Ducted air conditioner and air conditioner indoor unit

Abstract

A ducted air conditioner and an air conditioner indoor unit (1), which belong to the technical field of air conditioning. The ducted air conditioner comprises: a housing (10); a fan assembly (20), which is arranged in the housing (10) and is configured to drive air to flow, wherein the fan assembly (20) comprises a volute (21) covering the outside of an impeller (22); and a heat exchanger (30), which is arranged in a first direction with the fan assembly (20), wherein the heat exchanger (30) comprises heat exchange fins (32) passing through a heat exchange tube (31), and the plurality of heat exchange fins (32) are arranged in a second direction. When the heat exchange fins (32) are projected on a plane perpendicular to the second direction, the contour line thereof comprises an air inlet side contour line (321), wherein as the height decreases, the air inlet side contour line gradually approaches the direction of the volute (21), and the included angle between same and the first direction gradually decreases; and the included angle α between the normal of the air inlet side contour line (321) and the flow direction of air flowing to the heat exchanger (30) is less than or equal to 30°. The ducted air conditioner can reduce the air resistance of the heat exchanger (30).

Description

Ductless air conditioner and indoor air conditioning unit

[0001] This application claims priority to Chinese patent application No. 202510465422.4, filed on April 14, 2025; Chinese patent application No. 202510465441.7, filed on April 14, 2025; Chinese patent application No. 202520700004.4, filed on April 14, 2025; Chinese patent application No. 202520700050.4, filed on April 14, 2025; and Chinese patent application No. 202510465468.6, filed on April 14, 2025, the entire contents of which are incorporated herein by reference. Technical Field

[0002] This disclosure relates to the field of air conditioning technology, and in particular to a ducted air conditioner and an indoor air conditioning unit. Background Technology

[0003] In air conditioning systems, ducted air conditioners are a common type of indoor unit. A ducted air conditioner typically consists of a heat exchanger and a fan assembly. When the fan is operating, the airflow is directed towards the heat exchanger, where it exchanges heat before circulating back into the room, thus regulating the indoor air temperature. Usually, there is a significant angle between the airflow direction before and after entering the heat exchanger; the resistance of the heat exchanger causes this large-angle deflection of the airflow direction. Summary of the Invention

[0004] This disclosure provides a ducted air conditioner and an indoor air conditioning unit that can solve the technical problem in related technologies where the resistance of the heat exchanger forces the airflow direction to deflect at a large angle, thereby increasing the air supply resistance.

[0005] On one hand, some embodiments of this disclosure provide a ducted air conditioner, including: a fan assembly configured to drive airflow, the fan assembly including: an impeller; a volute housing covering the impeller, the volute housing having an air outlet; a heat exchanger arranged with the fan assembly along a first direction, the first direction being perpendicular to the height direction, the heat exchanger including: a heat exchange tube; heat exchange fins passing through the heat exchange tube, a plurality of heat exchange fins arranged along a second direction, the second direction being perpendicular to both the first direction and the height direction; projected onto a plane perpendicular to the second direction, the outline of the heat exchange fins includes: an air inlet side outline, which is close to the volute housing, the air inlet side outline can be divided into a first segment air inlet side outline connected sequentially from top to bottom, a second segment air inlet side outline, and a third segment air inlet side outline. The wind-side profile line and the third segment of the air-inlet side profile line; the angle γ1 between the first segment of the air-inlet side profile line and the first direction, the angle γ2 between the second segment of the air-inlet side profile line and the first direction, and the angle γ3 between the third segment of the air-inlet side profile line and the first direction, where γ1 > γ2 > γ3; where the dimension of the air-inlet side profile line in the height direction is H, A is any point on the air-inlet side profile line, and the vertical distance from A to the top of the air-inlet side profile line is H0; the dimension of the air outlet in the height direction is h, a is a point on the air outlet, and the vertical distance from a to the top of the air outlet is h0; H0 / H = h0 / h; the line connecting point A and point a is line Aa, and the angle α between the normal of the air-inlet side profile line at point A and line Aa is ≤ 30°. According to some embodiments of the ducted air conditioner provided in this disclosure, since the ratio of the vertical distance from point A to the top of the air inlet side profile to the dimension of the air inlet side profile in the height direction is equal to the ratio of the vertical distance from point a on the air outlet to the top of the air outlet to the dimension of the air outlet in the height direction, the airflow direction entering the heat exchanger at point A can be approximated by the airflow direction exiting the volute at the corresponding air outlet a. That is, line Aa can approximate the airflow direction on the windward side of the heat exchanger. Consequently, after the airflow enters the heat exchanger, it can pass through the heat exchanger along a path with less resistance, i.e., a shorter path. The airflow turning angle between the profile normal direction and the airflow direction is α. To ensure smooth airflow and low wind resistance, α can be controlled within 30°, thereby achieving the matching of the air inlet side profile of the heat exchanger with the airflow direction. Through the smooth design of the flow field, the air supply resistance is effectively reduced. Compared with heat exchangers in related technologies, the air supply resistance can be reduced by 10%; at the same time, air disturbance and air supply noise are reduced.

[0006] On the other hand, some embodiments of this disclosure provide a ducted air conditioner, including: a fan assembly configured to drive airflow, the fan assembly including: an impeller; a volute housing covering the impeller, the volute housing having an air outlet; a heat exchanger arranged with the fan assembly along a first direction, the first direction being perpendicular to the height direction, the heat exchanger including: heat exchange tubes; heat exchange fins passing through the heat exchange tubes, a plurality of heat exchange fins arranged along a second direction, the second direction being perpendicular to both the first and height directions; projected onto a plane perpendicular to the second direction, the outline of the heat exchange fins includes: The air inlet profile gradually approaches the volute as the height decreases, and the angle between it and the first direction gradually decreases. The dimension of the air inlet profile in the height direction is H, A is any point on the air inlet profile, and the vertical distance from A to the top of the air inlet profile is H0. The dimension of the air outlet in the height direction is h, a is a point on the air outlet, and the vertical distance from a to the top of the air outlet is h0. H0 / H = h0 / h. The line connecting point A and point a is line Aa, and the angle α between the normal to the air inlet profile at point A and line Aa is ≤30°. According to some embodiments of the ducted air conditioner provided in this disclosure, since the ratio of the vertical distance from point A to the top of the air inlet side profile to the dimension of the air inlet side profile in the height direction is equal to the ratio of the vertical distance from point a on the air outlet to the top of the air outlet to the dimension of the air outlet in the height direction, the airflow direction entering the heat exchanger at point A can be approximated by the airflow direction exiting the volute at the corresponding air outlet a. That is, line Aa can approximate the airflow direction on the windward side of the heat exchanger. Consequently, after the airflow enters the heat exchanger, it can pass through the heat exchanger along a path with less resistance, i.e., a shorter path. The airflow turning angle between the profile normal direction and the airflow direction is α. To ensure smooth airflow and low wind resistance, α can be controlled within 30°, thereby achieving the matching of the air inlet side profile of the heat exchanger with the airflow direction. Through the smooth design of the flow field, the air supply resistance is effectively reduced. Compared with heat exchangers in related technologies, the air supply resistance can be reduced by 10%; at the same time, air disturbance and air supply noise are reduced.

