiments of the present invention. These embodiments are intended to explain the technical principles of the present invention and are not intended to limit the scope of protection of the present invention. Based on the embodiments provided by the present invention, all other embodiments obtained by those skilled in the art without creative effort should still fall within the scope of protection of the present invention.

[0046] It should be noted that in the description of this utility model, terms such as "center," "upper," "lower," "top," "bottom," "left," "right," "vertical," "horizontal," "inner," and "outer," which indicate direction or positional relationships, are based on the direction or positional relationships shown in the accompanying drawings. These are used merely for ease of description and do not indicate or imply that the corresponding device or element must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this utility model. Furthermore, the terms "first," "second," and "third" are used for descriptive purposes only and should not be construed as indicating or implying relative importance.

[0047] Furthermore, it should be noted that, in the description of this utility model, unless otherwise explicitly specified and limited, the terms "installation," "connection," and "joining" should be interpreted broadly. For example, they can refer to fixed connections, detachable connections, or integral connections; they can refer to mechanical connections or electrical connections; they can refer to direct connections or indirect connections through an intermediate medium; and they can refer to the internal connection of two components. Those skilled in the art can understand the specific meaning of the above terms in this utility model according to the specific circumstances. For example, unless otherwise specified, the terms "installation," "connection," "joining," and "fixing" can specifically refer to any feasible connection form such as bolt connection, screw connection, welding, insertion, riveting, fusion welding, or snap-fit.

[0048] Furthermore, it should be noted that in the description of this utility model, mm represents millimeter, cm represents centimeter, and m represents meter.

[0049] Furthermore, it should be noted that in the description of this utility model, the terms "coldness" and "heat" are two descriptions of the same physical state. That is, the higher the "coldness" of a target object (e.g., evaporator, air, condenser, etc.), the lower its "heat," and vice versa. A target object absorbs "coldness" while releasing "heat," and releases "coldness" while absorbing "heat." A target object retains "coldness" or "heat" to maintain its current temperature. "Refrigeration" and "heat absorption" are two descriptions of the same physical phenomenon; that is, a target object (e.g., evaporator) absorbs heat while refrigerating.

[0050] like Figure 1 As shown, the heat exchanger 001 of this utility model includes a refrigerant pipe 100 and fins 200. The refrigerant pipe 100 and the fins 200 are thermally connected, specifically, they are in contact with each other and fixed together by means of clamping, welding, etc., so that heat can be transferred between the refrigerant pipe 100 and the fins 200. That is, heat can be conducted from the refrigerant pipe 100 to the fins 200, or from the fins 200 to the refrigerant pipe 100.

[0051] It should be noted that this utility model Figure 1 The heat exchanger 001 shown is intended to illustrate the structure of the heat exchanger 001 and does not imply that the heat exchanger 001 of this utility model is only of this one form. Those skilled in the art can, as needed, configure the fins 200 of the heat exchanger 001 of this utility model as corrugated fins, flat fins, open fins, etc., and can also make at least one side of the circumferential edge of the fins 200 have an uneven structure. Furthermore, the pipe segments 110 through which the refrigerant pipe 100 passes on the fins 200 can be arranged in one row, two rows, three rows, or more rows. In this utility model, the pipe segments 110 in the same row are along the length direction of the fins 200 (e.g., ...). Figure 1 and Figure 2 (As shown). Furthermore, a pipe segment 110 in a certain column can be aligned with or misaligned with the nearest pipe segment 110 in the adjacent column (e.g., ...). Figure 8 and Figure 9 (As shown).

[0052] For example, in Figures 2 to 6 In the illustrated embodiment, the fin 200 is a flat fin, and both sides of the fin 200 in the width direction are respectively provided with concave and convex structures 211 extending along the length direction of the fin body 210. Only one row of refrigerant pipe 100 segments 110 is arranged on the fin 200. Figures 2 to 6 The illustrated embodiments are intended to clearly and concisely explain the heat exchanger 001 and fins 200 protected by this invention, so as to facilitate understanding by those skilled in the art. Furthermore, Figure 2The two rows of arrows on the left and right sides of the middle fin 200 are used to indicate the direction of wind flow, so as to help those skilled in the art understand the technical solution of this utility model.

