Heat exchanger with vortex generation unit and air conditioner

Abstract

The invention relates to the technical field of air conditioners, and discloses a heat exchanger with vortex generation units, which comprises a fin, the fin comprises a middle fin section, a first heat exchange pipe hole and a second fin section, the upper fin section is obliquely connected to the upper end of the middle fin section; the lower fin section is obliquely connected to the lower end of the middle fin section, and the lower fin section and the upper fin section are located on the same side of the middle fin section; an included angle area is formed by taking the center of the first heat exchange tube hole as a vertex, one side edge of the included angle area is parallel to the air inlet direction, and an opening of an included angle alpha of the included angle area faces the air inlet direction; wherein the vortex generation unit is arranged in the included angle area. The invention further discloses the air conditioner.

Description

Technical Field

[0001] This application relates to the field of air conditioner technology, for example to a heat exchanger and air conditioner having a vortex generating unit. Background Technology

[0002] In air conditioners, heat exchangers, including evaporators and condensers, are the main energy-consuming structural components. The performance of the heat exchanger directly affects the energy consumption level of the air conditioner. Wall-mounted, floor-standing, and ducted household air conditioners widely use finned tube heat exchangers, whose external air-side thermal resistance typically accounts for 70%-90% of the total thermal resistance, thus determining the overall performance of the heat exchanger.

[0003] In the process of implementing the embodiments of this disclosure, at least the following problems were found in the related art: The heat exchange performance of the fins is poor.

[0004] It should be noted that the information disclosed in the background section above is only used to enhance the understanding of the background of this application, and therefore may include information that does not constitute prior art known to those skilled in the art. Summary of the Invention

[0005] To provide a basic understanding of some aspects of the disclosed embodiments, a brief summary is given below. This summary is not intended as a general commentary, nor is it intended to identify key / important components or describe the scope of protection of these embodiments, but rather as a prelude to the detailed description that follows.

[0006] This disclosure provides a heat exchanger and air conditioner with a vortex generating unit, which improves the heat exchange performance of the fins.

[0007] In some embodiments, the heat exchanger having a vortex generating unit includes: fins, the fins comprising: The middle fin segment has a vortex generating unit and a first heat exchange tube hole on its surface; The upper wing segment is obliquely connected to the upper end of the middle wing segment; The lower wing segment is obliquely connected to the lower end of the middle wing segment and is located on the same side of the middle wing segment as the upper wing segment; An angled region is formed with the center of the first heat exchange tube hole as the vertex. One side of the angled region is parallel to the air inlet direction, and the opening of the angle α of the angled region faces the air inlet direction. The vortex generating unit is arranged in the angled region.

[0008] In some embodiments, the air conditioner includes the heat exchanger.

[0009] The heat exchanger and air conditioner with vortex generating unit provided in this disclosure can achieve the following technical effects: For the three-section fins with inclined connections in this application, the vortex generating unit is set in the included angle region. Since the included angle region matches the air inlet direction, turbulence is only generated in the core included angle region around the first heat exchange tube hole. During the process of the incoming flow in the high-velocity zone in the middle of the fin being guided to the upper and lower parts, the vortex generating unit set in the above position can play a targeted turbulence role, avoiding ineffective turbulence and excessive wind resistance, improving the overall uniformity of wind speed distribution, and helping to reduce the flow stagnation zone on the leeward side of the fin, thereby improving the heat exchange performance of the fin.

[0010] The above general description and the description below are exemplary and illustrative only and are not intended to limit this application. Attached Figure Description

[0011] One or more embodiments are illustrated by way of example with reference to the accompanying drawings. These illustrations and drawings do not constitute a limitation on the embodiments. Elements having the same reference numerals in the drawings are shown as similar elements. The drawings are not to be scaled. And wherein: Figure 1 This is a schematic diagram of the structure of an air conditioner provided in an embodiment of this disclosure; Figure 2 This is a schematic diagram of the angles corresponding to the windward profile lines provided in the embodiments of this disclosure; Figure 3 This is a schematic diagram of the volute structure provided in an embodiment of this disclosure; Figure 4 This is a schematic diagram of the structure of the fins provided in the embodiments of this disclosure, wherein (a) is a schematic diagram of the windward side outline, and (b) is a schematic diagram of the heat transfer unit of each fin segment; Figure 5 This is a schematic diagram of the characteristic parameters of the bridge plate structure provided in the embodiments of this disclosure; Figure 6 This is a schematic diagram of the characteristic parameters of the louver structure provided in the embodiments of this disclosure; Figure 7 This is a schematic diagram of the characteristic parameters of the louver structure provided in the embodiments of this disclosure; Figure 8 This is a schematic diagram of the drag coefficient of each wing segment provided in the embodiments of this disclosure; Figure 9 This is a schematic diagram of another drag coefficient of each wing segment provided in the embodiments of this disclosure, wherein (a) is a schematic diagram of the drag coefficients corresponding to the two drag zones on the upper wing segment, and (b) is a schematic diagram of the drag coefficients corresponding to the two drag zones on the lower wing segment. Figure 10 This is a schematic diagram of the structure of a fin provided in an embodiment of this disclosure; Figure 11 This is a schematic diagram of another fin structure provided in an embodiment of this disclosure; Figure 12 This is a schematic diagram of another fin structure provided in an embodiment of this disclosure; Figure 13 This is a schematic diagram of another fin structure provided in an embodiment of this disclosure; Figure 14 This is a schematic diagram of another fin structure provided in an embodiment of this disclosure; Figure 15 This is a schematic diagram of another fin structure provided in an embodiment of this disclosure; Figure 16 This is a velocity distribution cloud map of the heat exchanger; Figure 17 This is a velocity distribution cloud map of a C-type finned heat exchanger; Figure 18 This is a velocity distribution cloud map of the heat exchanger provided in the embodiments of this disclosure; Figure 19 This is a pressure distribution cloud map of a C-type finned heat exchanger; Figure 20 This is a pressure distribution cloud map of the heat exchanger provided in an embodiment of this disclosure; Figure 21 This is a schematic diagram of the structure of the vortex generating unit provided in the embodiments of this disclosure; Figure 22 This is a schematic diagram of relevant parameters of the vortex generating unit provided in the embodiments of this disclosure; Figure 23 This is a schematic diagram of the relevant parameters of the vortex generating structure provided in the embodiments of this disclosure.