[0007] In another aspect, some embodiments of this disclosure provide an indoor unit for an air conditioner, including: a fan assembly configured to drive airflow, the fan assembly including: an impeller; a volute housing covering the impeller; and a heat exchanger arranged with the fan assembly along a first direction, the first direction being perpendicular to the height direction, with the upper middle part of the heat exchanger facing the air outlet of the volute housing in the first direction, the heat exchanger including: a heat exchange tube configured to circulate refrigerant; and heat exchange fins passing through the heat exchange tube, a plurality of heat exchange fins arranged along a second direction, the second direction being perpendicular to the height direction and perpendicular to the first direction, projected onto a plane perpendicular to the second direction, the heat exchange fins... It includes an air inlet side profile line and an air outlet side profile line extending in the same direction; wherein, the air inlet side profile line can be divided into the following segments connected from top to bottom: a first segment of the air inlet side profile line, extending along the height direction or inclined from top to bottom towards the direction of the fan assembly, the first segment of the air inlet side profile line forming an angle γ1 with the first direction; a second segment of the air inlet side profile line, inclined from top to bottom towards the direction of the fan assembly, the second segment of the air inlet side profile line forming an angle γ2 with the first direction; a third segment of the air inlet side profile line, inclined from top to bottom towards the direction of the fan assembly, the third segment of the air inlet side profile line forming an angle γ3 with the first direction, γ1 > γ2 > γ3. According to some embodiments of the air conditioning indoor unit provided in this disclosure, as the height of the first, second, and third air inlet side contour lines decreases, the inclination degree of the first, second, and third air inlet side contour lines towards the fan assembly increases sequentially. This results in a smaller turning angle between the airflow direction towards the air inlet side contour line and the airflow direction after entering the heat exchanger, thereby effectively reducing wind resistance and noise. Furthermore, due to the inclination of the air inlet side contour line and the fact that the air inlet side contour line and the air outlet side contour line extend in the same direction, the width of the heat exchange fins decreases sequentially with decreasing height. This causes the heat exchange capacity of the heat exchange fins to gradually weaken with decreasing height, which matches the wind speed at the volute air outlet, where the width is larger at the top and smaller at the bottom. This allows for full utilization of the heat exchange performance of the heat exchange fins and improves heat exchange efficiency.

[0008] In another aspect, some embodiments of this disclosure provide an indoor air conditioning unit, including: a fan assembly configured to drive airflow, the fan assembly including: an impeller; a volute housing covering the impeller; and a heat exchanger arranged with the fan assembly along a first direction, the first direction being perpendicular to the height direction, with the upper middle part of the heat exchanger facing the air outlet of the volute housing in the first direction, the heat exchanger including: a heat exchange tube configured to circulate refrigerant; and heat exchange fins passing through the heat exchange tube, a plurality of heat exchange fins arranged along a second direction, the second direction being perpendicular to the height direction and perpendicular to the first direction, projected onto a plane perpendicular to the second direction, the heat exchange fins including an inlet side profile and an outlet side profile. The air inlet side contour line, after being translated along the first direction, can coincide with the air outlet side contour line with an overlap of greater than 90%; wherein, the air inlet side contour line can be divided into the following segments connected sequentially from top to bottom: a first segment of the air inlet side contour line, extending along the height direction or inclined from top to bottom towards the direction closer to the fan assembly, with the first segment of the air inlet side contour line forming an angle γ1 with the first direction; a second segment of the air inlet side contour line, inclined from top to bottom towards the direction closer to the fan assembly, with the second segment of the air inlet side contour line forming an angle γ2 with the first direction; and a third segment of the air inlet side contour line, inclined from top to bottom towards the direction closer to the fan assembly, with the third segment of the air inlet side contour line forming an angle γ3 with the first direction, where γ1 > γ2 > γ3. According to some embodiments of the air conditioning indoor unit provided in this disclosure, as the height of the first, second, and third air inlet side contour lines decreases, the inclination degree of the first, second, and third air inlet side contour lines towards the fan assembly increases sequentially. This results in a smaller turning angle between the airflow direction towards the air inlet side contour line and the airflow direction after entering the heat exchanger, thereby effectively reducing wind resistance and noise. Furthermore, due to the inclination of the air inlet side contour line, and the fact that the air inlet side contour line can overlap with the air outlet side contour line after translation along the first direction with an overlap degree greater than 90%, the width of the heat exchange fins gradually decreases as the height decreases. This causes the heat exchange capacity of the heat exchange fins to gradually weaken as the height decreases, which matches the wind speed at the volute air outlet, where the width is larger at the top and smaller at the bottom. This allows for full utilization of the heat exchange performance of the heat exchange fins and improves heat exchange efficiency. Attached Figure Description

[0009] Figure 1 is a perspective view of an indoor air conditioner unit according to some embodiments;

[0010] Figure 2 is a cross-sectional view of an indoor air conditioning unit according to some embodiments;

[0011] Figure 3 is a side view of a heat exchanger in an indoor unit of an air conditioner according to some embodiments;

[0012] Figure 4 is a cross-sectional view of an indoor air conditioning unit in the related art;

[0013] Figure 5 is a cross-sectional view of an indoor air conditioner unit according to some embodiments;

[0014] Figure 6 is a side view of heat exchange fins in an indoor air conditioning unit according to some embodiments;

[0015] Figure 7 is a second side view of the heat exchange fins in an indoor air conditioning unit according to some embodiments;

[0016] Figure 8 is a cross-sectional view of an indoor air conditioning unit according to some embodiments;

[0017] Figure 9 is a side view of heat exchange fins in an indoor air conditioning unit according to some embodiments;

[0018] Figure 10 is a cross-sectional view of an indoor air conditioning unit according to some embodiments, omitting the heat exchanger;

[0019] Figure 11 is a wind speed-height linear graph according to some embodiments;

[0020] Figure 12 is a cross-sectional view of an indoor air conditioning unit according to some embodiments, omitting the heat exchanger;

[0021] Figure 13 is a cross-sectional view of another air conditioner indoor unit according to some embodiments;

[0022] Figure 14 is a side view of the fan assembly and heat exchanger in another air conditioning indoor unit according to some embodiments;

[0023] Figure 15 is a side view of heat exchange fins in another air conditioning indoor unit according to some embodiments;

[0024] Figure 16 is an example of heat exchange fins in another air conditioning indoor unit according to some embodiments;

[0025] Figure 17 is an example two of heat exchange fins in another air conditioning indoor unit according to some embodiments;

[0026] Figure 18 is a cross-sectional view of another air conditioner indoor unit according to some embodiments;

[0027] Figure 19 is a side view of heat exchange fins in another air conditioning indoor unit according to some embodiments;

[0028] Figure 20 is a side view of the fan assembly and heat exchanger in another air conditioning indoor unit according to some embodiments;

[0029] Figure 21 is a side view of heat exchange fins in another air conditioning indoor unit according to some embodiments;

[0030] Figure 22 is a diagram of a heat exchange enhancement assembly for an air conditioning indoor unit according to some embodiments;

[0031] Figure 23 is a front view of a heat exchange enhancement assembly for an air conditioning indoor unit according to some embodiments;

[0032] Figure 24 is an illustration according to some embodiments. and A schematic diagram illustrating the effect of the angle between the two on work efficiency;

[0033] Figure 25 is a schematic diagram of the angle between the pressure gradient direction and the air inlet direction according to some embodiments;

