Heat exchanger and air conditioner

Abstract

The invention relates to the technical field of air conditioners, and discloses a heat exchanger which comprises a middle fin section, a first heat transfer unit and a second fin section. Wherein the first heat transfer unit comprises P1 first heat transfer structures; the upper fin section is bent and connected to the upper end of the middle fin section, and a second heat transfer unit is arranged on the surface; the second heat transfer unit comprises P2 second heat transfer structures; the lower fin section is connected to the lower end of the middle fin section in a bent mode, and the lower fin section and the upper fin section are located on the same side of the middle fin section; a third heat transfer unit is arranged on the surface of the lower fin section and comprises P3 third heat transfer structures; wherein P1 is smaller than P2, and / or P1 < lt >; p3, and / or P3lt; p2. The invention further discloses the air conditioner.

Description

Technical Field

[0001] This application relates to the technical field of air conditioners, for example, to a heat exchanger and an air conditioner. Background Art

[0002] In an air conditioner, the heat exchanger includes an evaporator and a condenser, which are the main structural components consuming energy in the air conditioner. The performance of the heat exchanger directly affects the energy consumption level of the air conditioner. Finned tube heat exchangers are widely used in wall-mounted, floor-standing, and ducted household air conditioners. The air-side thermal resistance outside the tube usually accounts for 70%-90% of the total thermal resistance, determining the pros and cons of the performance of the entire heat exchanger.

[0003] In the process of implementing the embodiments of the present disclosure, it is found that at least the following problems exist in the related art:

[0004] Taking the indoor unit of a ducted air conditioner as an example, an I-shaped fin heat exchanger is mostly used. However, in the case of non-uniform wind field distribution, the performance of this heat exchanger cannot be fully exerted, reducing the heat transfer efficiency of the heat exchanger.

[0005] It should be noted that the information disclosed in the above background art section is only used to strengthen the understanding of the background of this application. Therefore, it may include information that does not constitute the prior art known to those of ordinary skill in the art. Summary of the Invention

[0006] To have a basic understanding of some aspects of the disclosed embodiments, a simple summary is given below. This summary is not a general review, nor is it intended to identify key / important constituent elements or delineate the protection scope of these embodiments. Instead, it serves as a preface to the subsequent detailed description.

[0007] Embodiments of the present disclosure provide a heat exchanger and an air conditioner, which improve the overall heat transfer efficiency of the heat exchanger.

[0008] In some embodiments, the heat exchanger includes:

[0009] A middle fin segment, with a first heat transfer unit provided on its surface; wherein, the first heat transfer unit includes P1 first heat transfer structures;

[0010] An upper fin segment, bent and connected to the upper end of the middle fin segment, with a second heat transfer unit provided on its surface; wherein, the second heat transfer unit includes P2 second heat transfer structures;

[0011] A lower fin segment, bent and connected to the lower end of the middle fin segment, and located on the same side of the middle fin segment as the upper fin segment; a third heat transfer unit is provided on the surface of the lower fin segment, and the third heat transfer unit includes P3 third heat transfer structures;

[0012] Wherein, P1 < P2, and / or, P1 < P3, and / or, P3 < P2.

[0013] In some embodiments, the air conditioner includes the heat exchanger.

[0014] The heat exchanger and air conditioner provided by the embodiments of the present disclosure can achieve the following technical effects:

[0015] The first, second, and third heat transfer structures all enhance the heat transfer capacity of their corresponding fin segments. The bending of the upper and lower fin segments affects the direction and velocity of air flowing through them. By optimizing the numerical relationship between P1, P2, and P3, we can adapt to the air flow characteristics of different fin segments, helping to guide air from the middle fin segment to the upper and lower fin segments, thereby improving the overall heat exchange efficiency of the fins.

[0016] The above general description and the following description are exemplary and explanatory only and are not intended to limit the present application. BRIEF DESCRIPTION OF THE DRAWINGS

[0017] One or more embodiments are exemplarily described by corresponding drawings. These exemplary descriptions and drawings do not limit the embodiments. Elements with the same reference numerals in the drawings are shown as similar elements. The drawings do not constitute a scale limitation. In addition,

[0018] Figure 1 is a structural diagram of an air conditioner provided by an embodiment of the present disclosure;

[0019] Figure 2 is a schematic diagram of the opening angles corresponding to each windward side contour line provided by an embodiment of the present disclosure;

[0020] Figure 3 Schematic diagram of the structure of the volute provided in an embodiment of the present disclosure;

[0021] Figure 4 Schematic diagrams of the structure of the fins provided in the embodiments of the present disclosure, wherein (a) is a schematic diagram of the windward side contour line, and (b) is a schematic diagram of the heat transfer unit on each fin segment;

[0022] Figure 5 is a schematic diagram of characteristic parameters of the bridge plate structure provided by an embodiment of the present disclosure;

[0023] Figure 6 is a schematic diagram of characteristic parameters of the shutter structure provided by an embodiment of the present disclosure;

[0024] Figure 7 is a schematic diagram of characteristic parameters of the shutter structure provided by an embodiment of the present disclosure;

[0025] Figure 8 is a schematic diagram of a drag coefficient of each wing segment provided by an embodiment of the present disclosure;

[0026] Figure 9 Schematic diagrams of another type of drag coefficient for each wing segment provided by an embodiment of the present disclosure, wherein (a) is a schematic diagram of the drag coefficient corresponding to two types of drag regions on the upper wing segment, and (b) is a schematic diagram of the drag coefficient corresponding to two types of drag regions on the lower wing segment;

[0027] Figure 10 is a structural schematic diagram of a fin provided by an embodiment of the present disclosure;

[0028] Figure 11 is a structural schematic diagram of another fin provided by an embodiment of the present disclosure;

[0029] Figure 12 is a structural schematic diagram of another fin provided by an embodiment of the present disclosure;

[0030] Figure 13 is a structural schematic diagram of another fin provided by an embodiment of the present disclosure;

[0031] Figure 14 is a structural schematic diagram of another fin provided by an embodiment of the present disclosure;

[0032] Figure 15 is a structural schematic diagram of another fin provided by an embodiment of the present disclosure;

[0033] Figure 16 It is the velocity distribution cloud diagram of the heat exchanger;

[0034] Figure 17 It is the velocity distribution cloud diagram of C-type fin heat exchanger;

[0035] Figure 18 is a velocity distribution cloud diagram of a heat exchanger provided by an embodiment of the present disclosure;

[0036] Figure 19 This is the pressure distribution cloud diagram of the C-type fin heat exchanger;

[0037] Figure 20 It is a pressure distribution cloud diagram of the heat exchanger provided in the embodiment of the present disclosure.