[0012] Figure label: 1. Upper wing segment; 11. First side profile; 111. First leeward side profile; 112. First windward side profile; 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; 2. Middle wing segment; 21. Second lateral profile; 211. Second leeward profile; 212. Second windward profile; 3. Lower wing segment; 31. Third lateral profile; 311. Third leeward profile; 312. Third windward profile; 4. Indoor unit housing; 41. Volute; 411. First diffuser plate; 412. Second diffuser plate; 413. Third diffuser plate; 414. Fourth diffuser plate; 415. Fifth diffuser plate; 416. Sixth diffuser plate; 417. Receiving cavity; 4171. Outlet of the receiving cavity; 418. Axis of the volute; 42. Air inlet; 43. Air outlet; 44. First air outlet; 441. Outlet of the first air outlet; 45. Second air outlet; 451. Outlet of the second air outlet; 46. Air outlet; 5. Indoor fan; 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 profile; 642. Leeward side profile; 65. Bridge structure; 651. Bridge top wall; 652. Bridge side wall; 66. Louver structure; 661. Window top wall; 662. Window side wall; 67. Vortex generating unit; 671. Vortex generating structure. Detailed Implementation

[0013] To provide a more detailed understanding of the features and technical content of the embodiments of this disclosure, the implementation of the embodiments of this disclosure will be described in detail below with reference to the accompanying drawings. The accompanying drawings are for illustrative purposes only and are not intended to limit the embodiments of this disclosure. In the following technical description, for ease of explanation, several details are used to provide a full understanding of the disclosed embodiments. However, one or more embodiments may still be implemented without these details. In other cases, well-known structures and devices may be simplified in their depiction to simplify the drawings.

[0014] The terms "first," "second," etc., used in the specification, claims, and accompanying drawings of this disclosure are used to distinguish similar objects and are not necessarily used to describe a specific order or sequence. It should be understood that such data can be interchanged where appropriate for describing embodiments of this disclosure herein. Furthermore, the terms "comprising" and "having," and any variations thereof, are intended to cover non-exclusive inclusion.

[0015] In this disclosure, the terms "upper," "lower," "inner," "middle," "outer," "front," and "rear," etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. These terms are primarily for better description of the embodiments of this disclosure and their implementations, and are not intended to limit the indicated devices, elements, or components to having a specific orientation, or to require them to be constructed and operated in a specific orientation. Furthermore, some of the aforementioned terms may be used to indicate other meanings besides orientation or positional relationship; for example, the term "upper" may in some cases indicate a dependency or connection relationship. Those skilled in the art can understand the specific meaning of these terms in the embodiments of this disclosure according to the specific circumstances.

[0016] Furthermore, the terms "set up," "connect," and "fix" should be interpreted broadly. For example, "connection" can be a fixed connection, a detachable connection, or an integral structure; it can be a mechanical connection or an electrical connection; it can be a direct connection or an indirect connection through an intermediate medium, or it can be an internal connection between two devices, components, or parts. Those skilled in the art can understand the specific meaning of the above terms in the embodiments of this disclosure according to the specific circumstances.

[0017] Unless otherwise stated, the term "multiple" means two or more.

[0018] In this embodiment of the disclosure, the character " / " indicates that the objects before and after it are in an "or" relationship. For example, A / B means: A or B.

[0019] 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.

[0020] It should be noted that, unless otherwise specified, the embodiments and features described in the present disclosure can be combined with each other.

[0021] This disclosure provides an air conditioner, which includes an indoor unit housing 4, a volute 41, an indoor fan 5, and a heat exchanger 6. For example... Figure 1 and Figure 3 As shown, the volute 41 includes a receiving cavity 417 and an air outlet 46. The indoor fan 5 is disposed in the receiving cavity 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, passes through the heat exchanger 6, and then flows into the room through the air outlet 43.

[0022] In some embodiments, the air conditioner includes a volute 41 and a heat exchanger 6. The volute 41 includes a receiving cavity 417 and an air outlet 46. The receiving cavity 417 is used to install an indoor fan 5, and the air outlet 46 communicates with the outlet 4171 of the receiving cavity 417. The heat exchanger 6 is disposed within the air outlet 46 and includes a plurality of fins 64 arranged parallel to each other 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 together. The upper fin segment 1 and the lower fin segment 3 are both inclined toward the receiving cavity 417, and the middle fin segment 2 includes a second windward profile 212. Figure 2 and Figure 3As shown, the midpoint of the longitudinal section of the outlet 4171 of the accommodating cavity 417 is the reference point H, and the angle subtended by the second windward profile 212 corresponding to the reference point H is c1, where 6°≤c1≤50°. For example, c1 can be selected as 6°, 10°, 15°, 20°, 25°, 30°, 35°, 40°, 45°, or 50°.

[0023] In this embodiment, the orientation of the air conditioner is as follows: Figure 2 As shown, the accommodating cavity 417 is located at the rear of the air conditioner, and the air outlet 46 is located at the front of the air conditioner. The heat exchanger 6 is installed after the air outlet 46. The three sections of the fins 64, from top to bottom, are called the upper fin section 1, the middle fin section 2, and the lower fin section 3. Since the accommodating cavity 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... Figure 3 As shown. The cross-section along the front-to-back direction of the air conditioner is called the longitudinal section, and the cross-section perpendicular to the longitudinal section is called the cross section. The three-segment fins 64 are arc-shaped or bow-shaped, hence also called arc-shaped fins 64 or bow-shaped fins 64. This shape design guides the airflow. The opening angle c1 of the middle fin segment 2 is designed between 6° and 50°, which helps to optimize the contact angle between the airflow and the middle fin segment 2, making heat exchange more complete and thus improving heat exchange efficiency.

[0024] Optionally, 6°≤c1≤30°. For example, c1 can be 6°, 8°, 12°, 16°, 22°, 26°, 28° or 30°.

[0025] Optionally, the upper wing segment 1, the middle wing segment 2, and the lower wing segment 3 of the wing 64 are integrally formed. For example... Figure 4 As shown in (a), to avoid confusion, the upper wing segment 1 includes a first side profile 11, which includes a first windward side profile 112 and a first leeward side profile 111. The middle wing segment 2 includes a second side profile 21, which includes a second windward side profile 212 and a second leeward side profile 211. The lower wing segment 3 includes a third side profile 31, which includes a third windward side profile 312 and a third leeward side profile 311. Furthermore, the first windward side profile 112, the second windward side profile 212, and the third windward side profile 312 form the windward side profile 641, and the first leeward side profile 111, the second leeward side profile 211, and the third leeward side profile 311 form the leeward side profile 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 or may not be rounded.

[0026] Optionally, such as Figure 2As shown, the upper wing segment 1 includes a first windward profile line 112, and the angle of the first windward profile line 112 corresponding to the reference point H is c2. The lower wing segment 3 includes a third windward profile line 312, and the angle of the third windward profile line 312 corresponding to the reference point H is c3.

[0027] In this embodiment, the relationship between c1, c2, and c3 is defined. Specifically, 0.3 ≤ c2 / c1 ≤ 0.7, for example, c2 / c1 can be 0.3, 0.4, 0.5, 0.6, or 0.7. Also, 0.5 ≤ c3 / c1 ≤ 0.9, for example, c3 / c1 can be 0.5, 0.6, 0.7, 0.8, or 0.9. Finally, 0.6 ≤ c1 / (c2+c3) ≤ 1, for example, c1 / (c2+c3) can be 0.6, 0.7, 0.8, 0.9, or 1. By designing the proportional relationship of the three opening angles, the contact angles between the airflow and the three wing segments can be optimized, resulting in a more uniform airflow distribution.

