Smaller heat exchangers and air conditioners

Abstract

This utility model belongs to the field of air conditioning technology, specifically providing a smaller heat exchanger and air conditioner. This utility model aims to solve the problem that existing heat exchangers are too large, hindering the miniaturization of air conditioners. To this end, the heat exchanger of this utility model includes refrigerant pipes and multiple fins. The diameter d of the refrigerant pipes is selected from any value between 5.8mm and 6.5mm. The refrigerant pipes include multiple pipe segments, and the distance between two adjacent pipe segments is denoted as H. Multiple fins are penetrated by the multiple pipe segments, and the width of the fins is denoted as W, where 0.743 ≤ H / W < 1. This utility model can reduce the size of the heat exchanger while ensuring that the heat exchange performance remains unchanged, thereby facilitating the miniaturization of air conditioners.

Description

Technical Field

[0001] This utility model belongs to the field of air conditioning technology, specifically providing a heat exchanger and air conditioner with a smaller volume. 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 typically consist of fins and refrigerant pipes running through the fins. To reduce airflow resistance, those skilled in the art usually design heat exchangers with a pipe pitch to fin width ratio greater than 1 or larger, thereby reducing airflow resistance.

[0004] To ensure efficient heat exchange between the fins and the refrigerant pipes, the length of the refrigerant pipe penetrating the fins must be sufficient; otherwise, the heat exchanger's heating or cooling efficiency for the air flowing through it will be poor. However, this would result in a larger heat exchanger size, hindering the miniaturization of air conditioners. Utility Model Content

[0005] One objective of this invention is to solve the problem that the large size of existing heat exchangers is not conducive to the miniaturization of air conditioners.

[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. The refrigerant pipe includes multiple pipe segments, and the distance between two adjacent pipe segments is denoted as H.

[0008] Multiple fins are penetrated by the multiple tube segments, and the width of the fins is denoted as W, where 0.743 ≤ H / W < 1.

[0009] Optionally, 0.758 ≤ H / W < 1.

[0010] 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.

[0011] Optionally, the heat exchange enhancement structure is a bridge structure, a convex hull structure, and / or a louver structure.

[0012] Optionally, the heat exchange enhancement structure is a structure formed by a stamping process.

[0013] Optionally, the density of the heat exchange enhancement structure gradually increases towards the leeward direction of the fins.

[0014] Optionally, 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%.

[0015] Optionally, the surface of the fins is coated with a coating to improve heat exchange efficiency or reduce wind resistance.

[0016] Optionally, the coating may include metal particles to increase the roughness of the fin surface.

[0017] The present invention provides an air conditioner in a second aspect, comprising the heat exchanger described in any one of the first aspects.

[0018] 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 refrigerant pipe diameter d from any value between 5.8 mm and 6.5 mm, and by selecting the ratio between the pipe spacing and the fin width from any value between [0.743, 1), the density of the pipe section penetrating the fins is increased. Simultaneously, by using refrigerant pipes with a diameter of 5.8 mm to 6.5 mm, the heat exchange performance between the fins and the refrigerant pipe is improved, while minimizing the obstruction of the refrigerant pipe to airflow. Based on this, this utility model can reduce the size of the heat exchanger while ensuring that the heat exchange performance remains unchanged, thereby facilitating the miniaturization of air conditioners. Furthermore, this inventive technical improvement overcomes the technical bias mentioned in the background art—to reduce the airflow resistance of the heat exchanger, the conventional design by those skilled in the art is to make the ratio of the refrigerant pipe spacing to the fin width greater than 1 or larger, in order to reduce the airflow resistance of the refrigerant pipe.

[0019] 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.

[0020] 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.

[0021] 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.

[0022] 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

[0023] 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:

[0024] Figure 1 This is a schematic diagram of the structure of a heat exchanger provided by this utility model;

[0025] Figure 2 This is a partial top view of the fins in the first embodiment of this utility model;

[0026] Figure 3 yes Figure 2 A cross-sectional view of the middle fin along the AA direction (showing one fin);

[0027] Figure 4 yes Figure 2 A cross-sectional view of the middle fin along the AA direction (showing two fins);

[0028] Figure 5 This is a partial top view of the fins in the second embodiment of this utility model;

[0029] Figure 6 yes Figure 5 Cross-sectional view of the middle fin along the BB direction;

[0030] Figure 7 This is a partial top view of the fins in the third embodiment of this utility model;

[0031] Figure 8 This is a partial top view of the fins in the fourth embodiment of this utility model;

[0032] Figure 9 yes Figure 8 Cross-sectional view of the middle fin along the CC direction;

[0033] Figure 10This is a partial top view of the fins in the fifth embodiment of this utility model;

[0034] Figure 11 This is a partial top view of the fins in the sixth embodiment of this utility model;

[0035] Figure 12 yes Figure 10 Cross-sectional view of the middle fin along the DD direction;

[0036] Figure 13 yes Figure 11 Cross-sectional view of the middle fin along the EE direction;

[0037] Figure 14 This is a partial top view of the fins in the seventh embodiment of this utility model;

[0038] Figure 15 This is a wind speed field cloud map (side view) when the fins are flat.

[0039] Figure 16 This is a top view of the wind speed field when the fins are flat.

