Compact heat exchanger and air conditioner

Abstract

This utility model belongs to the field of air conditioning technology, specifically providing a compact heat exchanger and air conditioner. This utility model aims to solve the problem of poor overall performance of 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. The width W of the fins is selected from any value between 18mm and 23mm, and the distance L between two adjacent fins is selected from any value between 0.8mm and 1.5mm. The thickness S of the fins is greater than or equal to 0.085mm and less than 0.1mm. This utility model, while ensuring heat exchange, effectively avoids increased wind resistance, improves the overall performance of the heat exchanger, and also makes the heat exchanger more compact and lower in cost.

Description

Technical Field

[0001] This utility model belongs to the field of air conditioning technology, specifically providing a compact heat exchanger and air conditioner. 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, characterized in that it comprises:

[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 between 18 mm and 23 mm. The fin spacing L between two adjacent fins is selected from any value between 0.8 mm and 1.5 mm. The thickness S of the fins is greater than or equal to 0.085 mm and less than 0.1 mm.

[0009] Optionally, the fin spacing L between two adjacent fins is determined based on the pipe spacing H between two adjacent pipe sections, the fin width W, and the fin thickness S, in order to balance the heat exchange efficiency and air resistance of the heat exchanger.

[0010]

[0011] Where a is selected from any value between 0.5 and 1; b is selected from any value between 1.2 and 5.

[0012] Optionally, 0.743 ≤ H / W ≤ 1.25.

[0013] Optionally, the fin includes a fin body and at least one heat exchange enhancement structure disposed on at least one side of the fin body in the thickness direction, so as to increase the surface area of ​​the fin through the heat exchange enhancement structure, thereby increasing the heat exchange efficiency between the fin and the air flowing through it.

[0014] Optionally, the heat exchange enhancement structure is a bridge structure, a convex hull structure, and / or a louver structure; and / or, the heat exchange enhancement structure is a structure formed by a stamping process.

[0015] Optionally, the density of the heat exchange enhancement structure gradually increases in the leeward direction of the fins; and / or, the ratio of the height G of the heat exchange enhancement structure protruding from the fin body to the fin spacing L between two adjacent fins is selected from any value from 1% to 45%.

[0016] Optionally, the surface of the fins is coated with a coating to improve heat exchange efficiency or reduce wind resistance.

[0017] Optionally, the coating may include metal particles to increase the roughness of the fin surface.

[0018] 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.

[0019] The present invention provides an air conditioner in a second aspect, comprising the heat exchanger described in any one of the first aspects.

[0020] 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.

[0021] Furthermore, by making the fin thickness S greater than or equal to 0.085 mm and less than 0.1 mm, the fins can be made as thin as possible, reducing the material used in the heat exchanger, lowering the production cost of the heat exchanger, and also making the heat exchanger more compact, which helps to achieve the miniaturization of the heat exchanger.

[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, the fin width W, and the fin thickness S. 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 at least one heat exchange enhancement structure on at least one side of the fin in the thickness direction, not only can the surface area of ​​the fin be increased, thereby increasing the heat exchange efficiency between the fin and the air flowing through it, but the heat exchange enhancement structure protruding from the fin can also disturb the airflow and break the boundary layer attached to the surface of the fin, allowing more air to contact and exchange heat with the fin, further improving the heat exchanger's heat exchange efficiency.

[0024] Furthermore, by gradually increasing the density of the heat exchange enhancement structure towards the leeward side of the fins, not only is the heat exchange performance on the leeward side of the fins improved, but the wind resistance of the heat exchange enhancement structure to the airflow is also effectively reduced. In addition, some airflow can be directed to the leeward side of the refrigerant pipe to eliminate the dead air zone on the leeward side of the refrigerant pipe as much as possible, thereby improving the heat exchange efficiency of the heat exchanger.

[0025] Furthermore, by coating the surface of the fins with a coating designed to improve heat exchange efficiency or reduce air resistance, the heat exchanger's heat exchange efficiency can be effectively improved or its air resistance reduced. In particular, when the coating includes metal particles, the roughness of the fin surface can be increased by the metal particles, thereby further increasing the surface area of ​​the fins in contact with the airflow and thus improving the heat exchanger's heat exchange performance.