[0038] Reference numerals:

[0039] 1. Upper wing segment; 11. First side contour line; 111. First leeward side contour line; 112. First windward side contour line; 12. First heat transfer unit; 121. First heat transfer structure; 13. Second heat transfer unit; 131. Second heat transfer structure; 14. Third heat transfer unit; 141. Third heat transfer structure;

[0040] 2. Middle wing segment; 21. Second side contour line; 211. Second leeward side contour line; 212. Second windward side contour line;

[0041] 3. Lower wing segment; 31. Third side contour line; 311. Third leeward side contour line; 312. Third windward side contour line;

[0042] 4. Indoor unit casing; 41. Volute; 411. First diffuser; 412. Second diffuser; 413. Third diffuser; 414. Fourth diffuser; 415. Fifth diffuser; 416. Sixth diffuser; 417. Accommodation chamber; 4171. Exit of the accommodating chamber; 418. Axis of volute; 42. Air inlet; 43. Air outlet; 44. First air outlet; 441. Exit of the first air outlet; 45. Second air outlet; 451. Exit of the second air outlet; 46. Air outlet;

[0043] 5. Indoor fan;

[0044] 6. Heat exchanger; 61. First heat exchange tube hole group; 611. First heat exchange tube hole; 62. Second heat exchange tube hole group; 621. Second heat exchange tube hole; 63. Third heat exchange tube hole group; 631. Third heat exchange tube hole; 64. Fin; 641. Windward side contour line; 642. Leeward side contour line; 65. Bridge structure; 651. Bridge top wall; 652. Bridge side wall; 66. Louver structure; 661. Window top wall; 662. Window side wall. DETAILED DESCRIPTION

[0045] In order to be able to understand the features and technical content of the embodiments of the present disclosure in more detail, the implementation of the embodiments of the present disclosure is described in detail below in conjunction with the accompanying drawings. The accompanying drawings are for reference only and are not used to limit the embodiments of the present disclosure. In the following technical description, for the sake of convenience of explanation, a full understanding of the disclosed embodiments is provided through multiple details. However, one or more embodiments can still be implemented without these details. In other cases, to simplify the drawings, well-known structures and devices can be simplified for display.

[0046] In the description and claims of the embodiments of the present disclosure, as well as in the accompanying drawings, the terms "first," "second," and the like are used to distinguish similar items and are not necessarily used to describe a particular order or precedence. It should be understood that such terms are interchangeable where appropriate to describe the embodiments of the present disclosure. Furthermore, the terms "including," "having," and any variations thereof are intended to cover non-exclusive inclusions.

[0047] In the embodiments of the present disclosure, the terms "upper", "lower", "inside", "middle", "outside", "front", "back" and the like indicate directions or positional relationships based on the directions or positional relationships shown in the accompanying drawings. These terms are mainly intended to better describe the embodiments of the present disclosure and their embodiments, and are not intended to limit the indicated devices, elements or components to having a specific direction, or to be constructed and operated in a specific direction. Moreover, in addition to being used to indicate directions or positional relationships, some of the above terms may also be used to indicate other meanings. For example, the term "upper" may also be used to indicate a certain dependency or connection relationship in certain circumstances. For those of ordinary skill in the art, the specific meanings of these terms in the embodiments of the present disclosure can be understood according to specific circumstances.

[0048] Furthermore, the terms "disposed," "connected," and "fixed" should be interpreted broadly. For example, "connected" can mean a fixed connection, a removable connection, or an integral structure; it can be a mechanical connection or an electrical connection; it can be a direct connection, an indirect connection through an intermediary, or an internal connection between two devices, elements, or components. Those skilled in the art will understand the specific meanings of these terms in the embodiments of this disclosure based on the specific circumstances.

[0049] Unless otherwise stated, the term "plurality" means two or more.

[0050] In the embodiment of the present disclosure, the character " / " indicates that the preceding and following objects are in an "or" relationship. For example, A / B means: A or B.

[0051] The term "and / or" describes an association between objects, indicating that three relationships can exist. For example, A and / or B means: A or B, or A and B.

[0052] It should be noted that, in the absence of conflict, the embodiments and features in the embodiments of the present disclosure can be combined with each other.

[0053] The embodiment of the present disclosure provides an air conditioner, which includes an indoor unit housing 4, a volute 41, an indoor fan 5 and a heat exchanger 6. Figure 1 and Figure 3 As shown, the volute 41 includes a housing chamber 417 and an air outlet 46. The indoor fan 5 is disposed in the housing chamber 417, the heat exchanger 6 is disposed in the air outlet 46, and the volute 41 is disposed in the indoor unit housing 4. The indoor unit housing 4 includes an air inlet 42 and an air outlet 43. Outside air flows into the volute 41 through the air inlet 42, flows through the heat exchanger 6, and then flows into the room through the air outlet 43.

[0054] In some embodiments, the air conditioner includes a volute 41 and a heat exchanger 6. The volute 41 includes a receiving chamber 417 and an air outlet 46. The receiving chamber 417 is used to install the indoor fan 5. The air outlet 46 is connected to the outlet 4171 of the receiving chamber 417. The heat exchanger 6 is arranged in the air outlet 46. The heat exchanger 6 includes a plurality of fins 64 arranged in parallel along the axis 418 of the volute 41. The fins 64 include an upper fin segment 1, a middle fin segment 2 and a lower fin segment 3 connected to each other. The upper fin segment 1 and the lower fin segment 3 are both inclined toward the receiving chamber 417, and the middle fin segment 2 includes a second windward side contour line 212. As shown in FIG. Figure 2 and Figure 3 As shown, the midpoint of the longitudinal section of the outlet 4171 of the accommodating cavity 417 is a reference point H. The opening angle of the second windward side contour line 212 corresponding to the reference point H is c1, and 6°≤c1≤50°. For example, c1 can be 6°, 10°, 15°, 20°, 25°, 30°, 35°, 40°, 45°, or 50°.

[0055] In this embodiment, the orientation of the air conditioner is as follows: Figure 2 As shown, the accommodating chamber 417 is located at the rear of the air conditioner, and the air outlet 46 is located at the front of the air conditioner. After the heat exchanger 6 is installed on the air outlet 46, the three sections of the fin 64 are called the upper fin section 1, the middle fin section 2 and the lower fin section 3 from top to bottom. Since the accommodating chamber 417 of the volute 41 is used to install the indoor fan 5, the axis 418 of the volute 41 is also the axis of the indoor fan 5, as shown in FIG. Figure 3 As shown. A cross section taken along the front-to-back direction of the air conditioner is called a longitudinal section, and a cross section taken perpendicular to the longitudinal section is called a transverse section. The three-segment fins 64 are arcuate or bow-shaped, hence also called arcuate fins 64 or bow-shaped fins 64. This design guides the air flowing through them. The opening angle c1 of the middle fin segment 2 is designed to be between 6° and 50°, which helps optimize the contact angle between the airflow and the middle fin segment 2, ensuring more complete heat exchange and improving heat exchange efficiency.

[0056] Optionally, 6°≤c1≤30°. For example, c1 can be selected from 6°, 8°, 12°, 16°, 22°, 26°, 28°, or 30°.