[0028] Optionally, such 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. Furthermore, 0.2 ≤ h2 / (h1+h2+h3) ≤ 0.5. For example, h2 / (h1+h2+h3) can be chosen as 0.2, 0.3, 0.4, or 0.5. This design, through the height relationship of the three wing segments, allows for matching the distribution of circulating air. With the upper wing segment 1 and the lower wing segment 3 arranged at an angle, the length of the slope section of fin 64 is shorter, reducing the risk of poor drainage on the surface of fin 64.

[0029] Optionally, the height of the longitudinal section of the outlet 4171 of the accommodating cavity 417 is T, and the height of the middle fin segment 2 is h2, where 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. Here, h2 affects the heat exchange area of ​​the middle fin segment 2, and T affects the air outlet area. Through a reasonable proportional design, the air outlet area is matched with the heat exchange area of ​​the middle fin segment 2. Furthermore, combining the design of the three opening angles and the height relationship of the three fin segments, when the wind speed corresponding to the middle fin segment 2 is relatively high, it is beneficial for the air flowing through the middle fin segment 2 to diffuse upwards to the upper fin segment 1 and lower fin segment 3, ensuring that the airflow is matched with the heat exchange area, thereby improving heat exchange efficiency.

[0030] Optionally, the middle wing segment 2 also includes a second leeward profile line 211, both of which are straight lines and parallel to each other. Thus, the middle wing segment 2 is straight.

[0031] In some embodiments, the air conditioner includes a volute 41 and a heat exchanger 6. The volute 41 includes an air outlet 46, which includes a first diffuser 411. The heat exchanger 6 is disposed in the air outlet 46 and includes a plurality of fins 64 arranged parallel to each other along the axis 418 of the volute 41. The fins 64 include a windward profile 641, and the first diffuser 411 extends toward the windward profile 641. Figure 3 As shown, the intersection point of the extension direction of the first diffuser plate 411 and the windward profile line 641 is T1. The length between T1 and the nearest endpoint of the windward profile line 641 is t1, and the total length of the windward profile line 641 is t, with t1 / t ≤ 30%. In this way, the first diffuser plate 411 and the windward profile line 641 intersect, which is beneficial for guiding the airflow. Furthermore, the t1 / t ratio design helps to match the airflow guided by the first diffuser plate 411 with the length of the windward profile line 641, thereby improving heat exchange efficiency.

[0032] In this embodiment, the total length t of the windward side profile 641 is equal to the sum of the lengths of the first windward side profile 112, the second windward side profile 212, and the third windward side profile 312. If the intersection point T1 is closest to the upper end of the windward side profile 641, then t1 is equal to the length between the intersection point T1 and the upper end of the windward side profile 641; if the intersection point T1 is closest to the lower end of the windward side profile 641, then t1 is equal to the length between the intersection point T1 and the lower end of the windward side profile 641.

[0033] Optionally, 5% ≤ t1 / t ≤ 30%. For example, t1 / t can be selected as 5%, 10%, 15%, 20%, 25%, or 30%.

[0034] Optionally, such as Figure 3 As shown, the angle between the first diffuser plate 411 and the horizontal direction is φ1, where 5°≤φ1≤60°. For example, φ1 can be selected as 5°, 10°, 20°, 30°, 40°, 50°, or 60°. By adjusting the value of φ1, the position of the intersection point T1 can be adjusted, and the smaller φ1 is, the closer the intersection point T1 is to the upper end of the first windward side contour line 112.

[0035] Optionally, the fin 64 includes an upper fin segment 1, a middle fin segment 2, and a lower fin segment 3 connected in sequence, with both the upper fin segment 1 and the lower fin segment 3 inclined towards the axis 418 of the volute 41. The windward profile 641 corresponding to the upper fin segment 1 is called the first windward profile 112, and the extending direction of the first diffuser plate 411 intersects the first windward profile 112 at T1. Here, the first diffuser plate 411 is located at the upper part of the volute 41.

[0036] Optionally, such as Figure 3As shown, the air outlet 46 also includes a second diffuser 412, which is spaced apart below the first diffuser 411 and extends toward the third windward profile line 312. The intersection point of the extension direction of the second diffuser 412 and the third windward profile line 312 is T2, and the length between T2 and the lower end of the third windward profile line 312 is t2, where t2 / t ≤ 30%. Further, 5% ≤ t2 / t ≤ 30%. For example, t2 / t can be selected as 5%, 10%, 15%, 20%, 25%, or 30%. In this way, the second diffuser 412 intersects with the third windward profile line 312, which is beneficial for guiding the airflow. Furthermore, the t2 / t ratio design helps to match the airflow guided by the second diffuser 412 with the length of the windward profile line 641.

[0037] Optionally, such as Figure 3 As shown, the angle φ2 between the second diffuser plate 412 and the horizontal direction is 5°≤φ2≤60°. For example, φ2 can be selected as 5°, 10°, 20°, 30°, 40°, 50°, or 60°. By adjusting the value of φ2, the position of the intersection point T2 can be adjusted, and the larger the value of φ2, the closer the intersection point T2 is to the lower end of the third windward profile line 312. In this way, the first diffuser plate 411 and the second diffuser plate 412 form a diffusion-type airflow guide. The design of the values ​​of φ1 and φ2, combined with the ratio design of t1 / t and t2 / t, enables the air to diffuse evenly towards the heat exchanger 6.

[0038] Optionally, such 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 profile line 642, and the leeward profile line 642 corresponding to the upper fin segment 1 is called the first leeward profile line 111. Furthermore, the first leeward profile line 111 intersects with the third diffuser plate 413 at an angle γ1, where 20°≤γ1≤90°. For example, γ1 can be selected as 20°, 30°, 40°, 50°, 60°, 70°, 80°, or 90°.

[0039] Optionally, such as Figure 3As shown, the air outlet 46 also includes a fourth diffuser 414 and a sixth diffuser 416. The fourth diffuser 414 is connected to the second diffuser 412 and extends downward, while the sixth diffuser 416 is connected to the fourth diffuser 414 and extends upward. The fin 64 also includes a leeward side profile line 642, and the leeward side profile line 642 corresponding to the lower fin segment 3 is called the third leeward side profile line 311. Furthermore, the third leeward side profile line 311 intersects with the sixth diffuser 416 at an angle γ2, where 20°≤γ2≤90°. For example, γ2 can be selected as 20°, 30°, 40°, 50°, 60°, 70°, 80°, or 90°.

[0040] In some embodiments, the volute 41 includes a receiving cavity 417 and an air outlet 46, the air outlet 46 including a first air outlet 44 and a second air outlet 45. For example... Figure 3 As shown, the cavity 417 is used to install an indoor fan 5. A first air outlet 44 is connected to the outlet 4171 of the cavity 417, and the cross-sectional area of ​​the gas flow in the first air outlet 44 gradually increases along the airflow direction. A second air outlet 45 is connected to the outlet 441 of the first air outlet 44 and is used to house a heat exchanger 6, and at least a portion of the cross-sectional area of ​​the gas flow in the second air outlet 45 is larger than the maximum cross-sectional area of ​​the gas flow in the first air outlet 44.