[0026] 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

[0027] 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:

[0028] Figure 1 This is a schematic diagram of the structure of a heat exchanger provided by this utility model;

[0029] Figure 2 This is a partial top view of the fins in the first embodiment of this utility model;

[0030] Figure 3 yes Figure 2 A cross-sectional view of the middle fin along the AA direction (showing two fins);

[0031] Figure 4 yes Figure 2 A cross-sectional view of the middle fin along the AA direction (showing one fin);

[0032] Figure 5 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.

[0033] Figure 6 This is a wind speed field contour map when H / W = 0.97;

[0034] Figure 7 This is a wind speed field contour map when H / W = 0.7;

[0035] Figure 8 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.

[0036] Figure 9 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.

[0037] Figure 10 This is a partial top view of the fins in the second embodiment of this utility model;

[0038] Figure 11 yes Figure 10 Cross-sectional view of the middle fin along the BB direction;

[0039] Figure 12 This is a partial top view of the fins in the third embodiment of this utility model;

[0040] Figure 13 This is a partial top view of the fins in the fourth embodiment of this utility model;

[0041] Figure 14 yes Figure 13 Cross-sectional view of the middle fin along the CC direction;

[0042] Figure 15 This is a partial top view of the fins in the fifth embodiment of this utility model;

[0043] Figure 16 This is a partial top view of the fins in the sixth embodiment of this utility model;

[0044] Figure 17 yes Figure 15 Cross-sectional view of the middle fin along the DD direction;

[0045] Figure 18 yes Figure 16 Cross-sectional view of the middle fin along the EE direction;

[0046] Figure 19 This is a partial top view of the fins in the seventh embodiment of this utility model;

[0047] Figure 20 This is a wind speed field cloud map (side view) when the fins have a flat structure;

[0048] Figure 21 This is a top view of the wind speed field when the fins are flat.

[0049] Figure 22 This is a wind speed field cloud map (side view) when the fins have a heat exchange enhancement structure;

[0050] Figure 23 This is a top view of the wind speed field when the fins have a heat exchange enhancement structure.

[0051] Figure 24 This is a schematic diagram of the fin structure in the eighth embodiment of this utility model;

[0052] Figure 25 This is a schematic diagram of an air conditioner provided by this utility model.

[0053] Explanation of reference numerals in the attached figures:

[0054] 001. Heat exchanger;

[0055] 100. Refrigerant pipe; 110. Pipe section;

[0056] 200, fin; 210, fin body; 220, clamp; 221, through hole; 230, heat exchange enhancement structure; 231, bridge structure; 2311, through hole; 232, convex hull structure; 233, louver structure; 240, coating; 241, metal particles;

[0057] 002, Air conditioner; 300, Indoor air conditioner unit; 400, Outdoor air conditioner unit. Detailed Implementation

[0058] 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.

[0059] 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.

[0060] 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.

[0061] Furthermore, it should be noted that in the description of this utility model, mm represents millimeter, cm represents centimeter, and m represents meter.

[0062] 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.

[0063] 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.

[0064] It should be noted that this utility model Figure 1 The heat exchanger 001 shown is intended to illustrate the configuration 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, arrange the pipe segments 110 of the refrigerant pipe 100 penetrating the fins 200 into one, two, three, 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 certain pipe segment 110 in a certain column and the pipe segment 110 in the adjacent column that is closest to that pipe segment 110 can be aligned or misaligned with each other.

[0065] like Figure 1 and Figure 2 As shown, in the first embodiment 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.

[0066] 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.

[0067] 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.

[0068] 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.

[0069] In the first embodiment 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.

[0070] like Figures 1 to 3 As shown, in the first embodiment 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. The thickness S of the fin 200 is greater than or equal to 0.085 mm and less than 0.1 mm.

[0071] 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.

[0072] 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.

[0073] 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.

[0074] The thickness S of the fin 200 can be any feasible value such as 0.085mm, 0.089mm, 0.091mm, 0.095mm, or 0.097mm.

[0075] Those skilled in the art will understand that by selecting the tube spacing H between two adjacent tube sections 110 from any value between 17.1 mm and 22.5 mm, the width W of the fin 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 taken into account while the increase in wind resistance is effectively avoided, which can be described as killing two birds with one stone.