[0057] Optionally, the upper fin segment 1, the middle fin segment 2 and the lower fin segment 3 of the fin 64 are integrally formed. Figure 4As shown in (a), to avoid confusion, the upper wing section 1 includes a first side contour line 11, which includes a first windward side contour line 112 and a first leeward side contour line 111. The middle wing section 2 includes a second side contour line 21, which includes a second windward side contour line 212 and a second leeward side contour line 211. The lower wing section 3 includes a third side contour line 31, which includes a third windward side contour line 312 and a third leeward side contour line 311. Moreover, the first windward side contour line 112, the second windward side contour line 212, and the third windward side contour line 312 constitute a windward side contour line 641, and the first leeward side contour line 111, the second leeward side contour line 211, and the third leeward side contour line 311 constitute a leeward side contour line 642. In this embodiment, the first side contour line 11 , the second side contour line 21 , and the third side contour line 31 are all straight lines, and the connection between adjacent contour lines may be rounded or not.

[0058] Alternatively, as Figure 2 As shown, the upper wing section 1 includes a first windward side contour line 112, and the opening angle of the first windward side contour line 112 corresponding to the reference point H is c2. The lower wing section 3 includes a third windward side contour line 312, and the opening angle of the third windward side contour line 312 corresponding to the reference point H is c3.

[0059] In this embodiment, the relationship between c1, c2, and c3 is limited. Among them, 0.3≤c2 / c1≤0.7, for example, c2 / c1 can be selected from 0.3, 0.4, 0.5, 0.6, or 0.7. Among them, 0.5≤c3 / c1≤0.9, for example, c3 / c1 can be selected from 0.5, 0.6, 0.7, 0.8, or 0.9. Among them, 0.6≤c1 / (c2+c3)≤1, for example, c1 / (c2+c3) can be selected from 0.6, 0.7, 0.8, 0.9, or 1. In this way, by designing the proportional relationship between the three opening angles, the contact angles of the airflow with the three wing segments can be optimized, thereby making the airflow distribution more uniform.

[0060] Alternatively, as Figure 2 As shown, the height of the upper wing segment 1 is h1, the height of the middle wing segment 2 is h2, and the height of the lower wing segment 3 is h3. Moreover, 0.2≤h2 / (h1+h2+h3)≤0.5. For example, h2 / (h1+h2+h3) can be selected as 0.2, 0.3, 0.4 or 0.5. In this way, the distribution of the circulating air can be matched by designing the height relationship of the three wing segments. When the upper wing segment 1 and the lower wing segment 3 are arranged at an angle, the length of the slope section of the fin 64 is shorter, reducing the risk of poor drainage on the surface of the fin 64.

[0061] Optionally, the height of the longitudinal section of the outlet 4171 of the accommodating cavity 417 is T, the height of the middle wing segment 2 is h2, and 1≤T / h2≤2.5. For example, T / h2 can be selected as 1, 1.2, 1.5, 1.8, 2, 2.2 or 2.5. Among them, h2 affects the heat exchange area of ​​the middle wing segment 2, and T affects the air outlet area. Through a reasonable proportional relationship design, the air outlet area is adapted to the heat exchange area of ​​the middle wing segment 2. In addition, combined with the design of the above-mentioned three opening angles and the height relationship design of the three wing segments, when the wind speed corresponding to the middle wing segment 2 is relatively large, it is beneficial for the air flowing through the middle wing segment 2 to diffuse to the upper wing segment 1 and the lower wing segment 3, and the air volume is adapted to the heat exchange area, thereby improving the heat exchange efficiency.

[0062] Optionally, the middle wing section 2 further includes a second leeward side contour line 211, and the second leeward side contour line 211 and the second windward side contour line 212 are both straight and parallel to each other. In this way, the middle wing section 2 is straight.

[0063] In some embodiments, the air conditioner includes a volute 41 and a heat exchanger 6. The volute 41 includes an air outlet 46, and the air outlet 46 includes a first diffuser plate 411. The heat exchanger 6 is disposed at the air outlet 46, and the heat exchanger 6 includes a plurality of fins 64 arranged in parallel along the axis 418 of the volute 41. The fins 64 include a windward side contour line 641, and the first diffuser plate 411 extends toward the windward side contour line 641. Figure 3 As shown, the intersection of the extension direction of the first diffuser plate 411 and the windward contour line 641 is T1, the length between T1 and the nearest endpoint of the windward contour line 641 is t1, the total length of the windward contour line 641 is t, and t1 / t ≤ 30%. In this way, the intersection of the first diffuser plate 411 and the windward contour line 641 facilitates air flow guidance. Furthermore, the t1 / t ratio helps ensure that the air volume guided by the first diffuser plate 411 matches the length of the windward contour line 641, thereby improving heat exchange efficiency.

[0064] In this embodiment, the total length t of the windward side contour line 641 is equal to the sum of the lengths of the first windward side contour line 112, the second windward side contour line 212, and the third windward side contour line 312. If the intersection point T1 is closest to the upper end of the windward side contour line 641, then t1 is equal to the length between the intersection point T1 and the upper end of the windward side contour line 641; if the intersection point T1 is closest to the lower end of the windward side contour line 641, then t1 is equal to the length between the intersection point T1 and the lower end of the windward side contour line 641.

[0065] Optionally, 5%≤t1 / t≤30%. For example, t1 / t can be selected as 5%, 10%, 15%, 20%, 25% or 30%.

[0066] Alternatively, as Figure 3 As shown, the angle between the first diffuser plate 411 and the horizontal direction is For example, You can choose 5°, 10°, 20°, 30°, 40°, 50° or 60°. The value of can adjust the position of the intersection point T1, and The smaller the intersection point T1 is, the closer it is to the upper end of the first windward side contour line 112 .

[0067] Optionally, fin 64 includes an upper fin segment 1, a middle fin segment 2, and a lower fin segment 3, which are sequentially connected. Both upper fin segment 1 and lower fin segment 3 are inclined toward axis 418 of volute 41. The windward contour line 641 corresponding to upper fin segment 1 is referred to as first windward contour line 112, and the extension direction of first diffuser 411 intersects first windward contour line 112 at T1. Here, first diffuser 411 is located at the upper portion of volute 41.

[0068] Alternatively, as Figure 3 As shown, the air outlet 46 also includes a second diffuser plate 412, which is spaced apart and disposed below the first diffuser plate 411. The second diffuser plate 412 extends toward the third windward side contour line 312. The intersection of the extension direction of the second diffuser plate 412 and the third windward side contour line 312 is T2. The length between T2 and the lower end of the third windward side contour line 312 is t2, and t2 / t ≤ 30%. Furthermore, 5% ≤ t2 / t ≤ 30%. For example, t2 / t can be selected from 5%, 10%, 15%, 20%, 25%, or 30%. In this way, the second diffuser plate 412 intersects with the third windward side contour line 312, which helps guide the air flow. Furthermore, the t2 / t ratio design helps ensure that the air volume guided by the second diffuser plate 412 matches the length of the windward side contour line 641.