[0034] Figure 26 is a schematic diagram of the flow direction deflection angle Y according to some embodiments;

[0035] Figure 27 is a schematic diagram showing the change of pressure drop with the deflection angle Y of the flow direction according to some embodiments. Detailed Implementation

[0036] To make the objectives and implementation methods of this disclosure clearer, exemplary embodiments of this disclosure will be clearly and completely described below with reference to the accompanying drawings of exemplary embodiments thereof. Obviously, the described exemplary embodiments are only a part of the embodiments of this disclosure, and not all of them. In the description of this disclosure, it should be understood that the terms "center," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," and "outer," etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are generally used for the convenience of describing this disclosure and simplifying the description, and do not indicate or imply that the device or element referred to has a specific orientation, is constructed or operated in a specific orientation. Therefore, the related descriptions should not be construed as limiting this disclosure. The terms "first" and "second" are configured for descriptive purposes and should not be construed as indicating or implying relative importance or implicitly specifying the number of indicated technical features. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of this disclosure, unless otherwise stated, "a plurality of" means two or more. In the description of this disclosure, it should be noted that, unless otherwise expressly specified and limited, the terms "installation," "connection," and "linkage" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to the internal connection between two components. Those skilled in the art can understand the specific meaning of the above terms in this disclosure based on the specific circumstances.

[0037] In some embodiments, the air conditioner performs a refrigeration cycle using a compressor. In some embodiments, the air conditioner performs a refrigeration cycle using a condenser. In some embodiments, the air conditioner performs a refrigeration cycle using an expansion valve. In some embodiments, the air conditioner performs a refrigeration cycle using an evaporator. In some embodiments, the refrigeration cycle includes a series of processes involving compression, condensation, expansion, and evaporation, supplying refrigerant to regulated and heat-exchanged air. In some embodiments, the compressor compresses refrigerant gas at a low temperature and low pressure. In some embodiments, the compressor discharges the compressed refrigerant gas. In some embodiments, the discharged refrigerant gas flows into the condenser. In some embodiments, the condenser condenses the compressed refrigerant into a liquid phase. In some embodiments, heat is released to the surrounding environment through the condensation process. In some embodiments, the expansion valve expands the high-temperature, high-pressure liquid refrigerant condensed in the condenser into a low-pressure liquid refrigerant. In some embodiments, the evaporator evaporates the refrigerant expanded in the expansion valve. In some embodiments, the evaporator returns the low-temperature, low-pressure refrigerant gas to the compressor. In some embodiments, the evaporator can achieve a cooling effect by utilizing the latent heat of refrigerant evaporation to exchange heat with the material to be cooled. In some embodiments, the air conditioner can regulate the temperature of the indoor space throughout the cycle. In some embodiments, the outdoor unit of an air conditioner refers to the portion of the refrigeration cycle that includes a compressor and an outdoor heat exchanger. In some embodiments, the indoor unit of an air conditioner includes an indoor heat exchanger. In some embodiments, an expansion valve may be provided in either the indoor or outdoor unit. In some embodiments, the indoor heat exchanger is configured as a condenser or an evaporator. In some embodiments, the outdoor heat exchanger is configured as a condenser or an evaporator. In some embodiments, when the indoor heat exchanger is determined to be configured as a condenser, the air conditioner is configured as a heater in heating mode. In some embodiments, when the indoor heat exchanger is determined to be used as an evaporator, the air conditioner is configured as a cooler in cooling mode.

[0038] In some embodiments, when the outdoor unit and indoor unit of the air conditioner are a two-piece structure, the outdoor unit is also referred to as the outdoor unit. In some embodiments, when the outdoor unit and indoor unit of the air conditioner are a two-piece structure, the indoor unit is also referred to as the indoor unit. The air conditioner indoor unit 1 of this disclosure is described below with reference to the accompanying drawings: Referring to FIG1, in some embodiments, the air conditioner indoor unit 1 includes a housing 10. In some embodiments, the housing 10 is generally rectangular, forming the appearance of the air conditioner indoor unit 1. In some embodiments, the housing 10 includes a bottom plate 11 forming a bottom structure. In some embodiments, the housing 10 includes a top plate 12 forming a top structure. In some embodiments, the housing 10 includes a side plate connecting the bottom plate 11 and the top plate 12. Referring to FIG2, in some embodiments, an air outlet 10a is provided on one side plate of the housing 10. In some embodiments, an air inlet 10b is provided on the side of the housing 10 opposite to the air outlet 10a. In some embodiments, an air inlet 10b is provided on the side of the bottom plate 11 of the housing 10 away from the air outlet 10a. In some embodiments, indoor air enters the housing 10 through the air inlet 10b and returns to the indoor space through the air outlet 10a. In some embodiments, the air conditioner indoor unit 1 of this disclosure can be applied to a ducted air conditioner. In some embodiments, the air conditioner indoor unit 1 of this disclosure can be applied to a wall-mounted air conditioner. In some embodiments, the air conditioner indoor unit 1 of this disclosure can be applied to a floor-standing air conditioner. The following description takes an air conditioner indoor unit 1 that is a ducted air conditioner (air conditioner indoor unit 1) as an example: In some embodiments, the ducted air conditioner includes a fan assembly 20. In some embodiments, the fan assembly is a centrifugal fan. In some embodiments, a partition 13 may be provided inside the housing 10. In some embodiments, the partition 13 divides the space inside the housing 10 into two chambers. In some embodiments, the partition 13 divides the space inside the housing 10 into two chambers, one chamber being an air inlet chamber 141. In some embodiments, the partition 13 divides the space inside the housing 10 into two chambers, the other chamber being an air outlet chamber 142. In some embodiments, the air inlet 10b communicates with the air inlet chamber 141. In some embodiments, the air outlet 10a communicates with the air outlet chamber 142. In some embodiments, the fan assembly 20 may be disposed within the air inlet chamber 141. In some embodiments, the fan assembly may be a cross-flow fan. In some embodiments, when the fan assembly is a cross-flow fan, the partition 13 within the housing 10 may be omitted. In some embodiments, the fan assembly 20 includes a volute 21. In some embodiments, the axial direction of the volute 21 is horizontal. In some embodiments, air inlets 21a are provided on the two sides of the volute 21 perpendicular to the axis. In some embodiments, an air outlet 211 is provided on the volute 21. In some embodiments, an air outlet 21b is formed at the end of the air outlet 211. In some embodiments, the air outlet 211 is a portion extending outward from the cylindrical portion of the volute 21. In some embodiments, the partition 13 passes through the air outlet 211 of the volute 21.In some embodiments, the air outlet 21b of the volute 21 is opposite to the opening on the partition plate 13. This arrangement allows the air outlet 21b of the volute 21 to communicate with the air outlet cavity 142.