[0041] In this embodiment, the orientation of the air conditioner is as follows: Figure 2 As shown, the cross-section along the front-to-back direction of the air conditioner is called the longitudinal section, and the cross-section perpendicular to the longitudinal section is called the cross-section. The cross-sectional area of ​​the gas flow in the first air outlet 44 refers to the area of ​​the first air outlet 44 on the cross-section, and the cross-sectional area of ​​the gas flow in the second air outlet 45 refers to the area of ​​the second air outlet 45 on the cross-section. The heat exchanger 6 is entirely disposed within the second air outlet 45, ensuring that all the air outlets of the volute 41 exchange heat with the heat exchanger 6. Furthermore, since the cross-sectional area of ​​the gas flow in the first air outlet 44 gradually increases along the air outlet direction, a diffusion-type flow is formed, and the reduced flow velocity after diffusion facilitates full contact between the air and the heat exchanger 6. Since at least part of the cross-sectional area of ​​the gas flow in the second air outlet 45 is larger than the maximum cross-sectional area of ​​the gas flow in the first air outlet 44, the abrupt increase in cross-sectional area of ​​the second air outlet 45 acts as a buffer, which is beneficial for the uniform contact between the air and the heat exchanger 6. In this way, the structural design of the volute 41 effectively improves the heat exchange efficiency between the air and the heat exchanger 6.

[0042] Optionally, such as Figure 3As 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 φ1, where 5°≤φ1≤60°. The second diffuser plate 412 is spaced apart from the first diffuser plate 411 and is not parallel to it. The second diffuser plate 412 is parallel to the axis 418 of the volute 41 and extends downward. The angle between the second diffuser plate 412 and the horizontal direction is φ2, where 5°≤φ2≤60°. 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 diffusion-type airflow guide, and the diffusion direction is optimized by the design of the values ​​of φ1 and φ2, which is beneficial for the uniform diffusion of air towards the heat exchanger 6.

[0043] Optionally, such 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 upwards, with an angle of φ3 between its extension direction and that of the first diffuser plate 411, where 10°≤φ3≤30°. The fourth diffuser plate 414 is connected to the second diffuser plate 412 and extends downwards, with an angle of φ5 between its extension direction and that of the second diffuser plate 412, where 15°≤φ5≤35°. The fifth diffuser plate 415 is connected to the third diffuser plate 413 and extends downwards, with an angle of φ4 between its extension direction and that of the third diffuser plate 413, where 40°≤φ4≤60°. The sixth diffuser plate 416 is connected to the fourth diffuser plate 414 and extends upward. The angle between the extending directions of the sixth diffuser plate 416 and the fourth diffuser plate 414 is φ6, and 40°≤φ6≤60°. For example, φ3 can be selected as 10°, 15°, 20°, 25°, or 30°. For example, φ4 can be selected as 40°, 45°, 50°, 55°, or 60°. For example, φ5 can be selected as 15°, 20°, 25°, 30°, or 35°. For example, φ6 can be selected as 40°, 45°, 50°, 55°, or 60°.

[0044] In this embodiment, the volute 41 is installed after the air conditioner is mounted, and the orientation of the air conditioner is as follows: Figure 2 As shown. The upward extension of the diffuser plate refers to its extension towards the top of the air conditioner, while the downward extension refers to its extension towards the bottom of the air conditioner. Thus, through the design of multiple diffusers in the second air outlet 45, and the specific values ​​of φ3, φ4, φ5, and φ6, the cross-sectional area of ​​the portion of the second air outlet 45 located upstream of the heat exchanger 6 abruptly increases, thereby providing a buffering effect. Furthermore, the cross-sectional area of ​​the portion of the second air outlet 45 near the air outlet 43 decreases again, thereby concentrating the air.

[0045] In some embodiments, the air conditioner includes a heat exchanger 6 and the aforementioned volute 41. For example... Figure 2 As shown, heat exchanger 6 is disposed in the second air outlet 45. The distance between the outlet 4171 of the accommodating cavity 417 and heat exchanger 6 is U1, and the distance between the outlet 451 of the second air outlet 45 and heat exchanger 6 is U2. Furthermore, 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 match the airflow distance before and after heat exchanger 6, thereby improving airflow efficiency. In this embodiment, U1 is the minimum distance between the outlet 4171 of the accommodating cavity 417 and the windward profile line 641. U2 is the minimum distance between the outlet 451 of the second air outlet 45 and the leeward profile line 642.

[0046] Optionally, 30mm ≤ U1 ≤ 150mm. For example, U1 can be selected as 30mm, 60mm, 80mm, 100mm, 110mm, 120mm, 130mm or 150mm.

[0047] Optionally, 10mm ≤ U2 ≤ 150mm. For example, U2 can be selected as 10mm, 20mm, 30mm, 60mm, 80mm, 100mm, 110mm, 120mm, 130mm or 150mm.

[0048] Optionally, such as Figure 2 As 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. Furthermore, 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. U1 affects the flow state of the airflow before entering the heat exchanger 6. Too small a spacing may lead to uneven velocity distribution of the airflow upon entering the heat exchanger 6, while too large a spacing may increase flow losses. The value of h1+h2+h3 affects the overall heat exchange height of the fins 64. By optimizing the ratio of U1 / (h1+h2+h3), it is ensured that the airflow contacts the fins 64 uniformly and efficiently.

[0049] In some embodiments, the heat exchanger 6 includes fins 64, which include a middle fin segment 2, an upper fin segment 1, and a lower fin segment 3. For example... Figure 4As shown in (b), 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.

[0050] 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. When the upper fin segment 1 and the lower fin segment 3 are bent, it will affect the direction and flow rate 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 exchange efficiency of the fin 64.

[0051] Optionally, 1≤P1≤10. For example, P1 can be selected as 1, 2, 3, 4, 5, 6, 7, 8, 9, 10. Optionally, 1≤P2≤10. For example, P2 can be selected as 1, 2, 3, 4, 5, 6, 7, 8, 9, 10. Optionally, 1≤P3≤10. For example, P3 can be selected as 1, 2, 3, 4, 5, 6, 7, 8, 9, 10. For example, each first heat transfer unit 12 includes 2 first heat transfer structures 121. Each second heat transfer unit 13 includes 4 second heat transfer structures 131. Each third heat transfer unit 14 includes 3 third heat transfer structures 141. That is, P1 = 2, P2 = 4, P3 = 3.

[0052] Optionally, 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, as Figure 5 shown. 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.

[0053] Optionally, 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 louver structure 66, as Figure 6 shown. The louver structure 66 includes a window top wall June 27, 2023 11:24 AM 661 not 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.

[0054] 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. Wherein, 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 sidewall 652 and the fin 64 or the window top wall 661 and the fin 64, and zn5 is the spacing between adjacent bridge structures 65 or adjacent louver structures 66.

[0055] 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 height of all bridge structures 65 or louver structures 66 is within the range of zn1.