[0069] Alternatively, as Figure 3 As shown, the angle between the second diffuser plate 412 and the horizontal direction is For example, You can choose 5°, 10°, 20°, 30°, 40°, 50° or 60°. The value of can adjust the position of the intersection point T2, and The larger the intersection point T2 is, the closer it is to the lower end of the third windward side contour line 312. In this way, the first diffuser plate 411 and the second diffuser plate 412 form a diffuser guide. and The value design combined with the ratio design of t1 / t and t2 / t can make the air diffuse evenly toward the heat exchanger 6.

[0070] Alternatively, as Figure 3 As shown, the air outlet 46 also includes a third diffuser plate 413, which is connected to the first diffuser plate 411 and extends upward. The fin 64 also includes a leeward side contour line 642. The leeward side contour line 642 corresponding to the upper fin segment 1 is called the first leeward side contour line 111. In addition, the first leeward side contour line 111 intersects with the third diffuser plate 413 and forms an angle γ1, and 20°≤γ1≤90°. For example, γ1 can be selected from 20°, 30°, 40°, 50°, 60°, 70°, 80°, or 90°.

[0071] Alternatively, as Figure 3 As shown, the air outlet 46 also includes a fourth diffuser plate 414 and a sixth diffuser plate 416. The fourth diffuser plate 414 is connected to the second diffuser plate 412 and extends downward, and the sixth diffuser plate 416 is connected to the fourth diffuser plate 414 and extends upward. The fin 64 also includes a leeward side contour line 642. The leeward side contour line 642 corresponding to the lower wing segment 3 is called the third leeward side contour line 311. In addition, the angle formed by the intersection of the third leeward side contour line 311 and the sixth diffuser plate 416 is γ2, and 20°≤γ2≤90°. For example, γ2 can be selected from 20°, 30°, 40°, 50°, 60°, 70°, 80° or 90°.

[0072] In some embodiments, the volute 41 includes a receiving cavity 417 and an air outlet 46, and the air outlet 46 includes a first air outlet 44 and a second air outlet 45. Figure 3 As shown, the interior of the accommodating chamber 417 is used to mount the indoor fan 5. A first air outlet 44 is connected to the outlet 4171 of the accommodating chamber 417, and the cross-sectional area of ​​the air flow of the first air outlet 44 gradually increases along the outlet direction. A second air outlet 45 is connected to the outlet 441 of the first air outlet 44 and is used to mount the heat exchanger 6. The cross-sectional area of ​​at least part of the second air outlet 45 is larger than the maximum cross-sectional area of ​​the air flow of the first air outlet 44.

[0073] In this embodiment, the orientation of the air conditioner is as follows: Figure 2As shown, a cross section taken along the front-to-back direction of the air conditioner is called a longitudinal cross section, and a cross section taken perpendicular to the longitudinal cross section is called a transverse cross section. The cross-sectional area of ​​the air flow through the first air outlet 44 refers to the cross-sectional area of ​​the first air outlet 44, while the cross-sectional area of ​​the air flow through the second air outlet 45 refers to the cross-sectional area of ​​the second air outlet 45. The heat exchanger 6 is entirely disposed within the second air outlet 45, ensuring that all air flowing out of the volute 41 exchanges heat with the heat exchanger 6. Furthermore, because the cross-sectional area of ​​the air flow through the first air outlet 44 gradually increases along the outlet direction, a diffuse flow is formed. The reduced flow velocity after diffusion facilitates sufficient contact between the air and the heat exchanger 6. Because the cross-sectional area of ​​the air flow through at least part of the second air outlet 45 is larger than the maximum cross-sectional area of ​​the air flow through the first air outlet 44, the second air outlet 45 acts as a buffer against the sudden increase in cross-sectional area, facilitating uniform air contact with the heat exchanger 6. Thus, the structural design of the volute 41 effectively improves the heat exchange efficiency between the air and the heat exchanger 6.

[0074] Alternatively, as Figure 3 As shown, the first air outlet 44 includes a first diffuser plate 411 and a second diffuser plate 412. The first diffuser plate 411 is parallel to the axis 418 of the volute 41 and extends downward. The angle between the first diffuser plate 411 and the horizontal direction is The second diffuser plate 412 is spaced apart from the first diffuser plate 411 and is arranged non-parallel to the first diffuser plate 411. The second diffuser plate 412 is parallel to the axis 418 of the volute 41 and extends downward. In addition, the angle between the second diffuser plate 412 and the horizontal direction is In this embodiment, the first diffuser plate 411 is located at the upper part of the volute 41, and the second diffuser plate 412 is located at the lower part of the volute 41. The first diffuser plate 411 and the second diffuser plate 412 form a diffuser guide, and through and The value design optimizes the diffusion direction, which is conducive to the uniform diffusion of air towards the heat exchanger 6.

[0075] Alternatively, as Figure 3 As shown, the second air outlet 45 includes a third diffuser plate 413, a fourth diffuser plate 414, a fifth diffuser plate 415 and a sixth diffuser plate 416. The third diffuser plate 413 is connected to the first diffuser plate 411 and extends upward. The angle between the third diffuser plate 413 and the first diffuser plate 411 is and The fourth diffuser plate 414 is connected to the second diffuser plate 412 and extends downward. The angle between the fourth diffuser plate 414 and the second diffuser plate 412 is and The fifth diffuser plate 415 is connected to the third diffuser plate 413 and extends downward. The angle between the fifth diffuser plate 415 and the third diffuser plate 413 is and The sixth diffuser plate 416 is connected to the fourth diffuser plate 414 and extends upward. The angle between the sixth diffuser plate 416 and the fourth diffuser plate 414 is and For example, You can choose 10°, 15°, 20°, 25° or 30°. For example, You can choose 40°, 45°, 50°, 55° or 60°. For example, You can choose 15°, 20°, 25°, 30° or 35°. For example, You can choose 40°, 45°, 50°, 55° or 60°.

[0076] In this embodiment, the volute 41 is installed after the air conditioner, and the orientation of the air conditioner is as follows: Figure 2 As shown. The upward extension of the pressure diffuser refers to the extension toward the top of the air conditioner, and the downward extension refers to the extension toward the bottom of the air conditioner. In this way, through the design of multiple pressure diffusers of the second air outlet 45, and and The value design makes the cross-sectional area of ​​the second air outlet portion 45 located upstream of the heat exchanger 6 suddenly increase, thereby having a buffering effect, and the cross-sectional area of ​​the second air outlet portion 45 close to the air outlet 43 is reduced again, thereby having the effect of gathering air.