[0039] In some embodiments, the fan assembly 20 includes an impeller 22. In some embodiments, the impeller 22 is disposed within a volute 21. In some embodiments, the impeller 22 may be disposed within a cylindrical portion of the volute 21. In some embodiments, when the fan assembly 20 is in operation, the impeller 22 rotates, causing indoor air to enter the air inlet chamber 141 through the air inlet 10b. In some embodiments, indoor air flows into the volute 21 through the air intake 21a, continues to be blown towards the air outlet chamber 142 through the air outlet 21b of the volute 21, and is finally delivered to the room through the air outlet 10. In some embodiments, the ducted air conditioner includes a heat exchanger 30. In some embodiments, the heat exchanger 30 is disposed within the air outlet chamber 142. In some embodiments, the heat exchanger 30 is located in the air flow path. In some embodiments, the heat exchanger 30 is configured to exchange heat with the air passing through it. In some embodiments, the heat exchanger 30 and the fan assembly 20 are arranged along a first direction. In some embodiments, the air outlet chamber 142 and the air inlet chamber 141 are arranged along a first direction. In some embodiments, the first direction is the direction from the fan assembly 20 to the heat exchanger 30. Referring to FIG3, in some embodiments, the heat exchanger 30 may be a tube-fin structure. In some embodiments, the heat exchanger 30 has a heat exchange tube 31. In some embodiments, the heat exchanger 30 has heat exchange fins 32. In some embodiments, the heat exchange tube 31 is configured to circulate refrigerant. In some embodiments, the heat exchange fins 32 pass through the heat exchange tube 31. In some embodiments, the heat exchange fins 32 improve the heat exchange efficiency between the refrigerant and air by increasing the surface area of ​​the heat exchange tube 31. In some embodiments, the heat exchange fins 32 may be stamped from a sheet of material such as aluminum foil. In some embodiments, a plurality of heat exchange fins 32 are stacked at intervals along a second direction. In some embodiments, the second direction is a horizontal direction perpendicular to the first direction.

[0040] In some embodiments, the airflow generated by the impeller 22 flows through the outlet 21b of the volute 21 to the heat exchanger 30 under the guidance of the volute 21. In some embodiments, air flows through the gaps between the heat exchange fins 32 and exchanges heat with the refrigerant flowing in the heat exchange tubes 31. In some embodiments, air flows through the gaps between the heat exchange fins 32 and exchanges heat with the refrigerant flowing in the heat exchange tubes 31 through the heat exchange fins 32. This achieves cooling or heating of the airflow. In some embodiments, referring to FIG2, the outlet 211 of the volute 21 includes a first diffuser 212 forming the upper wall. In some embodiments, the outlet 211 of the volute 21 includes a second diffuser 213 forming the lower wall. In some embodiments, the airflow within the volute 21 flows out of the outlet 21b under the guidance of the first diffuser 212 and the second diffuser 213. In some embodiments, the airflow within the volute 21 flows out of the outlet 21b under the guidance of the first diffuser 212. In some embodiments, the airflow within the volute 21 flows out of the outlet 21b under the guidance of the second diffuser 213. In some embodiments, the direction of airflow outflow is also the direction of airflow from the inlet chamber 141 to the outlet chamber 142. In some embodiments, the second diffuser 213 is inclined downward. This increases the angle range between the first diffuser 212 and the second diffuser 213, thereby increasing the airflow range of the volute 21, and thus allowing the airflow from the outlet 21b of the volute 21 to sweep across all parts of the heat exchanger 30. In some embodiments, projected onto a plane perpendicular to the second direction, the outline of the heat exchange fins 32 includes the inlet side outline 321. In some embodiments, the inlet side outline 321 is the outline of the heat exchange fins 32 that is closest to the volute 21 and extends generally vertically. In some embodiments, the heat exchange fins 32 may include the outlet side outline 322. In some embodiments, the outlet side profile 322 is the profile of the heat exchange fins 32 that is away from the volute 32. In some embodiments, the outlet side profile 322 is also the profile of the heat exchange fins 32 that is close to the air outlet 10a of the housing 10. In some embodiments, the heat exchange fins 32 may include a top side profile 323. In some embodiments, the top end of the inlet side profile 321 and the top end of the outlet side profile 322 are connected by the top side profile 323. In some embodiments, the heat exchange fins 32 may include a bottom side profile 324. In some embodiments, the bottom end of the inlet side profile 321 and the bottom end of the outlet side profile 322 are connected by the bottom side profile 324. In some embodiments, on the main surface of the heat exchange fin 32 (the main surface being the side with the largest area on the heat exchange fin 32), the outline of the heat exchange fin 32 is formed by connecting the air inlet side outline 321, the top side outline 323, the air outlet side outline 322, and the bottom side outline 324 end to end.In some embodiments, the air outlet 21b of the volute 21 is located in the upper-middle part of the housing 10. In some embodiments, the air outlet 21b of the volute 21 is opposite to the upper-middle part of the heat exchanger 30 in a first direction. In some embodiments, along the direction of decreasing height, the airflow from the air outlet 21b to the heat exchanger 30 is inclined downwards and the angle with the first direction gradually increases. That is, as the height decreases, the degree of downward inclination of the airflow gradually increases. It should be noted that in some embodiments, the indoor air conditioning unit 1 corresponding to FIG. 2 can be used upside down. The upside down described in this disclosure is a relative concept and should not be regarded as a limitation on the scope of protection of this disclosure.

[0041] Any type of heat exchanger in the related technology will significantly impede airflow, manifested as a large angle between the airflow direction before entering the heat exchanger and the airflow direction after entering the heat exchanger. The resistance of the heat exchanger forces the airflow direction to deflect at a large angle, thereby increasing the airflow resistance. Taking the heat exchanger in Figure 4 as an example, in some embodiments, since the airflow flows in the direction of lower resistance, the airflow will pass through the heat exchanger along the path of least resistance, i.e., the shortest path, after entering the heat exchanger. In some embodiments, the direction of this shortest path is the normal direction of the air inlet side profile. In some embodiments, when the airflow enters the heat exchanger, it deflects towards the normal direction of the air inlet side profile, thereby causing a large angle deflection of the airflow direction. In some embodiments, continuing to refer to Figure 2, as the height decreases, the air inlet side profile 321 gradually extends towards the volute 21. In some embodiments, continuing to refer to Figure 2, as the height decreases, the angle γ between the air inlet side profile 321 and the first direction gradually decreases. In some embodiments, referring to Figure 2, as the height decreases, the inlet side profile 321 gradually extends towards the volute 21, and the angle γ with the first direction gradually decreases. This ensures that the angle between the airflow direction entering the heat exchanger 30 and the normal direction of the inlet side profile 321 is small, thereby reducing the air resistance at the heat exchanger 30. In some embodiments, when the inlet side profile 321 includes a curve, the angle γ between the curve and the first direction specifically refers to the angle between the tangent of the curve and the first direction. In some embodiments, "gradually" as used in this disclosure refers to an overall trend of change, which can be a continuous change or a segmented change. In a segmented change, "gradually" means a change in segments. In some embodiments, referring to Figure 5, the dimension of the inlet side profile 321 in the height direction is defined as H. In some embodiments, the dimension of the air outlet 21b of the volute 21 in the height direction is h. In some embodiments, A is any point on the inlet side profile 321. In some embodiments, the vertical distance from A to the top of the inlet side profile 321 is H0. In some embodiments, 'a' is a point on the air outlet 21b. In some embodiments, the vertical distance from 'a' to the top of the air outlet 21b is h0. In some embodiments, h0 satisfies: H0 / H = h0 / h. In some embodiments, the line connecting point A and point 'a' is line Aa. In some embodiments, line Aa can be approximated as the direction of airflow towards the heat exchanger 30. In some embodiments, the angle α between the normal direction of the air inlet side profile 321 at point A and line Aa is ≤30°. In some embodiments, the angle α between the normal direction of the air inlet side profile 321 and the airflow is the airflow turning angle.This disclosure achieves the matching of the air inlet side profile 321 of the heat exchanger 30 with the air flow direction by controlling α within 30°. Through the smooth design of the flow field, the air supply resistance can be reduced by 10% compared with heat exchangers of related technologies. At the same time, air disturbance is reduced and air supply noise is lowered.