[0056] Optionally, the characteristic parameters of the first heat transfer structure 121, the second heat transfer structure 131, and the third heat transfer structure 141 may be the same or different, and / or, some or all of the characteristic parameters of the first heat transfer structure 121 may be the same or different, and / or, some or all of the characteristic parameters of the second heat transfer structure 131 may be the same or different, and / or, some or all of the characteristic parameters of the third heat transfer structure 141 may be the same or different. Figure 5 , Figure 6 and Figure 7 As shown, the characteristic parameters include zn1, zn2, zn3, zn4, and zn5.

[0057] 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 louver structure 66 corresponding to the first heat transfer structure 121, z12 is the width of the bridge structure 65 or louver structure 66 corresponding to the first heat transfer structure 121, z13 is the length of the bridge structure 65 or louver structure 66 corresponding to the first heat transfer structure 121, and z15 is the spacing between adjacent bridge structures 65 or louver structures 66 corresponding to the first heat transfer structure 121.

[0058] For example, z11 can be 0.5mm, 0.6mm, or 0.7mm. For example, z12 can be 1.6mm, 1.7mm, or 1.8mm. For example, z13 can be 3mm, 4mm, 5mm, 6mm, 7mm, 8mm, 9mm, or 10mm. For example, z14 can be 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 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; z15 = 0mm indicates that the two louver structures 66 have no gap.

[0059] Optionally, 0.5mm≤z21≤0.7mm, and / or, 1mm≤z22≤1.3mm, and / or, 5mm≤z23≤10mm, and / or, 10°≤z24≤90°, and / or, z25≤1.7mm; z21 is the height of the bridge structure 65 or louver structure 66 corresponding to the second heat transfer structure 131, z22 is the width of the bridge structure 65 or louver structure 66 corresponding to the second heat transfer structure 131, z23 is the length of the bridge structure 65 or louver structure 66 corresponding to the second heat transfer structure 131, and z25 is the spacing between adjacent bridge structures 65 or louver structures 66 corresponding to the second heat transfer structure 131.

[0060] For example, z21 can be 0.5mm, 0.6mm, or 0.7mm. For example, z22 can be 1mm, 1.2mm, or 1.3mm. For example, z23 can be 5mm, 6mm, 7mm, 8mm, 9mm, or 10mm. For example, z24 can be 10°, 20°, 30°, 45°, 60°, or 90°. When the second heat transfer structure 131 is a bridge structure 65, 1.1mm ≤ z25 ≤ 1.7mm; for example, z25 can be 1.1mm, 1.2mm, 1.4mm, 1.5mm, 1.6mm, or 1.7mm. When the second heat transfer structure 131 is a louver structure 66, 0mm ≤ z25 ≤ 1.7mm; z25 = 0mm indicates that the two louver structures 66 have no gap.

[0061] 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 adjacent bridge chip structures 65 or louver structures 66 corresponding to the third heat transfer structure 141.

[0062] For example, z31 can be selected as 0.5 mm, 0.6 mm or 0.7 mm. For example, z32 can be selected as 1.6 mm, 1.7 mm or 1.8 mm. For example, z33 can be selected as 5 mm, 6 mm, 7 mm, 8 mm, 9 mm or 10 mm. For example, z34 can be selected as 10°, 20°, 30°, 45°, 60° or 90°. When the third heat transfer structure 141 is the bridge chip structure 65, 1.1 mm ≤ z35 ≤ 1.7 mm. For example, z35 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 third heat transfer structure 141 is the louver structure 66, 0 mm ≤ z35 ≤ 1.7 mm. When z35 = 0 mm, it means that there is no gap between two louver structures 66.

[0063] Optionally, as Figure 8 shown, the air resistance coefficient of the middle fin segment 2 is f1, the air resistance coefficient of the upper fin segment 1 is f2, and the air resistance coefficient of the lower fin segment 3 is f3; where, f1 < f2, and / or, f1 < f3, and / or, f2 = f3.

[0064] In this embodiment, by optimizing the air resistance coefficients of the three fin segments, the parameter designs of different fin segments can be matched. Here, the air resistance coefficient can be determined in the following manner: f = 2F / (ρ * (v^2)), where f is the air resistance coefficient, F is the air resistance, ρ is the incoming air density, and v is the wind speed. And, the air resistance corresponding to the middle fin segment 2 is denoted as F1, and the corresponding wind speed is v1; the air resistance corresponding to the upper fin segment 1 is denoted as F2, and the corresponding wind speed is v2; the air resistance corresponding to the lower fin segment 3 is denoted as F3, and the corresponding wind speed is v3.

[0065] Since the change in air density is very small, the air density corresponding to each wing segment can be considered equal. Because the pressure difference before and after the airflow passes through each wing segment is very close, F1 = F2 = F3 can be assumed. Therefore, f ∝ 1 / (v^2), meaning 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.

[0066] Optionally, in the upper wing segment 1 or the lower wing segment 3, the drag coefficient is greater in the region farther away from the middle wing segment 2.

[0067] For example, such as Figure 9 As shown in (a), the upper wing segment 1 includes a first drag zone and a second drag zone. The first drag zone is close to the middle wing segment 2, and the second drag zone is located on the side of the first drag zone away from the middle wing segment 2. Furthermore, the drag coefficient corresponding to the first drag zone is f21, and the drag coefficient corresponding to the second drag zone is f22, and f1 < f21 < f22.

[0068] For example, such as Figure 9 (b) The lower wing segment 3 includes a third drag zone and a fourth drag zone. The third drag zone is close to the middle wing segment 2, and the fourth drag zone is located on the side of the third drag zone away from the middle wing segment 2. Furthermore, the drag coefficient corresponding to the third drag zone is f31, and the drag coefficient corresponding to the fourth drag zone is f32, and f1 < f31 < f32.

[0069] Optionally, such as Figure 4 , Figure 10 and Figure 11 As shown, the middle fin segment 2 has multiple rows of first heat exchange tube hole groups 61, and the extension direction of each row of 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 segment 2. The distance between two adjacent rows of first heat exchange tube hole groups 61 is m1. The upper fin segment 1 has multiple rows of second heat exchange tube hole groups 62, and the extension direction of each row of second heat exchange tube hole groups 62 is the same as the extension direction of the first side contour line 11 of the upper fin segment 1. The distance between two adjacent rows of second heat exchange tube hole groups 62 is m2. The lower fin segment 3 has multiple rows of third heat exchange tube hole groups 63, and the extension direction of each row of 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 segment 3. The distance between two adjacent rows of third heat exchange tube hole groups 63 is m3. The distance between adjacent first heat exchange tube holes 611 in the first heat exchange tube hole group 61 is b1, the distance between adjacent second heat exchange tube holes 621 in the second heat exchange tube hole group 62 is b2, and the distance between adjacent third heat exchange tube holes 631 in the third heat exchange tube hole group 63 is b3.

[0070] 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 through heat exchange tubes. The parameter values ​​of m1, m2, m3, b1, b2 and b3 affect the arrangement density of heat exchange tubes. By adjusting the values ​​of the above parameters, the arrangement of heat exchange tubes can be adapted to each fin segment, thereby improving the heat exchange efficiency.