[0053] For example, in Figure 8 and Figure 9 In the wind speed field cloud diagram shown, two rows of refrigerant pipes 100 are arranged on the fin 200, with pipe sections 110. Figure 8 and Figure 9 The wind speed field cloud map shown is intended to illustrate the changes in wind speed on opposite sides of pipe segment 110, and the changes when flowing through two pipe segments 110.

[0054] like Figure 1 and Figure 2 As shown, in some embodiments of this utility model, the diameter d of the refrigerant pipe 100 is selected from any value from 5.8mm to 6.5mm, the refrigerant pipe 100 includes a plurality of pipe segments 110, and the pipe distance H between two adjacent pipe segments 110 is selected from any value from 17.1mm to 22.5mm.

[0055] from Figure 2 As can be seen, the length direction of the tube spacing H is perpendicular to the width direction of the fin 200, so that the tube segments 110 in each row are arranged along the length direction of the fin 200. Of course, in other embodiments of this utility model, those skilled in the art can also, as needed, make the length direction of the tube spacing H form a certain angle with the width direction of the fin 200, so that the tube segments 110 in each row are arranged obliquely on the fin 200.

[0056] The pipe diameter d can be any feasible value such as 5.8mm, 5.85mm, 5.9mm, 6.0mm, 6.01mm, 6.2mm, 6.3mm, or 6.5mm. Furthermore, the pipe diameter d can be the size of the refrigerant pipe 100 before assembly with the fins 200, or the size after assembly with the fins 200.

[0057] Furthermore, the pipe diameter d of each pipe section 110 is selected from any value between 5.9mm and 6.2mm, specifically any feasible value such as 5.9mm, 5.95mm, 5.98mm, 6.0mm, 6.03mm, 6.045mm, 6.05mm, 6.08mm, 6.12mm, 6.15mm, 6.2mm, etc.

[0058] In some embodiments of this utility model, the pipe spacing H can be any feasible value such as 17.1mm, 17.2mm, 17.5mm, 18.1mm, 18.6mm, 19.1mm, 19.55mm, 19.8mm, 20.0mm, 20.3mm, 20.7mm, 20.9mm, 21.3mm, 21.8mm, 22.0mm, 22.35mm, 22.4mm, 22.5mm, etc.

[0059] like Figures 1 to 3 As shown, in some embodiments of this utility model, there are multiple fins 200, each penetrated by multiple tube segments 110. The width W of the fin 200 is selected from any value between 18 mm and 23 mm, and the fin spacing L between two adjacent fins 200 is selected from any value between 0.8 mm and 1.5 mm.

[0060] The width W of the fin 200 can be any feasible value such as 18mm, 18.5mm, 19mm, 19.8mm, 20.0mm, 20.5mm, 21.0mm, 21.3mm, 22.0mm, 22.7mm, or 23mm.

[0061] The spacing L can be any feasible value such as 0.8mm, 0.85mm, 0.87mm, 0.9mm, 0.93mm, 0.97mm, 1.0mm, 1.05mm, 1.1mm, 1.15mm, 1.2mm, 1.25mm, 1.3mm, 1.38mm, 1.4mm, 1.44mm, or 1.5mm.

[0062] Furthermore, the fin spacing L between two adjacent fins 200 is selected from any value between 1.1mm and 1.5mm, specifically any feasible value such as 1.1mm, 1.13mm, 1.14mm, 1.2mm, 1.26mm, 1.3mm, 1.38mm, 1.4mm, 1.42mm, 1.45mm, 1.48mm, 1.5mm, etc.

[0063] In some embodiments of this utility model, by selecting the pipe spacing H between two adjacent pipe sections 110 from any value between 17.1 mm and 22.5 mm, the width W of the fins 200 from any value between 18 mm and 23 mm, and the fin spacing L between two adjacent fins 200 from any value between 0.8 mm and 1.5 mm, the heat exchange of the heat exchanger 001 is considered while effectively avoiding an increase in wind resistance, achieving two goals at once. Therefore, this utility model solves a technical problem that people have long desired to solve but have been unable to achieve successfully, namely, the problem of poor overall performance of existing heat exchangers 001, and achieves unexpected technical effects.