[0077] In some embodiments, the air conditioner includes a heat exchanger 6 and the volute 41. Figure 2 As shown, the heat exchanger 6 is arranged in the second air outlet 45, and the distance between the outlet 4171 of the accommodating chamber 417 and the heat exchanger 6 is U1, and the distance between the outlet 451 of the second air outlet 45 and the heat exchanger 6 is U2. In addition, 0.1≤U2 / U1≤2. For example, U2 / U1 can be selected as 0.1, 0.3, 0.5, 0.7, 1, 1.2, 1.4, 1.6, 1.8 or 2. By optimizing the value of U2 / U1, it is beneficial to adapt the air circulation distance before and after the heat exchanger 6, thereby improving the air circulation efficiency. In this embodiment, U1 is the minimum distance between the outlet 4171 of the accommodating chamber 417 and the windward side contour line 641. U2 is the minimum distance between the outlet 451 of the second air outlet 45 and the leeward side contour line 642.

[0078] Optionally, 30 mm ≤ U1 ≤ 150 mm. For example, U1 can be 30 mm, 60 mm, 80 mm, 100 mm, 110 mm, 120 mm, 130 mm, or 150 mm.

[0079] Optionally, 10 mm ≤ U2 ≤ 150 mm. For example, U2 can be selected as 10 mm, 20 mm, 30 mm, 60 mm, 80 mm, 100 mm, 110 mm, 120 mm, 130 mm or 150 mm.

[0080] Optionally, as Figure 2 shown, the height of the upper fin segment 1 is h1, the height of the middle fin segment 2 is h2, and the height of the lower fin segment 3 is h3. And, 0.3 ≤ U1 / (h1 + h2 + h3) ≤ 2. For example, U1 / (h1 + h2 + h3) can be selected as 0.3, 0.5, 0.8, 1, 1.2, 1.5, 1.7 or 2. Among them, U1 affects the flow state of the air before entering the heat exchanger 6. If the spacing is too small, it may cause uneven velocity distribution of the air when entering the heat exchanger 6. If the spacing is too large, it may increase the flow loss. The value of h1 + h2 + h3 affects the overall heat transfer height of the fin 64. By optimizing the ratio of U1 / (h1 + h2 + h3), it is ensured that the air flows uniformly and efficiently into contact with the fin 64.

[0081] In some embodiments, the heat exchanger 6 includes fins 64, and the fins 64 include a middle fin segment 2, an upper fin segment 1 and a lower fin segment 3. As Figure 4 (b) shown, the surface of the middle fin segment 2 is provided with a first heat transfer unit 12, and the first heat transfer unit 12 includes P1 first heat transfer structures 121. The upper fin segment 1 is bent and connected to the upper end of the middle fin segment 2, and the surface is provided with a second heat transfer unit 13, and the second heat transfer unit 13 includes P2 second heat transfer structures 131. The lower fin segment 3 is bent and connected to the lower end of the middle fin segment 2, and is on the same side of the middle fin segment 2 as the upper fin segment 1. The surface of the lower fin segment 3 is provided with a third heat transfer unit 14, and the third heat transfer unit 14 includes P3 third heat transfer structures 141. Among them, 1 ≤ P1 < P2, and / or, 1 ≤ P1 < P3, and / or, 1 ≤ P3 < P2.

[0082] In this embodiment, the functions of the first heat transfer structure 121, the second heat transfer structure 131 and the third heat transfer structure 141 are all to enhance the heat transfer capacity of the corresponding fin segment. In the case where the upper fin segment 1 and the lower fin segment 3 are bent, it will affect the direction and velocity of the air flowing through. By optimizing the numerical relationship of P1, P2 and P3, it is possible to adapt to the air flow characteristics of different fin segments, guide the air flow of the middle fin segment 2 to the upper fin segment 1 and the lower fin segment 3, and thus improve the overall heat transfer efficiency of the fin 64.

[0083] Alternatively, 1≤P1≤10. For example, P1 can be 1, 2, 3, 4, 5, 6, 7, 8, 9, or 10. Alternatively, 1≤P2≤10. For example, P2 can be 1, 2, 3, 4, 5, 6, 7, 8, 9, or 10. Alternatively, 1≤P3≤10. For example, P3 can be 1, 2, 3, 4, 5, 6, 7, 8, 9, or 10. For example, each first heat transfer unit 12 includes two first heat transfer structures 121. Each second heat transfer unit 13 includes four second heat transfer structures 131. Each third heat transfer unit 14 includes three third heat transfer structures 141. That is, P1=2, P2=4, and P3=3.

[0084] Optionally, the first heat transfer structure 121 and / or the second heat transfer structure 131 and / or the third heat transfer structure 141 are constructed as a bridge structure 65, such as Figure 5 The bridge structure 65 includes a bridge top wall 651 parallel to the fins 64 and bridge side walls 652 at both ends of the bridge top wall 651 which are obliquely connected to the fins 64 .

[0085] Optionally, the first heat transfer structure 121 and / or the second heat transfer structure 131 and / or the third heat transfer structure 141 are configured as a louver structure 66, such as Figure 6 The shutter structure 66 includes a window top wall 661 that is non-parallel to the fins 64 and window side walls 662 at both ends of the window top wall 661 that are connected to the fins 64 respectively.

[0086] Optionally, 0.5mm≤zn1≤0.7mm, and / or 1mm≤zn2≤1.8mm, and / or 5mm≤zn3≤10mm, and / or 10°≤zn4≤90°, and / or zn5≤2mm. Here, zn1 is the height of the bridge structure 65 or the louver structure 66, zn2 is the width of the bridge structure 65 or the louver structure 66, zn3 is the length of the bridge structure 65 or the louver structure 66, zn4 is the angle between the bridge side wall 652 and the fin 64 or the angle between the window top wall 661 and the fin 64, and zn5 is the spacing between adjacent bridge structures 65 or adjacent louver structures 66.

[0087] In this embodiment, n represents the nth heat transfer structure. For example, when n = 1, z11 represents the height of the bridge structure 65 or louver structure 66 corresponding to the first heat transfer structure 121; when n = 2, z21 represents the height of the bridge structure 65 or louver structure 66 corresponding to the second heat transfer structure 131; when n = 3, z31 represents the height of the bridge structure 65 or louver structure 66 corresponding to the third heat transfer structure 141, and so on. It should be noted that when the first heat transfer unit 12 has multiple bridge structures 65 or louver structures 66, the heights of all bridge structures 65 or louver structures 66 are within the value range of zn1.

[0088] Optionally, the characteristic parameters of the first heat transfer structure 121, the second heat transfer structure 131 and the third heat transfer structure 141 are the same or different, and / or the characteristic parameters of part or all of the first heat transfer structure 121 are the same or different, and / or the characteristic parameters of part or all of the second heat transfer structure 131 are the same or different, and / or the characteristic parameters of part or all of the third heat transfer structure 141 are the same or different. Figure 5 、 Figure 6 and Figure 7 As shown, the characteristic parameters include zn1, zn2, zn3, zn4 and zn5.