[0071] Optionally, 1 ≤ m1 / m3 ≤ 1.25. For example, m1 / m3 can be selected as 1, 1.1, 1.15, 1.2 or 1.25.

[0072] Optionally, 1 ≤ m1 / m2 ≤ 1.25. For example, m1 / m2 can be selected as 1, 1.1, 1.15, 1.2 or 1.25.

[0073] Optionally, 1 ≤ m2 / m3 ≤ 1.12. For example, m1 / m3 can be 1, 1.1, 1.11, or 1.12.

[0074] 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.

[0075] Optionally, 1.05 ≤ b1 / b3 ≤ 1.25. For example, b1 / b3 can be 1.05, 1.1, 1.15, 1.2 or 1.25.

[0076] In the above embodiments, the shape of the fin 64 can be symmetrical or asymmetrical.

[0077] Optionally, such as Figure 12 As shown, the shape of fin 64 is symmetrical. The angle s1 between the first leeward profile line 111 and the horizontal direction, the angle s3 between the third leeward profile line 311 and the horizontal direction, and s1=s3; the angle s2 between the first windward profile line 112 and the horizontal direction, and the angle s4 between the third windward profile line 312 and the horizontal direction, and s2=s4. At this time, the curvature of the upper fin segment 1 is the same as the curvature of the lower fin segment 3, forming symmetry.

[0078] Optionally, such as Figure 13 As shown, the shape of fin 64 is asymmetrical. The angle between the first leeward profile line 111 and the horizontal direction is s1, the angle between the third leeward profile line 311 and the horizontal direction is s3, s1≠s3; the angle between the first windward profile line 112 and the horizontal direction is s2, the angle between the third windward profile line 312 and the horizontal direction is s4, s2≠s4. At this time, the degree of curvature of the upper fin segment 1 is different from the degree of curvature of the lower fin segment 3.

[0079] Optionally, such as Figure 14 and Figure 15 As shown, 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. Wherein, W2≥W1, and / or, W2>W3.

[0080] In this embodiment, W1 can be understood as the distance between the first windward profile line 112 and the first leeward profile line 111. W2 can be understood as the distance between the second windward profile line 212 and the second leeward profile line 211. W3 can be understood as the distance between the third windward profile line 312 and the third leeward profile line 311. W2 ≥ W1, that is, the width of the middle fin segment 2 is greater than or equal to the width of the upper fin segment 1. W2 > W3, that is, the width of the middle fin segment 2 is greater than the width of the lower fin segment 3. This is beneficial for the shape of the fins 64 to match the uneven distribution of the wind speed generated by the indoor fan 5 in the air duct, thereby improving the heat exchange efficiency of the heat exchanger 6.

[0081] Alternatively, 1≤W2 / W1≤2, and / or 1≤W2 / W3≤2.

[0082] Optionally, 1 < W2 / W1 ≤ 2, 1 < W2 / W3 ≤ 2. In this 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 effect 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 wing 64.

[0083] Based on the above embodiments of this application, compared with existing type I finned heat exchangers (heat exchangers with I-shaped side profiles of the fins) and type C finned heat exchangers (heat exchangers with C-shaped side profiles of the fins), the performance of the heat exchanger 6 and the air conditioner of this application is effectively improved. The effect comparison with the prior art is as follows.

[0084] Figure 16 This is a comparison of the velocity distribution cloud maps of heat exchanger 6 in this application and the existing type I finned heat exchanger. Among them, Figure 16 Figure a above is a velocity distribution cloud map of an existing type I finned heat exchanger. Figure 16 Figure b below is a velocity distribution cloud map of the heat exchanger 6 in various embodiments of this application.

[0085] from Figure 16 As can be seen, the Type I finned heat exchanger exhibits uneven airflow distribution, with high air velocity at the top and low air velocity at the bottom, resulting in low heat exchange efficiency. Specifically, the area with high air velocity at the top is as follows: Figure 16 As shown in the upper circle of 'a', the lower area with low wind speed is as follows: Figure 16 The lower circle of 'a' in the diagram is shown.

[0086] The heat exchanger 6 provided in this application effectively guides the incoming flow in the high-velocity zone in the middle to the upper and lower parts, resulting in a uniform overall airflow distribution. This uniform airflow distribution improves the uniformity of the heat exchange field, thus enhancing the overall heat exchange performance of the heat exchanger 6. For example... Figure 16 As shown in b in the figure.

[0087] Existing C-type finned heat exchangers have a large flow stagnation zone in the middle on the leeward side, resulting in uneven outlet air velocity distribution. Compared to existing C-type finned heat exchangers, the heat exchanger 6 provided in this embodiment effectively guides the incoming flow in the high-velocity zone in the middle to both the upper and lower parts, significantly reducing the flow stagnation zone in the middle on the leeward side and resulting in a more uniform outlet air velocity distribution. Figure 17 As shown in the velocity distribution cloud map, it can be seen that the C-type finned heat exchanger has a large flow stagnation zone in the middle of the leeward side. Figure 18 To and Figure 17 A velocity distribution contour map of the heat exchanger 6 of this application, measured at the same wind speed. From Figure 18 As can be seen, the flow stagnation zone on the leeward side of heat exchanger 6 is significantly reduced.

[0088] Figure 19 This is a pressure distribution cloud map of a C-type finned heat exchanger. Figure 20 This is a pressure distribution cloud diagram of the heat exchanger 6 provided in this embodiment. It can be measured that the pressure drop on the windward and leeward sides of the existing C-fin heat exchanger is 278 Pa, while the pressure drop on the windward and leeward sides of the heat exchanger 6 provided in this embodiment is 271 Pa. It can be seen that the pressure drop of the existing C-fin heat exchanger is relatively large. Compared with the C-fin heat exchanger, the pressure drop of the heat exchanger 6 provided in this embodiment is reduced by 2.5%.

[0089] In some embodiments, the heat exchanger 6 includes fins 64, which include an upper fin segment 1, a middle fin segment 2, and a lower fin segment 3. For example... Figure 21 As shown, the surface of the middle fin segment 2 is provided with a vortex generating unit 67 and a first heat exchange tube hole 611. The upper fin segment 1 is obliquely connected to the upper end of the middle fin segment 2. The lower fin segment 3 is obliquely connected to the lower end of the middle fin segment 2 and is located on the same side of the middle fin segment 2 as the upper fin segment 1. An angled region is formed with the center of the first heat exchange tube hole 611 as the vertex. One side of this angled region is parallel to the air inlet direction, and the opening of the angle α of this angled region faces the air inlet direction. The vortex generating unit 67 is arranged in this angled region.