[0064] Furthermore, in some embodiments of this utility model, the fin spacing L between two adjacent fins 200 is determined based on the pipe spacing H between two adjacent pipe sections 110 and the width W of the fins 200, in order to balance the heat exchange efficiency and air resistance of the heat exchanger 001.

[0065]

[0066] Where 'a' is the correction coefficient, selected from any value between 0.5 and 1, specifically any feasible value such as 0.5, 0.7, 0.8, 0.9, 1, etc. 'b' is the correction variable, with the same unit as H and W, selected from any value between 0.1 and 0.6, specifically any feasible value such as 0.1, 0.15, 0.2, 0.32, 0.38, 0.4, 0.43, 0.5, 0.51, 0.53, 0.56, 0.6, etc.

[0067] For example, when a = 0.8 and b = 0.3 mm, if H = 18 mm and W = 20 mm, substituting these values ​​into the above formula yields L = 1.02 mm. When a = 0.9 and b = 0.4 mm, if H = 21 mm and W = 21 mm, substituting these values ​​into the above formula yields L = 1.4 mm. When a = 1 and b = 0.2 mm, if H = 22 mm and W = 18 mm, substituting these values ​​into the above formula yields L ≈ 1.4 mm.

[0068] Those skilled in the art will understand that, through the above formula, they can determine the formula for the fin spacing L between two adjacent fins 200 based on the pipe spacing H between two adjacent pipe sections 110 and the width W of the fins 200, which greatly improves the design efficiency of the heat exchanger 001 and shortens the design time of the heat exchanger 001.

[0069] Compared to determining the values ​​of H, W, and L separately, the formula described above allows for the direct calculation of H after determining W and L. Furthermore, it ensures the coordination among H, W, and L, thereby balancing heat exchange in heat exchanger 001 while avoiding increased air resistance.

[0070] The above formula was obtained because those skilled in the art creatively determined the appropriate numerical ranges for the correction coefficient a and the correction variable b.

[0071] like Figure 3 and Figure 4 As shown, in some embodiments of this utility model, each fin 200 includes a fin body portion 210 and a plurality of clamp portions 220 disposed on the fin body portion 210. The clamp portion 220 is provided with a through hole 221 through which the pipe segment 110 passes, so that the pipe segment 110 of the refrigerant pipe 100 passes through the clamp portion 220.

[0072] Those skilled in the art will understand that the installation of the clamp portion 220 increases the contact area between the fins 200 and the refrigerant pipe 100, thereby improving the heat exchange efficiency between the fins 200 and the refrigerant pipe 100.

[0073] Furthermore, the height of the clamp portion 220 protruding from the plate portion 210 is less than or equal to the plate spacing L between two adjacent fins 200.

[0074] Continue reading Figure 3 and Figure 4 In some embodiments of this utility model, the clamp portion 220 abuts against the adjacent fin 200, thereby limiting the fin spacing L between two adjacent fins 200.

[0075] from Figure 3 and Figure 4 As can be seen, an annular step (not marked in the figure) is formed in the area of ​​the clamp portion 220 near the plate portion 210, and thus a groove is formed at the root of the clamp portion 220 to accommodate the top of another clamp portion 220 (e.g., Figure 3 As shown in the diagram, this design prevents misalignment between two adjacent fins 200 in the extension direction of the fins 200, allowing the refrigerant pipe 100 to pass through multiple fins 200 simultaneously. Furthermore, this fitting structure also ensures that the height of the clamp portion 220 protruding from the fin portion 210 is less than the fin spacing L between two adjacent fins 200.

[0076] In other embodiments of this utility model, those skilled in the art may omit the annular step at the root of the clamp portion 220 as needed, so that the height of the clamp portion 220 protruding from the plate portion 210 is equal to the plate distance L between two adjacent fins 200.

[0077] like Figure 3 and Figure 4 As shown, in some embodiments of this utility model, the windward side and / or the windward side of the sheet portion 210 is provided with a concave-convex structure 211 extending along the length direction of the sheet portion 210 to increase the structural strength of the sheet portion 210 and effectively prevent the sheet portion 210 from increasing wind resistance due to deformation. Furthermore, the ratio of the height P of the protrusion 2111 of the concave-convex structure 211 protruding from the sheet portion 210 to the thickness S of the sheet portion 210 is selected from any value from 1 to 3.5 to avoid excessive wind resistance from the protrusion 2111.