[0089] Optionally, 0.5mm≤z11≤0.7mm, and / or, 1.6mm≤z12≤1.8mm, and / or, 3mm≤z13≤10mm, and / or, 10°≤z14≤90°, and / or, z15≤2mm; wherein, z11 is the height of the bridge structure 65 or the louver structure 66 corresponding to the first heat transfer structure 121, z12 is the width of the bridge structure 65 or the louver structure 66 corresponding to the first heat transfer structure 121, z13 is the length of the bridge structure 65 or the louver structure 66 corresponding to the first heat transfer structure 121, and z15 is the spacing between the bridge structures 65 or the louver structures 66 corresponding to adjacent first heat transfer structures 121.

[0090] For example, z11 can be selected as 0.5mm, 0.6mm, or 0.7mm. For example, z12 can be selected as 1.6mm, 1.7mm, or 1.8mm. For example, z13 can be selected as 3mm, 4mm, 5mm, 6mm, 7mm, 8mm, 9mm, or 10mm. For example, z14 can be selected as 10°, 20°, 30°, 45°, 60°, or 90°. When the first heat transfer structure 121 is a bridge structure 65, 1mm≤z15≤2mm. For example, z15 can be selected as 1mm, 1.2mm, 1.4mm, 1.5mm, 1.8mm, or 2mm. When the first heat transfer structure 121 is a louver structure 66, 0≤z15≤2mm. When z15=0mm, it means that there is no gap between the two louver structures 66.

[0091] Optionally, 0.5 mm ≤ z21 ≤ 0.7 mm, and / or, 1 mm ≤ z22 ≤ 1.3 mm, and / or, 5 mm ≤ z23 ≤ 10 mm, and / or, 10° ≤ z24 ≤ 90°, and / or, z25 ≤ 1.7 mm; z21 is the height of the bridge chip structure 65 or the louver structure 66 corresponding to the second heat transfer structure 131, z22 is the width of the bridge chip structure 65 or the louver structure 66 corresponding to the second heat transfer structure 131, z23 is the length of the bridge chip structure 65 or the louver structure 66 corresponding to the second heat transfer structure 131, and z25 is the spacing between the bridge chip structures 65 or the louver structures 66 corresponding to adjacent second heat transfer structures 131.

[0092] For example, z21 can be selected as 0.5 mm, 0.6 mm, or 0.7 mm. For example, z22 can be selected as 1 mm, 1.2 mm, or 1.3 mm. For example, z23 can be selected as 5 mm, 6 mm, 7 mm, 8 mm, 9 mm, or 10 mm. For example, z24 can be selected as 10°, 20°, 30°, 45°, 60°, or 90°. When the second heat transfer structure 131 is the bridge chip structure 65, 1.1 mm ≤ z25 ≤ 1.7 mm. For example, z25 can be selected as 1.1 mm, 1.2 mm, 1.4 mm, 1.5 mm, 1.6 mm, or 1.7 mm. When the second heat transfer structure 131 is the louver structure 66, 0 mm ≤ z25 ≤ 1.7 mm. When z25 = 0 mm, it means that there is no gap between the two louver structures 66.

[0093] Optionally, 0.5 mm < z31 < 0.7 mm, and / or, 1.6 mm < z32 < 1.8 mm, and / or, 5 mm ≤ z33 ≤ 10 mm, and / or, 10° ≤ z34 ≤ 90°, and / or, z35 ≤ 1.7 mm; z31 is the height of the bridge chip structure 65 or the louver structure 66 corresponding to the third heat transfer structure 141, z32 is the width of the bridge chip structure 65 or the louver structure 66 corresponding to the third heat transfer structure 141, z33 is the length of the bridge chip structure 65 or the louver structure 66 corresponding to the third heat transfer structure 141, and z35 is the spacing between the bridge chip structures 65 or the louver structures 66 corresponding to adjacent third heat transfer structures 141.

[0094] For example, z31 can be selected as 0.5mm, 0.6mm or 0.7mm. For example, z32 can be selected as 1.6mm, 1.7mm or 1.8mm. For example, z33 can be selected as 5mm, 6mm, 7mm, 8mm, 9mm or 10mm. For example, z34 can be selected as 10°, 20°, 30°, 45°, 60° or 90°. In the case where the third heat transfer structure 141 is a bridge structure 65, 1.1mm≤z35≤1.7mm, for example, z35 can be selected as 1.1mm, 1.2mm, 1.4mm, 1.5mm, 1.6mm or 1.7mm. In the case where the third heat transfer structure 141 is a louver structure 66, 0mm≤z35≤1.7mm, and when z35=0mm, it means that there is no gap between the two louver structures 66.

[0095] Alternatively, as Figure 8 As shown, the drag coefficient of the middle wing segment 2 is f1, the drag coefficient of the upper wing segment 1 is f2, and the drag coefficient of the lower wing segment 3 is f3; wherein, f1<f2, and / or, f1<f3, and / or, f2=f3.

[0096] In this embodiment, by optimizing the drag coefficients of the three wing segments, it is possible to match the design parameters of different wing segments. Here, the drag coefficient can be determined as follows:

[0097] f = 2F / (ρ*(v^2)), where f is the drag coefficient, F is the wind resistance, ρ is the incoming air density, and v is the wind speed. The wind resistance corresponding to middle wing segment 2 is F1, and the corresponding wind speed is v1; the wind resistance corresponding to upper wing segment 1 is F2, and the corresponding wind speed is v2; and the wind resistance corresponding to lower wing segment 3 is F3, and the corresponding wind speed is v3.

[0098] Because the air density changes minimally, the air density corresponding to each wing segment can be assumed to be equal. Since the pressure differentials before and after the air flows through each wing segment are very similar, we can assume that F1 = F2 = F3. Therefore, f ∝ 1 / (v^2), meaning that f and v are inversely proportional. When f1 < f2, v1 is greater than v2; when f1 < f3, v1 is greater than v3. When f2 = f3, v2 equals v3.

[0099] Optionally, in the upper wing section 1 or the lower wing section 3 , the farther the area is from the middle wing section 2 , the greater the drag coefficient.

[0100] For example, Figure 9As shown in (a), the upper wing section 1 includes a first wind resistance region and a second wind resistance region. The first wind resistance region is close to the middle wing section 2, and the second wind resistance region is located on the side of the first wind resistance region away from the middle wing section 2. Furthermore, the drag coefficient corresponding to the first wind resistance region is f21, and the drag coefficient corresponding to the second wind resistance region is f22, with f1 < f21 < f22.

[0101] For example, Figure 9 (b) The lower wing section 3 includes a third wind resistance region and a fourth wind resistance region. The third wind resistance region is adjacent to the middle wing section 2, and the fourth wind resistance region is located on a side of the third wind resistance region away from the middle wing section 2. Furthermore, the drag coefficient corresponding to the third wind resistance region is f31, and the drag coefficient corresponding to the fourth wind resistance region is f32, with f1 < f31 < f32.