[0090] In this embodiment, the vortex generating unit 67 can turbulentize the flowing air, thereby improving heat exchange efficiency. Furthermore, the layout of the vortex generating unit 67 is related to the structure of the fins 64; improper arrangement can lead to turbulent flow and significantly increased wind resistance. For the inclined three-section fins 64 of this application, the vortex generating unit 67 is placed within the included angle region. Since the included angle region matches the airflow direction, turbulence is only generated in the core included angle region around the first heat exchange tube hole 611. During the process of guiding the incoming flow from the high-velocity area in the middle of the fins 64 to the upper and lower parts, the vortex generating unit 67 positioned at the aforementioned location can provide targeted turbulence, avoiding ineffective turbulence and excessive wind resistance, improving the overall uniformity of wind speed distribution, and reducing the flow stagnation area on the leeward side of the fins 64, thereby improving the heat exchange performance of the fins 64.

[0091] Optionally, such as Figure 21 As shown, the vortex generating unit 67 includes multiple vortex generating structures 671, which enclose a right-angled triangle. One right-angled side of the right-angled triangle is parallel to the wind inlet direction, and the angle between the hypotenuse of the right-angled triangle and the wind inlet direction is β. The opening of the angle β faces the wind inlet direction, and 0.3≤α / β≤1.

[0092] In this embodiment, multiple vortex generating structures 671 enclose a right-angled triangle, with one right-angled side parallel to the airflow direction and the other right-angled side parallel to the second windward profile 212 of the central fin segment 2. For the three-segment fin 64 of this application, the right-angled triangular arrangement can generate excellent turbulence at the connection points of adjacent fin segments. Furthermore, by further defining the ratio of the included angle α to β of the hypotenuses, the turbulence range of the vortex generating unit 67 is optimized.

[0093] Optionally, the value of α / β can be 0.3, 0.4, 0.5, 0.6, 0.7, 0.8, 0.9 or 1.

[0094] Optionally, 60°≤α≤150°. For example, the value of α can be 60°, 70°, 80°, 90°, 100°, 110°, 120°, 130°, 140° or 150°.

[0095] Optionally, 100°≤β≤160°. For example, the value of β can be 100°, 110°, 120°, 130°, 140°, 150° or 160°.

[0096] Optionally, the vortex generating unit 67 includes multiple vortex generating structures 671, which enclose a right-angled triangle. For example... Figure 21As shown, the center of the first heat exchange tube hole 611 is the reference point, and the angle subtended by the hypotenuse of the right triangle corresponding to the reference point is γ, where 1 ≤ α / γ ≤ 8. This further defines the ratio of the included angle α to γ ​​of the hypotenuse, optimizing the turbulence range of the vortex generating unit 67. For example, the value of α / γ can be selected as 1, 2, 5, 6, or 8.

[0097] Optionally, 20°≤γ≤80°. For example, the value of γ can be 20°, 30°, 40°, 50°, 60°, 70° or 80°.

[0098] Optionally, the relevant parameters of the vortex generating structure 671 and the first heat exchange tube hole 611 in this application are all measured with the center of the corresponding structure as the measurement point.

[0099] Optionally, two first heat exchange tube holes 611 are provided along the second windward side contour line 212 of the middle fin segment 2. The included angle α of the included angle region corresponding to the upper first heat exchange tube hole 611 faces upward in the air inlet direction, which is used to generate turbulence at the connection between the middle fin 64 and the upper fin segment 1. The included angle α of the included angle region corresponding to the lower first heat exchange tube hole 611 faces downward in the air inlet direction, which is used to generate turbulence at the connection between the middle fin 64 and the lower fin segment 3.

[0100] Optionally, such as Figure 22 As shown, the middle fin segment 2 includes a second windward profile line 212 and a second leeward profile line 211 that are parallel to each other. The distance between the vortex generating unit 67 and the second windward profile line 212 is k1, and the distance between the vortex generating unit 67 and the second leeward profile line 211 is k2. Wherein, 0.03 ≤ k1 / k2 ≤ 0.4. Thus, by limiting the ratio of k1 to k2, the position of the vortex generating unit 67 in the width direction of the fin 64 is optimized.

[0101] Optionally, 1.5mm ≤ k1 ≤ 10mm. For example, the value of k1 can be 1.5mm, 3mm, 4.5mm, 6mm, 7.5mm, 9mm, 9.5mm or 10mm.

[0102] Optionally, 25mm ≤ k2 ≤ 40mm. For example, the value of k2 can be 25mm, 28mm, 30mm, 32mm, 35mm, 38mm or 40mm.

[0103] Optionally, such as Figure 22 As shown, multiple vortex generating units 67 are arranged along the second windward side profile 212, and the spacing between two adjacent vortex generating units 67 is k3, where 12mm≤k3≤35mm. For example, the value of k3 can be selected as 12mm, 15mm, 20mm, 25mm, 30mm or 35mm.

[0104] Optionally, multiple vortex generating units 67 are arranged along the second windward profile line 212. The distance between the uppermost vortex generating unit 67 and the upper end of the upper fin segment 1 is k4, and the distance between the lowermost vortex generating unit 67 and the lower end of the lower fin segment 3 is k5. Wherein, 0.4 ≤ k4 / k5 ≤ 1.6. Thus, by limiting the ratio of k4 to k5, the position of the vortex generating unit 67 in the height direction of the fin 64 is optimized.

[0105] Optionally, 40mm ≤ k4 ≤ 80mm. For example, the value of k4 can be 40mm, 45mm, 50mm, 55mm, 60mm, 65mm, 70mm, 75mm or 80mm.

[0106] Optionally, 50mm ≤ k5 ≤ 90mm. For example, the value of k5 can be 50mm, 55mm, 60mm, 65mm, 70mm, 75mm, 80mm, 85mm or 90mm.

[0107] In some embodiments, such as Figure 21 and 23 As shown, the heat exchanger 6 includes fins 64, which comprise an upper fin segment 1, a middle fin segment 2, and a lower fin segment 3. A vortex generating structure 671 is provided on the surface of the middle fin segment 2. The diameter of the vortex generating structure 671 is d1, and the height of the vortex generating structure 671 is n1, where 1.2 ≤ d1 / n1 ≤ 20. The upper fin segment 1 is obliquely connected to the upper end of the middle fin segment 2. The lower fin segment 3 is obliquely connected to the lower end of the middle fin segment 2 and is located on the same side of the middle fin segment 2 as the upper fin segment 1.

[0108] In this embodiment, the vortex generating structure 671 can turbulentize the flowing air, thereby improving heat exchange efficiency. For the inclined three-section fins 64 of this application, by limiting the ratio of the diameter to the height of the vortex generating structure 671, the turbulence effect of the vortex generating structure 671 is improved, thereby enhancing the heat exchange performance of the fins 64.

[0109] Optionally, the value of d1 / n1 can be 1.2, 3, 5, 7, 9, 10, 12, 15, 18 or 20.

[0110] Optionally, the vortex generating structure 671 includes a convex hull structure.

[0111] Optionally, 1mm ≤ d1 ≤ 4mm. For example, the value of d1 can be 1mm, 1.5mm, 2mm, 2.5mm, 3mm, 3.5mm or 4mm.

[0112] Optionally, 0.2mm ≤ n1 ≤ 0.8mm. For example, the value of n1 can be 0.2mm, 0.3mm, 0.4mm, 0.5mm, 0.6mm, 0.7mm or 0.8mm.