[0078] from Figure 3 and Figure 4As can be seen, the concave-convex structure 211 also includes a recessed portion 2112, which, along with the protrusion 2111, is located on both sides of the plate portion 210, so that the concave-convex structure 211 can be formed by a stamping process. This also increases the heat exchange area of ​​the plate portion 210.

[0079] The ratio of the height P of the protrusion 2111 of the concave-convex structure 211 protruding from the sheet portion 210 to the thickness S of the sheet portion 210 can be any feasible value such as 1, 1.2, 1.5, 1.8, 2, 2.5, 2.8, 3, 3.2, 3.5, etc.

[0080] Furthermore, the ratio of the height P of the protrusion 2111 of the concave-convex structure 211 protruding from the sheet portion 210 to the thickness S of the sheet portion 210 is selected from any value from 2 to 3, specifically any feasible value such as 2, 2.2, 2.3, 2.34, 2.35, 2.5, 2.7, 2.8, 3, etc.

[0081] like Figure 4 As shown, in some embodiments of this utility model, the thickness S of the sheet portion 210 is selected from any value from 0.085mm to 0.1mm. Specifically, the thickness S of the sheet portion 210 can be any feasible value such as 0.085mm, 0.091mm, 0.095mm, 0.097mm, or 0.1mm.

[0082] Those skilled in the art will understand that by providing a concave-convex structure 211 extending along the length of the plate portion 210 on the windward side of the plate portion 210, not only is the structural strength of the plate portion 210 increased, but the boundary layer adhering to the surface of the plate portion 210 is also broken, allowing more air to contact and exchange heat with the plate portion 210, further improving the heat exchange efficiency of the heat exchanger 001. By making the ratio of the height P of the protrusion 2111 of the concave-convex structure 211 protruding from the plate portion 210 to the thickness S of the plate portion 210 selected from any value from 1 to 3.5, particularly any value selected from 2 to 3, excessive wind resistance of the protrusion 2111 is avoided, and wind noise when air flows through the protrusion 2111 is reduced. At the same time, the concave-convex structure 211 can also guide and drain condensate formed on the plate portion 210.

[0083] like Figure 5 and Figure 6 As shown, the tangent line between the windward end of the sheet portion 210 and the protrusion 2111 closest to the windward end on the windward side is denoted as the windward tangent line T1, and the angle between the windward tangent line T1 and the sheet portion 210 is denoted as α; the tangent line between the windward end of the sheet portion 210 and the side of the clamp portion 220 away from the sheet portion 210 is denoted as the clamp tangent line T2, and the angle between the clamp tangent line T2 and the sheet portion 210 is denoted as β, then α > 0.7β.

[0084] Those skilled in the art will understand that by making α > 0.7β, the change in airflow direction when passing through the protrusion 2111 is sufficiently large, thereby disturbing the airflow. The disturbed airflow will produce certain fluctuations when passing between two adjacent fins 200, thus increasing the airflow path compared to unfluctuated laminar flow, thereby increasing the heat exchange time between the air and the fins 200, and thus improving the heat exchange performance of the heat exchanger 001.

[0085] The following reference Figures 7 to 9 To analyze the effect of the ratio of tube spacing H to fin width W on the heat exchange efficiency of fin 200.

[0086] Figure 7 This is a simulation diagram showing the effect of the ratio of pipe spacing H to fin width W on the heat exchange efficiency of fin 200 when the diameter of refrigerant pipe 100 is 6mm, the fin spacing is 1.3mm, and the wind speed is 2m / s.

[0087] from Figure 7 As can be seen, when 0.6 ≤ H / W ≤ 1.3, the heat transfer efficiency of fin 200 first increases and then decreases with the increase of H / W. The inflection point of the curve is near H / W = 1.

[0088] from Figure 7 It can also be seen that when 0.743≤H / W≤1.25, the heat exchange efficiency of fin 200 is relatively ideal, higher than 0.881. When 0.96≤H / W≤1.15, the heat exchange efficiency of fin 200 is even better.