[0102] Alternatively, as Figure 4 、 Figure 10 and Figure 11 As shown, the middle fin section 2 is provided with multiple rows of first heat exchange tube hole groups 61. Each row of first heat exchange tube hole groups 61 extends in the same direction as the second side profile line 21 of the middle fin section 2, with the spacing between adjacent rows of first heat exchange tube hole groups 61 being m1. The upper fin section 1 is provided with multiple rows of second heat exchange tube hole groups 62. Each row of second heat exchange tube hole groups 62 extends in the same direction as the first side profile line 11 of the upper fin section 1, with the spacing between adjacent rows of second heat exchange tube hole groups 62 being m2. The lower fin section 3 is provided with multiple rows of third heat exchange tube hole groups 63. Each row of third heat exchange tube hole groups 63 extends in the same direction as the third side profile line 31 of the lower fin section 3, with the spacing between adjacent rows of third heat exchange tube hole groups 63 being m3. The spacing between adjacent first heat exchange tube holes 611 in the first heat exchange tube hole group 61 is b1, the spacing between adjacent second heat exchange tube holes 621 in the second heat exchange tube hole group 62 is b2, and the spacing between adjacent third heat exchange tube holes 631 in the third heat exchange tube hole group 63 is b3.

[0103] In this embodiment, the first heat exchange tube hole 611, the second heat exchange tube hole 621 and the third heat exchange tube hole 631 are used to pass the heat exchange tubes. The parameter values ​​of m1, m2, m3, b1, b2, and b3 affect the arrangement density of the heat exchange tubes. By adjusting the values ​​of the above parameters, the arrangement of the heat exchange tubes can be adapted to each fin segment, thereby improving the heat exchange efficiency.

[0104] Optionally, 1≤m1 / m3≤1.25. For example, m1 / m3 can be selected as 1, 1.1, 1.15, 1.2 or 1.25.

[0105] Optionally, 1≤m1 / m2≤1.25. For example, m1 / m2 can be selected as 1, 1.1, 1.15, 1.2 or 1.25.

[0106] Alternatively, 1≤m2 / m3≤1.12. For example, m1 / m3 can be selected as 1, 1.1, 1.11, or 1.12.

[0107] Optionally, 1.12≤b1 / b2≤1.43. For example, b1 / b2 can be 1.12, 1.2, 1.25, 1.3, 1.35, 1.4, or 1.43.

[0108] Optionally, 1.05≤b1 / b3≤1.25. For example, b1 / b3 can be 1.05, 1.1, 1.15, 1.2, or 1.25.

[0109] In the above embodiments, the shape of the fin 64 can be symmetrical or asymmetrical.

[0110] Alternatively, as Figure 12 As shown, the shape of fin 64 is symmetrical. The angle s1 between the first leeward contour line 111 and the horizontal direction, the angle s3 between the third leeward contour line 311 and the horizontal direction, s1 = s3, the angle s2 between the first windward contour line 112 and the horizontal direction, and the angle s4 between the third windward contour line 312 and the horizontal direction, s2 = s4. At this point, the curvature of the upper wing segment 1 is the same as that of the lower wing segment 3, forming a symmetrical shape.

[0111] Alternatively, as Figure 13 As shown, the shape of fin 64 is asymmetrical. The angle s1 between the first leeward side contour line 111 and the horizontal direction, the angle s3 between the third leeward side contour line 311 and the horizontal direction, s1 ≠ s3, the angle s2 between the first windward side contour line 112 and the horizontal direction, and the angle s4 between the third windward side contour line 312 and the horizontal direction, s2 ≠ s4. In this case, the curvature of the upper wing segment 1 is different from the curvature of the lower wing segment 3.

[0112] Alternatively, as Figure 14 and Figure 15 As shown, the width of the upper wing section 1 is W1, the width of the middle wing section 2 is W2, and the width of the lower wing section 3 is W3, wherein W2≥W1, and / or W2>W3.

[0113] In this embodiment, W1 can be understood as the distance between the first windward side contour line 112 and the first leeward side contour line 111. W2 can be understood as the distance between the second windward side contour line 212 and the second leeward side contour line 211. W3 can be understood as the distance between the third windward side contour line 312 and the third leeward side contour line 311. W2≥W1, that is, the width of the middle wing segment 2 is greater than or equal to the width of the upper wing segment 1. W2>W3, that is, the width of the middle wing segment 2 is greater than the width of the lower wing segment 3, which is conducive to matching the shape of the fin 64 with the uneven distribution of wind speed generated by the indoor fan 5 in the air duct, thereby improving the heat exchange efficiency of the heat exchanger 6.

[0114] Optionally, 1≤W2 / W1≤2, and / or, 1≤W2 / W3≤2.

[0115] Optionally, 1 < W2 / W1 ≤ 2, and 1 < W2 / W3 ≤ 2. In the disclosed embodiment, the width of the middle wing segment 2 is relatively large, greater than the widths of the upper wing segment 1 and the lower wing segment 3. This improves the effectiveness of the middle wing segment 2 in guiding airflow to the upper wing segment 1 and the lower wing segment 3, respectively, and improves the uniformity of the overall wind speed distribution of the fins 64.

[0116] In combination with the above-described embodiments of the present application, the heat exchanger 6 and air conditioner of the present application have significantly improved performance compared to existing I-fin heat exchangers (heat exchangers with I-shaped fin profiles) and C-fin heat exchangers (heat exchangers with C-shaped fin profiles). A comparison of the performance with the prior art is shown below.

[0117] Figure 16 The velocity distribution cloud diagram of the heat exchanger 6 of this application is compared with that of the existing I-type fin heat exchanger. Figure 16 The figure a above is the velocity distribution cloud diagram of the existing I-type fin heat exchanger. Figure 16 The following figure b is a velocity distribution cloud diagram of the heat exchanger 6 of each embodiment of the present application.

[0118] from Figure 16 It can be seen that the I-type fin heat exchanger has the characteristics of high wind speed at the top and low wind speed at the bottom. The wind speed distribution is uneven and the heat transfer efficiency of the heat exchanger is low. Figure 16 As shown in the upper circle of a in the figure, the area with low wind speed in the lower part is as follows Figure 16 As shown in the lower circle of a in .

[0119] The heat exchanger 6 provided by this application effectively guides the incoming flow in the middle high wind speed zone to the upper and lower parts, and the overall wind speed distribution is uniform. The uniform distribution of the wind field improves the uniformity of the heat exchange field, and the overall heat exchange performance of the heat exchanger 6 is improved. Figure 16 As shown in b.