[0076] Furthermore, by making the thickness S of the fin 200 greater than or equal to 0.085 mm and less than 0.1 mm, the fin 200 can be made as thin as possible, reducing the material used in the heat exchanger 001, lowering the production cost of the heat exchanger 001, and also making the heat exchanger 001 more compact, which helps to achieve the miniaturization of the heat exchanger 001.

[0077] Furthermore, in the first embodiment 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, the width W of the fins 200, and the thickness S of the fins 200, in order to balance the heat exchange efficiency and air resistance of the heat exchanger 001.

[0078]

[0079] Where 'a' is selected from any value between 0.5 and 1, specifically it can be any feasible value such as 0.5, 0.7, 0.8, 0.9, 1, etc. 'b' is selected from any value between 1.2 and 5, specifically it can be any feasible value such as 1.2, 1.5, 2, 2.1, 3, 3.6, 4, 4.1, 4.5, 4.7, 5, etc.

[0080] For example, when a = 0.8 and b = 3, if H = 18 mm, W = 20 mm, and S = 0.09 mm, substituting these values ​​into the above formula yields L = 0.99 mm. When a = 0.9 and b = 4, if H = 21 mm, W = 21 mm, and S = 0.085 mm, substituting these values ​​into the above formula yields L = 1.24 mm. When a = 1 and b = 2, if H = 22 mm, W = 18 mm, and S = 0.092 mm, substituting these values ​​into the above formula yields L ≈ 1.4 mm.

[0081] 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, the width W of the fin 200, and the width S of the fin 200. This greatly improves the design efficiency of the heat exchanger 001 and shortens the design time of the heat exchanger 001.

[0082] Compared to determining the values ​​of H, W, L, and S separately, the formula described above allows for the direct calculation of the value of H after determining W, L, and S. Furthermore, it ensures the coordination among H, W, L, and S, thereby balancing heat exchange in heat exchanger 001 while avoiding increased air resistance and reducing the cost of heat exchanger 001.

[0083] like Figure 3 and Figure 4 As shown, in the first embodiment 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.

[0084] 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.

[0085] 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.

[0086] Continue reading Figure 3 and Figure 4 In the first embodiment 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.

[0087] 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.

[0088] 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.

[0089] The following reference Figures 5 to 7 To analyze the effect of the ratio of tube spacing H to fin width W on the heat exchange efficiency of fin 200.

[0090] Figure 5 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.

[0091] from Figure 5 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.

[0092] from Figure 5 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.

[0093] Based on this, and the preceding formula, those skilled in the art will understand that once either H or W is determined, the other value of 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). After determining the thickness S of the fin 200, the value of H and W can be calculated by substituting them into the preceding formula.

[0094] Taking 0.96≤H / W≤1.15 as an example, when W=20mm, we determine 19.2mm≤H≤23mm. Considering the range of tube spacing H (17.1mm to 22.5mm), the value of H should be selected from 19.2mm to 22.5mm. Considering the range of fin thickness S (0.085mm, 0.1mm), the value of S should be selected from [0.085mm, 0.1mm). When we choose H=21mm, S=0.09mm, and a=0.9, b=0.3, substituting these values ​​into the above formula yields L≈1.28mm.

[0095] Therefore, this invention enables those skilled in the art to quickly determine the values ​​of H, W, L, and S, greatly improving their work efficiency and achieving unexpected technical effects.

[0096] Figure 6 The wind speed field contour map is shown when H / W = 0.97. Figure 7 This is a wind speed field contour map when H / W = 0.7. Figure 6 and Figure 7 The stroke blows from left to right, and Figure 6 and Figure 7 The inlet velocity, pipe diameter d, and fin spacing L are all the same between adjacent fins 200.

[0097] The comparison shows that... Figure 6 The wind speed is higher than Figure 7 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.

[0098] based on Figures 5 to 7 It is undeniable that this utility model, 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, the fin spacing L from any value between 0.8mm and 1.5mm, ensuring 0.743≤H / W≤1.25, and especially ensuring 0.96≤H / W≤1.15, and the fin thickness S from any value between [0.085mm, 0.1mm), and ensuring that H, W, L, and S 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.

[0099] Figure 8 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.

[0100] from Figure 8 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.

[0101] Figure 9 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).

[0102] from Figure 9 As 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.