[0089] Based on this, and the preceding formula, those skilled in the art will understand that once either H or W is determined, the value of the other H or W can be determined according to the aforementioned range of H / W values ​​(0.743 to 1.25 or 0.96 to 1.15). Then, by substituting the values ​​of H and W into the preceding formula, the value of the inter-sheet spacing L can be calculated.

[0090] Taking 0.96≤H / W≤1.15 as an example, when W=20mm, we determine 19.2mm≤H≤23mm. Considering the range of pipe spacing H (17.1mm to 22.5mm), the value of H should be selected from 19.2mm to 22.5mm. When H=21mm, and a=0.9, b=0.3mm, substituting these values ​​into the above formula yields L≈1.25mm.

[0091] Therefore, this invention enables those skilled in the art to quickly determine the values ​​of H, W, and L, greatly improving their work efficiency and achieving unexpected technical effects.

[0092] Figure 8 The wind speed field contour map is shown when H / W = 0.97. Figure 9 This is a wind speed field contour map when H / W = 0.7. Figure 8 and Figure 9 The stroke blows from left to right, and Figure 8 and Figure 9 The inlet velocity, pipe diameter d, and fin spacing L are all the same between adjacent fins 200.

[0093] The comparison shows that... Figure 8 The wind speed is higher than Figure 9 At a lower wind speed, the wind resistance is lower. That is, the wind resistance at H / W = 0.97 is less than the wind resistance at H / W = 0.7.

[0094] based on Figures 7 to 9 It is undeniable that this invention, by selecting the tube spacing H from any value between 17.1mm and 22.5mm, the fin width W from any value between 18mm and 23mm, and the fin spacing L from any value between 0.8mm and 1.5mm, and by ensuring that 0.743≤H / W≤1.25, and especially 0.96≤H / W≤1.15, and by ensuring that H, W, and L satisfy the functional relationship of the preceding formula, enables the fin 200 to have good heat exchange performance while effectively avoiding the increase of wind resistance, thus improving the overall performance of the fin 200.

[0095] Figure 10 This is a simulation diagram showing the effect of fin spacing L on the heat exchange efficiency of fin 200 when the diameter of refrigerant pipe 100 is d=6mm, the width of fin 200 is W=21.6mm, the pipe spacing is H=21mm, and the wind speed is 2m / s.

[0096] from Figure 10 As can be seen, within the range of 0.8mm≤L≤1.5mm, the heat exchange efficiency of fin 200 is higher than 0.88. As the fin spacing L increases, the efficiency coefficient tends to decrease, and the decrease is more obvious before L=1.1mm. The decreasing trend is gradual within the range of 1.1mm≤L≤1.5mm.

[0097] Figure 11 This is a simulation diagram showing the effect of fin spacing L on the inlet and outlet pressure drop efficiency between fins 200 when the diameter of refrigerant pipe 100 is d = 6 mm, the width of fin 200 is W = 21.6 mm, the pipe spacing H = 21 mm, and the air velocity is 2 m / s. Here, inlet and outlet refer to the air-facing and air-discharging ports of the gap formed between two adjacent fins 200 (i.e., the flow channel between adjacent fins 200).

[0098] from Figure 11As can be seen, the influence of fin spacing L on the pressure drop in the inlet and outlet directions of the flow channel between adjacent fins 200 tends to decrease with the increase of fin spacing L. In particular, the pressure drop is relatively small when the fin spacing L > 1.1 mm. This can be understood as the denser the fins 200, the greater the drag coefficient and the greater the pressure drop.

[0099] Considering that high-density fins 200 would lead to increased costs, 1.1mm≤L≤1.5mm can simultaneously balance cost and heat exchange efficiency of fins 200.

[0100] like Figure 12 As shown, the present invention also provides an air conditioner 002, which includes the heat exchanger 001 described in any of the preceding embodiments.

[0101] The air conditioner 002 of this utility model can be a split-type air conditioner or an integrated air conditioner.