[0042] According to some embodiments of the ducted air conditioner provided in this disclosure, since the ratio of the vertical distance from point A to the top of the air inlet side profile to the dimension of the air inlet side profile in the height direction is equal to the ratio of the vertical distance from point a on the air outlet to the top of the air outlet to the dimension of the air outlet in the height direction, the airflow direction entering the heat exchanger at point A can be approximated by the airflow direction exiting the volute at the corresponding air outlet a. That is, line Aa can approximate the airflow direction on the windward side of the heat exchanger. Consequently, after the airflow enters the heat exchanger, it can pass through the heat exchanger along a path with less resistance, i.e., a shorter path. The airflow turning angle between the profile normal direction and the airflow direction is α. To ensure smooth airflow and low wind resistance, α can be controlled within 30°, thereby achieving the matching of the air inlet side profile of the heat exchanger with the airflow direction. Through the smooth design of the flow field, the air supply resistance is effectively reduced. Compared with heat exchangers in related technologies, the air supply resistance can be reduced by 10%; at the same time, air disturbance and air supply noise are reduced.

[0043] In some embodiments, as a continuous variation, reference can be made to Figures 2 and 5-9. In some embodiments, the inlet side profile 321 is arc-shaped. In some embodiments, as a segmented variation, reference can be made to Figures 13-17. In some embodiments, the inlet side profile 321 includes at least two segments divided along the height reduction direction. In some embodiments, along the height reduction direction, the angle between each segment of the inlet side profile and the first direction decreases sequentially. In some embodiments, the inlet side profile is divided according to the wind speed: when the fan assembly 20 is operating under standard conditions, a wind speed-height diagram can be obtained by measuring or simulating the windward wind speed (incoming wind speed) of the heat exchanger 30. In some embodiments, referring to Figure 10, assuming the height of each part of the heat exchanger 30 is the horizontal axis and the wind speed U is the vertical axis, the relationship between the wind speed U and the height of each part of the heat exchanger 30 is represented as a wind speed-height linear line. In some embodiments, referring to Figure 11, in the wind speed-height linear line, the maximum wind speed Umax is located at height H3, which is close to the top of the heat exchanger 30. In some embodiments, in the wind speed-height diagram, the wind speed U gradually increases from height 0 to H3. In some embodiments, since the wind speed at height H is close to Umax, it can be concluded that the wind speed generally increases with increasing height. In some embodiments, the wind speed at the upper part of the heat exchanger 30 is greater than the wind speed at the lower part of the heat exchanger 30. In some embodiments, the wind speed at height H1 is U1 = (0.6~0.8)Uave. In some embodiments, the wind speed at height H2 is U2 = (1.2~1.4)Uave. In some embodiments, Uave is the average wind speed. In some embodiments of this disclosure, the region with a wind speed greater than U2 is called a high wind speed region. In some embodiments of this disclosure, the region with a wind speed between U1 and U2 is called a medium wind speed region. In some embodiments of this disclosure, the region with a wind speed lower than U1 is called a low wind speed region. In some embodiments, U1 = 2 m / s. In some embodiments, U2 = 6.5 m / s. In some embodiments, the wind speed in the high wind speed region is greater than 6.5 m / s. In some embodiments, the wind speed in the medium wind speed area is between 2 m / s and 6.5 m / s. In some embodiments, the wind speed in the low wind speed area is less than 2 m / s.

[0044] In some embodiments, referring to Figure 12, the first dividing line between the high-wind-speed region and the medium-wind-speed region is F1. In some embodiments, the second dividing line between the medium-wind-speed region and the low-wind-speed region is F2. In some embodiments, the first dividing line F1 of the inlet side profile is determined based on the high, medium, and low-wind-speed regions. In some embodiments, the second dividing line F2 of the inlet side profile is determined based on the high, medium, and low-wind-speed regions. In some embodiments, the distance x between the heat exchanger and the volute outlet is determined based on the heat exchanger spatial layout. In some embodiments, the angle α between the airflow direction in front of the heat exchanger and the airflow direction in the heat exchanger can be less than 30°. In some embodiments, the angle between the inlet side profile and the inlet direction can be greater than 60°. This allows the maximum depression angle and maximum elevation angle of the upper inlet side profile to be obtained. In some embodiments, the upper inlet side profile needs to be designed between these two lines. In some embodiments, the angle γ1 between the actual upper inlet side profile and the first direction is determined by comprehensively considering at least one of the following factors: outlet direction, heat exchanger depth, maximum turning angle of the airflow direction, and the trend of heat exchanger width variation. In some embodiments, after determining the upper air inlet side profile, the angles of the middle and lower air inlet side profiles are further determined downwards to obtain the overall air inlet side profile. In some embodiments, the air inlet side profile 321 includes three segments divided along the height reduction direction. In some embodiments, the first segment of the three segments divided along the height reduction direction includes a first segment air inlet side profile 321a. In some embodiments, the second segment of the three segments divided along the height reduction direction includes a second segment air inlet side profile 321b. In some embodiments, the third segment of the three segments divided along the height reduction direction includes a third segment air inlet side profile 321c. In some embodiments, the first dividing line between the first segment air inlet side profile 321a and the second segment air inlet side profile 321b is F1. In some embodiments, the second dividing line between the second segment air inlet side profile 321b and the third segment air inlet side profile 321c is F2.

[0045] In some embodiments, the first air inlet side profile line 321a is located at the upper part of the heat exchange fin 32. In some embodiments, the second air inlet side profile line 321b is located at the middle part of the heat exchange fin 32. In some embodiments, the third air inlet side profile line 321c is located at the lower part of the heat exchange fin 32. In some embodiments, the second air inlet side profile line 321b connects the first air inlet side profile line 321a and the third air inlet side profile line 321c. In some embodiments, referring to FIG14, the first defining line Q1 is a line passing through the air outlet end of the second diffuser 213 and parallel to the first direction. In some embodiments, the extension line Q2 is the extension line of the inner wall of the second diffuser 213. In some embodiments, the connection point of the second air inlet side profile line 321b and the third air inlet side profile line 321c is located between the first defining line Q1 and the line Q2. In some embodiments, the second defining line Q3 is the angle bisector of the angle between the first diffuser 212 and the second diffuser 213. In some embodiments, the third defining line Q4 is a line passing through the midpoint of the air outlet 21b and parallel to the first direction. In some embodiments, the connection point of the first air inlet side profile line 321a and the second air inlet side profile line 321b is located between the second defining line Q3 and the third defining line Q4. In some embodiments, referring to FIG15, the angles γ1 between the first air inlet side profile line 321a and the first direction, γ2 between the second air inlet side profile line 321b and the first direction, and γ3 between the third air inlet side profile line 321c and the first direction decrease sequentially. That is, γ1 > γ2 > γ3.