[0040] Figure 17 This is a wind speed field cloud map (side view) when the fins have a heat exchange enhancement structure;

[0041] Figure 18 This is a top view of the wind speed field when the fins have a heat exchange enhancement structure.

[0042] Figure 19 This is a schematic diagram of the fin structure in the eighth embodiment of this utility model;

[0043] Figure 20 This is a schematic diagram of an air conditioner provided by this utility model.

[0044] Explanation of reference numerals in the attached figures:

[0045] 001. Heat exchanger;

[0046] 100. Refrigerant pipe; 110. Pipe section;

[0047] 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;

[0048] 002, Air conditioner; 300, Indoor unit of air conditioner; 400, Outdoor unit of air conditioner. Detailed Implementation

[0049] 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.

[0050] 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.

[0051] 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.

[0052] Furthermore, it should be noted that in the description of this utility model, mm represents millimeter, cm represents centimeter, and m represents meter.

[0053] 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.

[0054] 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.

[0055] 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.

[0056] 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.

[0057] 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.

[0058] 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.

[0059] 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.

[0060] 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.

[0061] like Figures 1 to 4 As shown, in the first embodiment of this utility model, there are multiple fins 200, each of which is 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.

[0062] 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.

[0063] 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.

[0064] 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.

[0065] In the first embodiment of this utility model, 0.743 ≤ H / W < 1. The specific value of H / W can be any feasible value such as 0.743, 0.748, 0.75, 0.765, 0.81, 0.875, 0.921, 0.987, etc.

[0066] Furthermore, 0.758 ≤ H / W < 1.

[0067] Those skilled in the art will understand that by selecting the diameter d of the refrigerant pipe 100 from any value between 5.8 mm and 6.5 mm, and by selecting the ratio between the pipe spacing H and the width W of the fin 200 from any value between [0.743, 1), the density of the pipe segments 110 penetrating the fin 200 is increased. Simultaneously, by using refrigerant pipes 100 with diameters between 5.8 mm and 6.5 mm, the heat exchange performance between the fins 200 and the refrigerant pipe 100 is improved, while minimizing the obstruction of the refrigerant pipe 100 to the airflow. Based on this, the present invention can reduce the size of the heat exchanger 001 while ensuring that the heat exchange performance of the heat exchanger 001 remains unchanged, thereby facilitating the miniaturization of the air conditioner 002.

[0068] 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.

[0069] 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.

[0070] 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.

[0071] 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.

[0072] 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 4 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.

[0073] 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.

[0074] like Figures 5 to 14 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.

[0075] like Figures 5 to 6 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.

[0076] like Figure 7 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.

[0077] like Figures 8 to 9 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.

[0078] like Figure 10 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.

[0079] like Figures 11 to 13 As 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.

[0080] like Figure 14 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.

[0081] 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.

[0082] 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.

[0083] The ratio of G to L can be any feasible value such as 1%, 2%, 5%, 8%, 10%, 15%, 23%, 31%, 42%, 45, etc.

[0084] 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.

[0085] The following reference Figures 15 to 18 The beneficial effects of the heat exchange enhancement structure 230 will be further explained below. Among them, Figure 15 This is a wind speed field cloud map (side view) when the fin 200 has a flat structure. Figure 16 This is a top view of the wind speed field when the fin 200 has a flat structure. Figure 17 This is a wind speed field cloud map (side view) when fin 200 has heat exchange enhancement structure 230. Figure 18 This is a top view of the wind speed field when fin 200 has heat exchange enhancement structure 230. Furthermore, in Figures 15 to 18 In the middle, the airflow always flows from right to left.

[0086] from Figure 15 and Figure 16 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.

[0087] from Figure 17 and Figure 18 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.

[0088] like Figure 19 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.

[0089] 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.

[0090] The metal particles 241 can be any feasible particles such as iron particles, iron powder, copper particles, or alloy particles.

[0091] like Figure 20 As shown, the present invention also provides an air conditioner 002, which includes the heat exchanger 001 described in any of the preceding embodiments.

[0092] The air conditioner 002 of this utility model can be a split-type air conditioner or an integrated air conditioner.

[0093] Among them, split-type air conditioners, such as Figure 20 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.

[0094] Among them, the integrated air conditioner can be a window unit.

[0095] 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.

[0096] 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. The refrigerant pipe includes multiple pipe segments, and the distance between two adjacent pipe segments is denoted as H. Multiple fins are penetrated by the multiple tube segments, and the width of the fins is denoted as W, where 0.743 ≤ H / W < 1.

2. The heat exchanger according to claim 1, characterized in that, 0.758≤H / W<1.

3. The heat exchanger according to claim 1, 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.

4. The heat exchanger according to claim 3, characterized in that, The heat exchange enhancement structure is a bridge structure, a convex hull structure, and / or a louver structure.

5. The heat exchanger according to claim 4, characterized in that, The heat exchange enhancement structure is formed by a stamping process.

6. The heat exchanger according to any one of claims 3 to 5, characterized in that, The density of the heat exchange enhancement structure gradually increases towards the leeward side of the fins.

7. The heat exchanger according to any one of claims 3 to 5, characterized in that, 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%.

8. The heat exchanger according to any one of claims 1 to 5, characterized in that, The surface of the fins is coated with a coating to improve heat exchange efficiency or reduce wind resistance.

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

10. An air conditioner characterized by comprising: The heat exchanger includes any one of claims 1 to 9.

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