[0102] Among them, split-type air conditioner 002, such as Figure 12 The illustrated unit includes an indoor air conditioning unit 300 and an outdoor air conditioning unit 400. The indoor air conditioning unit 300 can be a wall-mounted air conditioner, a floor-standing air conditioner, a ducted air conditioner, a ceiling-mounted air conditioner, etc. The heat exchanger 001 described in any of the preceding embodiments can be arranged in the indoor air conditioning unit 300 or in the outdoor air conditioning unit 400.

[0103] Among them, the integrated air conditioner 002 can be a window unit.

[0104] The technical solution of this utility model has been described in conjunction with several embodiments above. However, it will be readily understood by those skilled in the art that the protection scope of this utility model is not limited to these specific embodiments. Without departing from the technical principles of this utility model, those skilled in the art can disassemble and combine the technical solutions in the above embodiments, and can also make equivalent changes or substitutions to the relevant technical features. Any changes, equivalent substitutions, improvements, etc., made within the technical concept and / or technical principles of this utility model will fall within the protection scope of this utility model.

[0105] Finally, it should be noted that in this invention, the term "connection" refers to fluid communication, allowing fluid (e.g., air, liquid) to flow between two interconnected entities. Furthermore, this "connection" can be either a leak-free flow of fluid between two interconnected entities, or a flow with slight leakage between two interconnected entities.

Claims

1. A heat exchanger, characterized by, include: The refrigerant pipe has a diameter d selected from any value between 5.8 mm and 6.5 mm, and the refrigerant pipe includes multiple pipe segments, with the pipe spacing H between two adjacent pipe segments selected from any value between 17.1 mm and 22.5 mm. Multiple fins are penetrated by the multiple tube segments, the width W of the fins is selected from any value from 18mm to 23mm, and the fin spacing L between two adjacent fins is selected from any value from 0.8mm to 1.5mm.

2. The heat exchanger according to claim 1, characterized in that, The fin spacing L between two adjacent fins is determined based on the pipe spacing H between two adjacent pipe sections and the fin width W, in order to balance the heat exchange efficiency and air resistance of the heat exchanger. Where a is a correction coefficient, selected from any value between 0.5 and 1; b is a correction variable, selected from any value between 0.1 and 0.

6.

3. The heat exchanger according to claim 2, characterized in that, 0.743≤H / W≤1.

25.

4. The heat exchanger according to claim 1, characterized in that, The pipe diameter d of each of the aforementioned pipe sections is selected from any value between 5.9 mm and 6.2 mm; and / or, The fin spacing L between two adjacent fins is selected from any value between 1.1 mm and 1.5 mm.

5. The heat exchanger according to any one of claims 1 to 4, characterized in that, The length direction of the tube spacing H is perpendicular to the width direction of the fin.

6. The heat exchanger according to any one of claims 1 to 4, characterized in that, Each of the fins includes a fin body and a plurality of clamp portions disposed on the fin body, wherein the clamp portions are provided with through holes through which the pipe segment passes; The height of the tube clamp protruding from the fin body is less than or equal to the fin spacing L between two adjacent fins.

7. The heat exchanger according to claim 6, characterized in that, The clamp portion abuts against the adjacent fin; and / or, Multiple tubular clamps are respectively provided on the opposite sides of the sheet portion.

8. The heat exchanger according to claim 6, characterized in that, The windward side and / or the windward side of the sheet portion are provided with concave and convex structures extending along the length direction of the sheet portion to increase the structural strength of the sheet portion; The ratio of the height of the protrusion of the concave-convex structure protruding from the sheet portion to the thickness of the sheet portion is selected from any value from 1 to 3.5, so as to avoid excessive wind resistance of the protrusion.

9. The heat exchanger according to claim 8, characterized in that, The ratio of the height of the protrusion of the raised portion of the concave-convex structure to the thickness of the sheet portion is selected from any value between 2 and 3; and / or, The tangent between the windward end of the sheet portion and the protrusion closest to the windward end on the windward side is denoted as the windward tangent, and the angle between the windward tangent and the sheet portion is denoted as α; the tangent between the windward end of the sheet portion and the side of the clamp portion away from the sheet portion is denoted as the clamp tangent, and the angle between the clamp tangent and the sheet portion is denoted as β, where α > 0.7β.

10. An air conditioner, characterized in that, The heat exchanger includes any one of claims 1 to 9.

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