[0046] In some embodiments, the first air inlet side profile 321a is a straight line segment. In some embodiments, the angle γ1 between the first air inlet side profile 321a and the first direction is 70° to 90°. In some embodiments, the first air inlet side profile 321a is nearly vertical. In some embodiments, γ1 within this angle range ensures that the angle α between the normal direction of the first air inlet side profile 321a and the airflow direction is small. This ensures that the airflow direction on the windward side of the upper part of the heat exchanger 30 does not deviate significantly from the airflow direction after entering the heat exchanger 30, thereby reducing air supply resistance and noise. In some embodiments, γ1 is 85° to 90°, and the first air inlet side profile 321a is almost vertical. This allows the heat exchange fins 32 to be more compact in the first direction. In some embodiments, if γ1 is within the range of 70° to 85°, a small angle tilt of the first air inlet side profile 321a will result in an increase in the size of the heat exchange fins 32 in the first direction.

[0047] In some embodiments, the angle γ1 between the first inlet side profile 321a and the first direction is related to the relative position between the outlet 21b of the volute 21 and the heat exchanger 30. In some embodiments, the relative position between the outlet 21b of the volute 21 and the heat exchanger 30 determines the inlet direction corresponding to the inlet velocity relative to the first inlet side profile 321a. In some embodiments, the angle between the inlet direction and the pressure gradient affects the pressure's work efficiency, thereby affecting the pressure drop. In some embodiments, In some embodiments, W p It is the power output of the pressure. In some embodiments, This is the pressure gradient on the wall surface corresponding to the air inlet side profile 321. In some embodiments, This refers to the inlet air velocity corresponding to the inlet side profile 321. In some embodiments, W p When the working power corresponds to the pressure of the first section of the air intake side profile 321a, it is... It is the pressure gradient on the wall surface corresponding to the first segment of the air inlet side profile 321a in the air inlet side profile 321. This refers to the inlet air velocity corresponding to the first segment of the inlet side profile 321a in the inlet side profile 321. In some embodiments, W p When the working power corresponds to the pressure of the second section of the air inlet side profile 321b, it is... It is the pressure gradient on the wall surface corresponding to the second segment of the air inlet side profile 321b in the air inlet side profile 321. This refers to the inlet air velocity corresponding to the second segment of the inlet side profile 321b within the inlet side profile 321. In some embodiments, W p When the power output corresponds to the pressure of the third section of the air intake side profile 321c, It is the pressure gradient on the wall surface corresponding to the third segment of the air inlet side profile 321c in the air inlet side profile 321. This refers to the inlet air velocity corresponding to the third segment of the inlet side profile 321c within the inlet side profile 321. In some embodiments, and The larger the angle between the two, the more thorough the workmanship and the smaller the pressure drop. In some embodiments, and When the angle between the two is 180°, the pressure gradient does sufficient work. Since the heat exchanger 30 is the main source of pressure drop, the direction of the pressure gradient is ideally perpendicular to the inlet side profile 321. Therefore, the arrangement angle of the inlet side profile 321 should be related to the air inlet direction. In some embodiments, the angle between the normal of the first section of the inlet side profile 321a and the horizontal direction is usually between -5° and 10°. To ensure that the overall angle of the first section of the inlet side profile 321a matches the air inlet direction, the angle γ1 between the first section of the inlet side profile 321a and the first direction can be designed to be 85° to 90°. For an air inlet direction where the airflow is more downward, the angle γ1 between the first section of the inlet side profile 321a and the first direction can be 70° to 85°. In some embodiments, refer to Figure 24. and The effect of the angle between the two on the work efficiency is shown in the figure. Refer to Figure 25. and The angle between the two is shown in the figure. In some embodiments, and When the included angle θ is close to 180°, sufficient work is done. In some embodiments, as... and As the angle between the two decreases, the efficiency of work reduction decreases. In some embodiments, and When the angle between the two is greater than 170°, that is, when the angle between the inlet velocity direction and the inlet side profile 321 is greater than 80°, there is basically no additional pressure drop. In some embodiments, referring to Figures 26 and 27, for the flow channel simulation results with flow direction deflection, when the flow direction deflection angle Y is greater than 40°, the pressure drop increases rapidly. In some embodiments, limiting Y to 30° can ensure that no additional pressure drop is generated, that is, the angle γ3 between the third inlet side profile 321c and the first direction is greater than or equal to 30°.

[0048] In some embodiments, the third air inlet side profile 321c is a straight segment. In some embodiments, the third air inlet side profile 321c is inclined from top to bottom towards the air inlet side (near the fan assembly 20). In some embodiments, the angle γ3 between the third air inlet side profile 321c and the first direction is 30° to 60°. In some embodiments, within this angle range, γ3 ensures that the angle α between the normal direction of the third air inlet side profile 321c and the airflow direction is small, thereby ensuring that the airflow direction on the windward side of the lower part of the heat exchanger 30 does not deviate significantly from the airflow direction after entering the heat exchanger 30, thereby reducing air supply resistance and noise. In some embodiments, if γ3 is large, the inclination degree of the third air inlet side profile 321c is large, which will result in a relatively large size of the heat exchanger 30 in the first direction. In some embodiments, if γ3 is small, the inclination degree of the third air inlet side profile 321c is small, and its effect on reducing wind resistance will be weakened. Therefore, in some embodiments, the angle γ3 between the third air inlet side profile 321c and the first direction is 40° to 45°. Within this range, both wind resistance can be reduced and the size of the heat exchanger 30 can be kept from being too large. In some embodiments, the second air inlet side profile 321b is a straight line. In some embodiments, the angle γ2 between the second air inlet side profile 321b and the first direction is 50° to 80°. In some embodiments, γ2 within this angle range can ensure that the angle α between the normal direction of the second air inlet side profile 321b and the airflow direction is small, thereby ensuring that the airflow direction on the windward side of the middle of the heat exchanger 30 does not deviate by a large angle from the airflow direction after entering the heat exchanger 30, thereby reducing the air supply resistance. In some embodiments, the second air inlet side profile 321b is an arc segment. In some embodiments, the second air inlet side profile 321b extends from top to bottom towards the fan assembly 20. In some embodiments, the angle between the second air inlet side profile 321b and the first direction is the angle between the tangent direction of the second air inlet side profile 321b and the first direction. In some embodiments, the angle between the second air inlet side profile 321b and the first direction gradually decreases as the height decreases. In some embodiments, the second air inlet side profile 321b is tangentially connected to the first air inlet side profile 321a and the third air inlet side profile 321c, respectively. That is, the upper end of the second air inlet side profile 321b is tangent to the lower end of the first air inlet side profile 321a, and the lower end of the second air inlet side profile 321b is tangent to the upper end of the third air inlet side profile 321c. In some embodiments, the connection between the first air inlet side profile 321a and the second air inlet side profile 321b is connected by a rounded corner transition. In some embodiments, the connection between the second air inlet side profile 321b and the third air inlet side profile 321c is connected by a rounded corner transition. In some embodiments, the radius of the fillet can be between 5mm and 20mm.In some embodiments, the rounded corner design allows the air inlet side profile 321 of the heat exchange fins 32 to be smooth and flat at the corners. In some embodiments, the smooth connection of the three profile segments can reduce local wind resistance and reduce lateral disturbance and mixing of the air field. In some embodiments, the smooth connection of the three profile segments facilitates the downward flow of condensate, avoids local accumulation of condensate, and further improves the heat exchange effect. In some embodiments, when the rate of change of the incoming flow velocity Rv in the height direction of the second air inlet side profile 321b is greater than 0.1, the second air inlet side profile 321b adopts an arc segment. In some embodiments, when the rate of change of the incoming flow velocity Rv in the height direction of the second air inlet side profile 321b is less than or equal to 0.1, the second air inlet side profile 321b adopts a straight segment.