[0103] 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.

[0104] like Figures 10 to 19 As shown, the fin 200 of this utility model may further include at least one heat exchange enhancement structure 230 disposed on at least one side of the fin portion 210 in the thickness direction, so as to increase the surface area of ​​the fin 200 by means of the heat exchange enhancement structure 230, thereby increasing the heat exchange efficiency between the fin 200 and the air flowing through it. At the same time, the heat exchange enhancement structure 230 protruding from the fin portion 210 can also disturb the airflow and break the boundary layer attached to the surface of the fin portion 210, so that more air can come into contact with the fin portion 210 and exchange heat, further improving the heat exchange efficiency of the heat exchanger 001.

[0105] like Figures 10 to 11 As shown, in the second embodiment of this utility model, the heat exchange enhancement structure 230 is a bridge structure 231, and a through hole 2311 is formed between the bridge structure 231 and the plate body portion 210. Simply put, the bridge structure 231 can be a U-shaped, C-shaped, or V-shaped structure, and its two ends in the length direction are respectively connected to the plate body portion 210 to form a structure similar to a bridge.

[0106] like Figure 12 As shown, in the third embodiment of this utility model, compared with the second embodiment, the density of the bridge structure 231 gradually increases towards the leeward side of the fin 200 to improve the heat exchange performance of the leeward side of the fin 200; it can also effectively reduce the wind resistance of the heat exchange enhancement structure 230 to the airflow; and guide part of the airflow to the leeward side of the refrigerant pipe 100 to eliminate the dead air zone on the leeward side of the refrigerant pipe 100 as much as possible, thereby improving the heat exchange efficiency of the heat exchanger 001.

[0107] like Figures 13 to 14 As shown, in the fourth embodiment of this utility model, the heat exchange enhancement structure 230 is a convex hull structure 232. The convex hull structure 232 can be any feasible shape such as hemispherical or conical.

[0108] like Figure 15 As shown, in the fifth embodiment of this utility model, compared with the fourth embodiment, the density of the convex hull structure 232 gradually increases towards the leeward direction of the fin 200 to improve the heat exchange performance of the leeward side of the fin 200; it can also effectively reduce the wind resistance of the heat exchange enhancement structure 230 to the airflow; and guide part of the airflow to the leeward side of the refrigerant pipe 100 to eliminate the dead air zone on the leeward side of the refrigerant pipe 100 as much as possible, thereby improving the heat exchange efficiency of the heat exchanger 001.

[0109] like Figures 16 to 18As shown, in the sixth embodiment of this utility model, the heat exchange enhancement structure 230 is a louver structure 233. Simply put, the louver structure 233 is a structure where one end is connected to the sheet portion 210 and forms an acute angle with the sheet portion 210. Furthermore, an opening is provided in the area where the sheet portion 210 and the louver structure 233 are aligned.

[0110] like Figure 19 As shown, in the seventh embodiment of this utility model, compared with the sixth embodiment, the density of the louver structure 233 gradually increases towards the leeward side of the fin 200 to improve the heat exchange performance of the leeward side of the fin 200; it can also effectively reduce the wind resistance of the heat exchange enhancement structure 230 to the airflow; and guide part of the airflow to the leeward side of the refrigerant pipe 100 to eliminate the dead air zone on the leeward side of the refrigerant pipe 100 as much as possible, thereby improving the heat exchange efficiency of the heat exchanger 001.

[0111] In addition, in other embodiments of this utility model, those skilled in the art can also set the heat exchange enhancement structure 230 to other feasible structures as needed, such as a rod-shaped structure.

[0112] Furthermore, in any embodiment of the present invention, the ratio of the height G of the heat exchange enhancement structure 230 protruding from the fin portion 210 to the fin spacing L between two adjacent fins 200 is selected from any value from 1% to 45%, so as to enable the heat exchange enhancement structure 230 to improve the heat exchange performance of the fins 200 while avoiding the generation of large wind resistance.

[0113] The ratio of G to L can be any feasible value such as 1%, 2%, 5%, 8%, 10%, 15%, 23%, 31%, 42%, 45, etc.

[0114] Furthermore, in any embodiment of this utility model, the heat exchange enhancement structure 230 can be a structure formed by a stamping process to enable the fins 200 to be formed quickly.