[0120] The existing C-type fin heat exchanger has a large flow stagnation zone in the middle on the leeward side, and the outlet wind speed distribution is uneven. Compared with the existing C-type fin heat exchanger, the heat exchanger 6 provided by the embodiment of the present disclosure effectively guides the incoming flow in the middle high wind speed zone to the upper and lower parts, significantly reduces the flow stagnation zone in the middle on the leeward side, and the outlet wind speed distribution is more uniform. Figure 17 From the velocity distribution cloud diagram shown, it can be seen that the C-type fin heat exchanger has a large flow stagnation area in the middle of the leeward side. Figure 18 For Figure 17 Velocity distribution cloud diagram of the heat exchanger 6 of the present application measured at the same wind speed. Figure 18 As can be seen from the figure, the flow stagnation zone on the leeward side of the heat exchanger 6 is significantly reduced.

[0121] Figure 19 This is the pressure distribution cloud diagram of the C-type fin heat exchanger. Figure 20 This is a pressure distribution cloud diagram of the heat exchanger 6 provided in an embodiment of the present disclosure. It can be measured that the pressure drop between the windward and leeward sides of an existing C-fin heat exchanger is 278 Pa, while the pressure drop between the windward and leeward sides of the heat exchanger 6 provided in an embodiment of the present disclosure is 271 Pa. It can be seen that the pressure drop of the existing C-fin heat exchanger is larger. Compared with the C-fin heat exchanger, the pressure drop of the heat exchanger 6 provided in an embodiment of the present disclosure is reduced by 2.5%.

[0122] The above description and the accompanying drawings sufficiently illustrate the embodiments of the present disclosure to enable those skilled in the art to practice them. Other embodiments may include structural and other changes. The embodiments represent only possible variations. Unless expressly required, individual components and functions are optional, and the order of operations may vary. Portions and features of some embodiments may be included in or replace portions and features of other embodiments. The embodiments of the present disclosure are not limited to the structures described above and shown in the accompanying drawings, and various modifications and changes may be made without departing from the scope thereof. The scope of the present disclosure is limited only by the appended claims.

Claims

1. A heat exchanger, characterized in that: It includes fins (64), and the fins (64) include: A middle fin segment (2) with a first heat transfer unit (12) provided on its surface; wherein, the first heat transfer unit (12) includes P1 first heat transfer structures (121); An upper fin segment (1) bent and connected to the upper end of the middle fin segment (2), with a second heat transfer unit (13) provided on its surface; wherein, the second heat transfer unit (13) includes P2 second heat transfer structures (131); A lower fin segment (3) bent and connected to the lower end of the middle fin segment (2) and located on the same side of the middle fin segment (2) as the upper fin segment (1); a third heat transfer unit (14) is provided on the surface of the lower fin segment (3), and the third heat transfer unit (14) includes P3 third heat transfer structures (141); Wherein, 1≤P1<P2, and / or, 1≤P1<P3, and / or, 1≤P3<P2.

2. The heat exchanger according to claim 1, wherein The first heat transfer structure (121) and / or the second heat transfer structure (131) and / or the third heat transfer structure (141) is / are configured as a bridge plate structure (65) or a louver structure (66); The bridge plate structure (65) includes a bridge top wall (651) parallel to the fin (64), and bridge side walls (652) respectively and obliquely connected to the fin (64) at both ends of the bridge top wall (651); the louver structure (66) includes a window top wall (661) non - parallel to the fin (64), and window side walls (662) respectively connected to the fin (64) at both ends of the window top wall (661).

3. The heat exchanger according to claim 2, wherein 0.5mm≤zn1≤0.7mm, and / or, 1mm≤zn2≤1.8mm, and / or, 5mm≤zn3≤10mm, and / or, 10°≤zn4≤90°, and / or, zn5≤2mm; Wherein, znl is the height of the bridge plate structure (65) or the louver structure (66), zn2 is the width of the bridge plate structure (65) or the louver structure (66), zn3 is the length of the bridge plate structure (65) or the louver structure (66), zn4 is the included angle between the bridge side wall (652) and the fin (64) or the included angle between the window top wall (661) and the fin (64), and zn5 is the spacing between adjacent bridge plate structures (65) or adjacent louver structures (66).

4. The heat exchanger according to claim 3, wherein The characteristic parameters of the first heat transfer structure (121), the second heat transfer structure (131) and the third heat transfer structure (141) are the same or different, and / or, the characteristic parameters of some or all of the first heat transfer structures (1(21) are the same or different, and / or, the characteristic parameters of some or all of the second heat transfer structures (131) are the same or different, and / or, the characteristic parameters of some or all of the third heat transfer structures (141) are the same or different; Wherein, the characteristic parameters include zn1, zn2, zn3, zn4 and zn5.

5. The heat exchanger according to any one of claims 1 to 4, wherein The drag coefficient of the middle wing segment (2) is f1, the drag coefficient of the upper wing segment (1) is f2, and the drag coefficient of the lower wing segment (3) is f3; Among them, f1<f2, and / or, f1<f3, and / or, f2=f3.

6. The heat exchanger according to claim 5, characterized in that In the upper wing section (1) or the lower wing section (3), the farther the area is from the middle wing section (2), the greater the drag coefficient.

7. The heat exchanger according to any one of claims 1 to 4, characterized in that: The middle fin section (2) is provided with a plurality of rows of first heat exchange tube hole groups (61), the extension direction of each row of the first heat exchange tube hole groups (61) is the same as the extension direction of the second side contour line (21) of the middle fin section (2), wherein the spacing between two adjacent rows of the first heat exchange tube hole groups (61) is m1; The upper fin section (1) is provided with a plurality of rows of second heat exchange tube hole groups (62), the extension direction of each row of the second heat exchange tube hole groups (62) being the same as the extension direction of the first side contour line (11) of the upper fin section (1), wherein the spacing between two adjacent rows of the second heat exchange tube hole groups (62) is m2; The lower fin section (3) is provided with a plurality of rows of third heat exchange tube hole groups (63), the extension direction of each row of the third heat exchange tube hole groups (63) is the same as the extension direction of the third side contour line (31) of the lower fin section (3), wherein the spacing between two adjacent rows of the third heat exchange tube hole groups (63) is m3; Among them, 1≤m1 / m3≤1.25, and / or, 1≤m1 / m2≤1.25, and / or, 1≤m2 / m3≤1.

12.

8. The heat exchanger according to claim 7, characterized in that The spacing between adjacent first heat exchange tube holes (611) in the first heat exchange tube hole group (61) is b1, the spacing between adjacent second heat exchange tube holes (621) in the second heat exchange tube hole group (62) is b2, and the spacing between adjacent third heat exchange tube holes (631) in the third heat exchange tube hole group (63) is b3; Among them, 1.12≤b1 / b2≤1.43, and / or, 1.05≤b1 / b3≤1.

25.

9. The heat exchanger according to any one of claims 1 to 4, characterized in that: The width of the upper wing segment (1) is W1, the width of the middle wing segment (2) is W2, and the width of the lower wing segment (3) is W3; Among them, W2≥W1, and / or, W2>W3.

10. An air conditioner, characterized in that: Comprising the heat exchanger according to any one of claims 1 to 9.

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