[0049] In some embodiments, V1 is the wind speed at the upper end of the second air inlet side profile 321b. In some embodiments, V2 is the wind speed at the lower end of the second air inlet side profile 321b. In some embodiments, ΔZ is the length of the second air inlet side profile 321b in the height direction. In some embodiments, if Rv > 0.1, the rate of change of wind speed is relatively large, and the second air inlet side profile 321b adopts an arc. This can, to a certain extent, avoid the generation of local vortices in the wind field and reduce local wind resistance, thereby improving heat exchange. In some embodiments, if Rv ≤ 0.1, the rate of change of wind speed is relatively small, and the second air inlet side profile 321b adopts a straight line segment. This facilitates processing and cutting, improving manufacturing efficiency. In some embodiments, in addition to considering the airflow direction, it is also necessary to consider the matching of airflow rate with the heat exchanger 30's heat exchange capacity. In some embodiments, since the upper and middle parts of the heat exchanger 30 are closer to the air outlet 21b than the lower part of the heat exchanger 30, the air velocity flowing towards the upper and middle parts of the heat exchanger 30 is greater than the air velocity flowing towards the lower part of the heat exchanger 30. In some embodiments, if the heat exchange capacity of each part of the heat exchanger 30 is the same. In some embodiments, at high air velocities, the inlet and outlet temperature difference of the heat exchanger 30 decreases due to the increase in mass flow rate, i.e., insufficient heat exchange. In some embodiments, at low air velocities, the inlet and outlet temperature difference of the heat exchanger 30 increases as the mass flow rate decreases. In some embodiments, when the air-side outlet temperature approaches the refrigerant temperature inside the pipe, the outlet temperature will no longer change, i.e., the inlet and outlet temperature difference remains essentially unchanged after approaching the upper limit, resulting in wasted heat exchange capacity. In some embodiments, the heat exchange capacity of the heat exchanger can be increased in high air velocity regions, while the heat exchange capacity can be appropriately reduced in low air velocity regions, thereby avoiding insufficient and wasted heat exchange capacity, improving the utilization efficiency of heat exchange capacity, and achieving the effect of increasing heat exchange capacity and reducing material usage.

[0050] In some embodiments, since the air velocity flowing through the upper part of the heat exchanger 30 is greater than that flowing through the lower part of the heat exchanger 30, the upper part of the heat exchanger 30 needs to have a higher local heat exchange capacity, while the lower part of the heat exchanger 30 needs to have a lower local heat exchange capacity. In some embodiments, the width W of the heat exchange fins 32 gradually decreases as the height decreases. In some embodiments, the width of the heat exchange fins 32 refers to the width of the heat exchange fins 32 in the normal direction of the air inlet side profile 321. In some embodiments, the upper part of the heat exchange fins 32 has a larger width, which can increase the heat exchange capacity of the upper part of the heat exchanger 30. In some embodiments, the lower part of the heat exchange fins 32 has a smaller width, which can avoid wasting the heat exchange capacity of the lower part of the heat exchanger 30. Therefore, in some embodiments of this disclosure, the width of the heat exchange fins 32 is set to gradually decrease as the height decreases, which can fully utilize the heat exchange capacity of the heat exchanger 30 and improve the heat exchange performance. In some embodiments, the trend of change of the air outlet side profile 322 is generally the same as that of the air inlet side profile 321, that is, the extension direction of the air outlet side profile 322 is generally the same as that of the air inlet side profile 321. In some embodiments, as the height decreases, the air outlet side profile 322 gradually extends towards the volute 21, and the angle γ with the first direction gradually decreases.

[0051] In some embodiments, the outlet side contour line 322 can be obtained by translating the inlet side contour line 321 along a first direction. In some embodiments, the overlap between the outlet side contour line 322 and the inlet side contour line 321 after translation is greater than 90%. In some embodiments, except for the top and bottom portions, the outlet side contour line 322 of the heat exchange fin 32 can overlap with the inlet side contour line 321 after translation along the first direction. In some embodiments, except for the top and bottom portions, the outlet side contour line 322 of the heat exchange fin 32 can overlap with the inlet side contour line 321 after translation along the first direction, with an overlap rate of over 90%. This configuration, on the one hand, facilitates the cutting of the heat exchange fin 32 and greatly improves processing efficiency; on the other hand, it can significantly reduce waste generated during processing, which is beneficial to reducing the initial investment in materials. In some embodiments, the bottom end of the inlet side contour line 321 and the bottom side contour line 324 are connected by an arc. In some embodiments, the top end of the air inlet side profile 321 is connected to the top side profile 323 by an arc. In some embodiments, the top end of the air outlet side profile 322 is connected to the top side profile 323 by an arc. In some embodiments, referring to FIG6, as the height decreases, the angle γ between the air inlet side profile 321 and the first direction gradually decreases. It can be seen that the angle δ between the normal direction of the air inlet side profile 321 and the first direction gradually increases. In some embodiments, since the air inlet side profile 321 and the air outlet side profile 322 have the same horizontal distance L, the larger δ is, the shorter the width, thus the width of the heat exchange fins 32 gradually decreases as the height decreases. In some embodiments, point B1 is taken on the upper part of the air inlet side profile 321. In some embodiments, point B2 is taken on the middle part of the air inlet side profile 321. In some embodiments, point B3 is taken on the lower part of the air inlet side profile 321.

[0052] In some embodiments, the width at point B1 on the heat exchange fin 32 is W1. In some embodiments, the horizontal width at point B1 on the heat exchange fin 32 is L. In some embodiments, the angle between the width direction and the horizontal width direction at point B1 on the heat exchange fin 32 is δ1. In some embodiments, the width at point B2 on the heat exchange fin 32 is W2. In some embodiments, the horizontal width at point B2 on the heat exchange fin 32 is L. In some embodiments, the angle between the width direction and the horizontal width direction at point B2 on the heat exchange fin 32 is δ2. In some embodiments, the width at point B3 on the heat exchange fin 32 is W3. In some embodiments, the horizontal width at point B3 on the heat exchange fin 32 is L. In some embodiments, the angle γ between the width direction and the horizontal width direction at point B3 on the heat exchange fin 32 is δ3. In some embodiments, since the angle γ between the tangent of the air inlet side profile 321 at points B1, B2, and B3 and the horizontal width direction decreases sequentially, it can be known that δ1 < δ2 < δ3, thus W1 > W2 > W3. Therefore, in some embodiments, the outlet side profile 322 is obtained by translating the inlet side profile 321 along a first direction, which can achieve a form where the upper part of the heat exchange fins 32 is wider and the lower part is narrower. This setting matches the trend of wind speed variation from top to bottom, thereby improving the heat exchange capacity of the upper part of the heat exchanger 30 and avoiding the waste of heat exchange capacity at the bottom of the heat exchanger 30. In some embodiments, the upper part of the heat exchange fins 32 is located in the high wind speed region. In some embodiments, the middle part of the heat exchange fins 32 is located in the medium wind speed region. In some embodiments, the lower part of the heat exchange fins 32 is located in the low wind speed region. In some embodiments, the width of the lower part of the heat exchange fins 32 is reduced by 10% to 30% compared to the average width. In some embodiments, the width of the upper part of the heat exchange fins 32 is increased by 10% to 30% compared to the average width. In some embodiments, the average width = heat exchange area of ​​the heat exchange fins / length of the inlet side profile 321.