[0115] The following reference Figures 20 to 23 The beneficial effects of the heat exchange enhancement structure 230 will be further explained below. Among them, Figure 20 This is a wind speed field cloud map (side view) when the fin 200 has a flat structure. Figure 21 This is a top view of the wind speed field when the fin 200 has a flat structure. Figure 22 This is a wind speed field cloud map (side view) when fin 200 has heat exchange enhancement structure 230. Figure 23 This is a top view of the wind speed field when fin 200 has heat exchange enhancement structure 230. Furthermore, in Figures 20 to 23 In the middle, the airflow always flows from right to left.

[0116] from Figure 20 and Figure 21 As can be seen, for fins 200 without the heat exchange enhancement structure 230, a significant boundary layer exists on the surface of fins 200. Furthermore, a large dead air zone (no airflow) is formed downstream of the clamp section 220. Therefore, the heat exchange performance of fins 200 is poor.

[0117] from Figure 22 and Figure 23 As can be seen, for the fin 200 with the heat exchange enhancement structure 230, the boundary layer on the surface of the fin 200 is disturbed and destroyed by the heat exchange enhancement structure 230. Furthermore, under the disturbance of the heat exchange enhancement structure 230, the dead air zone downstream of the pipe clamp 220 is significantly reduced. Therefore, the heat exchange efficiency of the fin 200 with the heat exchange enhancement structure 230 of this invention is significantly higher than that of the fin 200 without the heat exchange enhancement structure 230.

[0118] like Figure 24 As shown, in the eighth embodiment of this utility model, compared with any of the previous embodiments, the surface of the fin 200 is coated with a coating 240 for improving heat exchange efficiency or reducing wind resistance, so as to effectively improve the heat exchange efficiency of the heat exchanger 001 or reduce wind resistance.

[0119] Furthermore, the coating 240 includes metal particles 241 to increase the roughness of the surface of the fin 200, further increasing the surface of the fin 200 in contact with the airflow, and thus improving the heat exchange performance of the heat exchanger 001.

[0120] The metal particles 241 can be any feasible particles such as iron particles, iron powder, copper particles, or alloy particles.

[0121] like Figure 25 As shown, the present invention also provides an air conditioner 002, which includes the heat exchanger 001 described in any of the preceding embodiments.

[0122] The air conditioner 002 of this utility model can be a split-type air conditioner or an integrated air conditioner.

[0123] Among them, split-type air conditioners, such as Figure 25 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.

[0124] Among them, the integrated air conditioner can be a window unit.

[0125] 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.

Claims

1. A heat exchanger, characterized in that, 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 between 18 mm and 23 mm. The fin spacing L between two adjacent fins is selected from any value between 0.8 mm and 1.5 mm. The thickness S of the fins is greater than or equal to 0.085 mm and less than 0.1 mm.

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, the fin width W, and the fin thickness S, in order to balance the heat exchange efficiency and air resistance of the heat exchanger. Where a is selected from any value between 0.5 and 1; b is selected from any value between 1.2 and 5.

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

25.

4. The heat exchanger according to any one of claims 1 to 3, characterized in that, The fin includes a fin body and at least one heat exchange enhancement structure disposed on at least one side of the fin body in the thickness direction, so as to increase the surface area of ​​the fin through the heat exchange enhancement structure, thereby increasing the heat exchange efficiency between the fin and the air flowing through it.

5. The heat exchanger according to claim 4, characterized in that, The heat exchange enhancement structure is a bridge structure, a convex hull structure, and / or a louver structure; and / or... The heat exchange enhancement structure is formed by a stamping process.

6. The heat exchanger according to claim 4, characterized in that, The density of the heat exchange enhancement structure gradually increases towards the leeward side of the fins; and / or, The ratio of the height G of the heat exchange enhancement structure protruding from the fin portion to the fin spacing L between two adjacent fins is selected from any value between 1% and 45%.

7. The heat exchanger according to any one of claims 1 to 3, characterized in that, The surface of the fins is coated with a coating to improve heat exchange efficiency or reduce wind resistance.

8. The heat exchanger according to claim 7, characterized in that, The coating includes metal particles to increase the roughness of the fin surface.

9. The heat exchanger according to any one of claims 1 to 3, 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.

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

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