[0113] Optionally, the spacing between adjacent fins 64 is N, where 0.1 ≤ n1 / N ≤ 0.8. In this embodiment, by limiting the ratio between the height of the vortex generating structure 671 and the spacing between adjacent fins 64, it is beneficial to ensure smooth airflow between the multiple fins 64.

[0114] Optionally, the value of n1 / N can be 0.1, 0.2, 0.4, 0.6 or 0.8.

[0115] Optionally, 1mm ≤ N ≤ 1.5mm. For example, the value of N can be 1mm, 1.1mm, 1.2mm, 1.3mm, 1.4mm or 1.5mm.

[0116] Optionally, such as Figure 23 As shown, the middle fin segment 2 is also provided with a first heat exchange tube hole 611, the diameter of the first heat exchange tube hole 611 is d2, and 0.12≤d1 / d2≤0.97. In this embodiment, by limiting the ratio of the diameter of the vortex generating structure 671 to the diameter of the first heat exchange tube hole 611, it is beneficial to optimize the turbulence effect of the vortex generating structure 671.

[0117] Optionally, the value of d1 / d2 can be 0.12, 0.2, 0.4, 0.6, 0.8, 0.9 or 0.97.

[0118] Optionally, 4.2mm ≤ d2 ≤ 7.3mm. For example, the value of d2 can be 4.2mm, 4.5mm, 5mm, 5.5mm, 6mm, 6.5mm, 7mm or 7.3mm.

[0119] Optionally, multiple vortex generating structures 671 can be arranged to form a right-angled triangle, with the distance between adjacent vortex generating structures 671 on the right-angled side of the triangle being d3, where 0.1 ≤ d1 / d3 ≤ 1.8. This helps to reduce the mutual influence between adjacent vortex generating structures 671.

[0120] Optionally, the value of d1 / d3 can be 0.1, 0.5, 0.8, 1, 1.5 or 1.8.

[0121] Optionally, 2.5mm ≤ d3 ≤ 7mm. For example, the value of d3 can be 2.5mm, 3.5mm, 4.5mm, 5.5mm, 6.5mm or 7mm.

[0122] Optionally, multiple vortex generating structures 671 enclose a right-angled triangle, and a first heat exchange tube hole 611 is provided on the central fin segment 2. The distance between the hypotenuse of the right-angled triangle and the first heat exchange tube hole 611 is d4. Wherein, 3.5mm ≤ d4 ≤ 10mm. In this embodiment, the relative position of the right-angled triangle formed by the multiple vortex generating structures 671 and the first heat exchange tube hole 611 is defined by limiting the range of values ​​for d4. For example, the value of d4 can be selected as 3.5mm, 4mm, 5mm, 6mm, 7mm, 8mm, 9mm, or 10mm.

[0123] Based on the above embodiments, the arrangement of the vortex generating units 67 on the fins 64 was optimized, including the ratios and value ranges of included angles α, β, and γ, and spacing k1, k2, k3, k4, and k5. Furthermore, the relevant parameters of the vortex generating structure 671 were optimized, including the ratios and value ranges of diameter d1, height n1, and the spacing d3 between adjacent vortex generating structures 671. Thus... Figures 16 to 20 As shown, the turbulence effect of the vortex generating structure 671 is effectively improved, and in conjunction with the three-section fins 64 of this application, the overall wind speed distribution uniformity is effectively improved and the flow stagnation zone on the leeward side is reduced.

[0124] The foregoing description and accompanying drawings fully illustrate 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. Individual components and functions are optional unless explicitly required, and the order of operation may vary. Parts and features of some embodiments may be included or substituted for parts and features of other embodiments. 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 its scope. The scope of the present disclosure is limited only by the appended claims.

Claims

1. A heat exchanger with a vortex generating unit, characterized in that, Includes fins (64), which include: The middle fin segment (2) has a vortex generating unit (67) and a first heat exchange tube hole (611) on its surface; The upper wing segment (1) is obliquely connected to the upper end of the middle wing segment (2); The lower wing segment (3) is obliquely connected to the lower end of the middle wing segment (2) and is located on the same side of the middle wing segment (2) as the upper wing segment (1). An angled region is formed with the center of the first heat exchange tube hole (611) as the vertex. One side of the angled region is parallel to the air inlet direction, and the opening of the angle α of the angled region faces the air inlet direction. The vortex generating unit (67) is arranged in the angled region.

2. The heat exchanger with a vortex generating unit according to claim 1, characterized in that, The vortex generating unit (67) includes multiple vortex generating structures (671), and the multiple vortex generating structures (671) enclose a right-angled triangle; One right-angled side of the right triangle is parallel to the air inlet direction, and the angle between the hypotenuse of the right-angled triangle and the air inlet direction is β. The opening of the angle β faces the air inlet direction, and 0.3≤α / β≤1.

3. The heat exchanger with a vortex generating unit according to claim 2, characterized in that, 60°≤α≤150°; and / or, 100°≤β≤160°。 4. The heat exchanger with a vortex generating unit according to any one of claims 1 to 3, characterized in that, The vortex generating unit (67) includes multiple vortex generating structures (671), and the multiple vortex generating structures (671) enclose a right-angled triangle; The center of the first heat exchange tube hole (611) is the reference point, and the angle subtended by the hypotenuse of the right triangle corresponding to the reference point is γ, and 1≤α / γ≤8.

5. The heat exchanger with a vortex generating unit according to claim 4, characterized in that, 20°≤γ≤80°.

6. The heat exchanger with a vortex generating unit according to any one of claims 1 to 3, characterized in that, The middle wing segment (2) includes a second windward profile line (212) and a second leeward profile line (211) that are parallel to each other. The distance between the vortex generating unit (67) and the second windward profile line (212) is k1, and the distance between the vortex generating unit (67) and the second leeward profile line (211) is k2. Where 0.03≤k1 / k2≤0.

4.

7. The heat exchanger with a vortex generating unit according to claim 6, characterized in that, 1.5mm≤k1≤10mm; and / or, 25mm≤k2≤40mm.

8. The heat exchanger with a vortex generating unit according to claim 6, characterized in that, Multiple vortex generating units (67) are arranged along the second windward side profile (212), and the distance between two adjacent vortex generating units (67) is k3, 12mm≤k3≤35mm.

9. The heat exchanger with a vortex generating unit according to claim 6, characterized in that, Multiple vortex generating units (67) are arranged along the second windward side profile (212). The distance between the uppermost vortex generating unit (67) and the upper end of the upper wing segment (1) is k4, and the distance between the lowermost vortex generating unit (67) and the lower end of the lower wing segment (3) is k5. Where 0.4≤k4 / k5≤1.

6.

10. The heat exchanger with a vortex generating unit according to claim 9, characterized in that, 40mm≤k4≤80mm; and / or, 50mm≤k5≤90mm.

11. An air conditioner, characterized in that, Includes the heat exchanger as described in any one of claims 1 to 10.

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