[0053] This configuration allows the width variation of the heat exchange fins 32 to match the high, medium, and low wind speed zones. In some embodiments, the heat exchanger 30 in the high wind speed zone is wider. In some embodiments, the heat exchanger 30 in the low wind speed zone is narrower. This configuration improves the heat exchange capacity of the upper part of the heat exchanger 30 while avoiding waste of heat exchange capacity at the bottom of the heat exchanger 30. In some embodiments, referring to FIG15, the heat exchange fins 32 include a first fin portion 32a located above the first dividing line F1. In some embodiments, referring to FIG15, the heat exchange fins 32 include a second fin portion 32b located between the first dividing line F1 and the second dividing line F2. In some embodiments, referring to FIG15, the heat exchange fins 32 include a third fin portion 32c located below the second dividing line F2. In some embodiments, the first fin portion 32a is located at the upper part. In some embodiments, the second fin portion 32b is located in the middle part. In some embodiments, the third fin portion 32c is located at the lower part. In some embodiments, the widths of the first fin portion 32a, the second fin portion 32b, and the third fin portion 32c decrease sequentially. In some embodiments, the width of the first fin portion 32a is W1. In some embodiments, the width of the second fin portion 32b is W2. In some embodiments, the width of the third fin portion 32c is W3. In some embodiments, W1 > W2 > W3. In some embodiments, the air velocity flowing through the first fin portion 32a is greater than the air velocity flowing through the second fin portion 32b. In some embodiments, the air velocity flowing through the second fin portion 32b is greater than the air velocity flowing through the third fin portion 32c. In some embodiments, the upper width of the heat exchange fin 32 is larger than the lower width, matching the trend of the air velocity being larger at the top and smaller at the bottom. This allows for increased heat exchange capacity of the heat exchanger 32 in high-speed regions and appropriately reduced heat exchange capacity in low-speed regions, avoiding insufficient and wasted heat exchange capacity, improving the utilization efficiency of heat exchange capacity, and achieving the effect of increasing capacity or reducing material usage. Therefore, some embodiments of this disclosure can improve the heat exchange capacity of the heat exchange fins by 32 unit area, while reducing unnecessary fin material consumption and space occupation.

[0054] According to some embodiments of this disclosure, the angle between the first fin portion 32a and the first direction is γ1. According to some embodiments of this disclosure, the angle between the second fin portion 32b and the first direction is γ2. According to some embodiments of this disclosure, the angle between the third fin portion 32c and the first direction is γ3. In some embodiments, the horizontal width of the heat exchange fins 32 along the first direction is between 35mm and 55mm. In some embodiments, within this width range, both the heat exchange capacity and air resistance of the heat exchanger 30 can be balanced. In some embodiments, if the width of the heat exchange fins 32 is larger, the heat exchange capacity will be better, but the air resistance generated by the heat exchanger 30 will be larger. In some embodiments, if the width of the heat exchange fins 32 is smaller, although the air resistance generated by the heat exchanger 30 is smaller, its heat exchange capacity will not be guaranteed. In some embodiments, the width W1 of the first fin portion 32a is 10% to 30% larger than the average width of the heat exchange fins 32. In some embodiments, the airflow velocity in the first fin portion 32a is relatively high. In some embodiments, the width W1 of the first fin portion 32a is larger than the average width of the heat exchange fins 32. This improves the heat exchange capacity of the upper part of the heat exchanger 32. In some embodiments, the width W3 of the third fin portion 32c is reduced by 10% to 30% compared to the average width of the heat exchange fins 32. In some embodiments, the airflow velocity in the third fin portion 32c is lower. In some embodiments, the width W3 of the third fin portion 32a is smaller than the average width of the heat exchange fins 32. This reduces the heat exchange capacity of the lower part of the heat exchange fins 32, reduces the amount of aluminum foil material used, and avoids wasting the heat exchange capacity of the lower part of the heat exchange fins 32.

[0055] In some embodiments, the first air inlet side profile 321a is vertically arranged, i.e., γ1 = 90°. In some embodiments, the second air inlet side profile 321b forms an angle γ2 = 65° with the first direction. In some embodiments, the third air inlet side profile 321c forms an angle γ3 = 50° with the first direction. In some embodiments, the horizontal width of the heat exchange fin 32 is 45 mm. In some embodiments, the width W1 of the first fin portion 32a is 45 mm. In some embodiments, the width W2 of the second fin portion 32b is 40.5 mm. In some embodiments, the width W3 of the third fin portion 32c is 34.5 mm. In some embodiments, the average width of the heat exchange fin 32 is 39.5 mm. In some embodiments, the width of the first fin portion 32a is 14% greater than the average width. In some embodiments, the width of the third fin portion 32c is 13% less than the average width. In some embodiments, referring to FIG8, the first diffuser portion 212 is inclined downward β1 relative to the first direction. In some embodiments, β1 = 0° to 5°. In some embodiments, the first diffuser 212 is slightly tilted downward by β1, which causes the airflow at the top of the outlet 21b to tilt slightly downward, avoiding the direct airflow from the top onto the heat exchange fins 32 and thus preventing significant wind resistance. In some embodiments, projected onto a plane perpendicular to the second direction, the inner extension line of the first diffuser 212 is LP1, and the angle between LP1 and the first direction is β1. In some embodiments, when β1 is small, the portion of the heat exchanger 30 located above LP1 is smaller. This ensures that the wind speed at the top of the heat exchanger 30 is not significantly different from the maximum wind speed flowing through the heat exchanger 30, thus guaranteeing a relatively high wind speed at the top of the heat exchanger 30.

[0056] In some embodiments, if β1 is large, the portion of heat exchanger 30 located above LP1 is larger. Therefore, the air velocity at the top of heat exchanger 30 is significantly reduced compared to the maximum air velocity flowing through heat exchanger 30. In some embodiments, given a fixed top width of heat exchanger 30, a decrease in air velocity can lead to wasted heat exchange capacity. In this case, if the width of the top of heat exchanger 30 is reduced to avoid waste, the heat exchange fins 32 can be configured as shown in Figure 9, which increases the processing difficulty of the heat exchange fins 32. In some embodiments, the second diffuser 213 is inclined downwards by β2 relative to the first direction. In some embodiments, β2 = 16° to 45°. Within this angle range, the uniformity of airflow velocity can be ensured as much as possible. In some embodiments, the included angle θ between the extension lines of the first diffuser 212 and the second diffuser 213 is 15° to 40°, which can ensure the air outlet range. In some embodiments, unlike the above embodiments, referring to Figures 18 to 21, the first section of the air inlet side contour line 321a is curved. This allows the upper part of the heat exchange fins 32 to be curved, thereby increasing the heat exchange area of ​​the upper part of the heat exchange fins 32 and improving the heat exchange capacity of the upper part of the heat exchange fins 32. In some embodiments, the first section of the air inlet side profile 321a is V-shaped. In some embodiments, the opening end of the V-shape faces the air inlet side. In some embodiments, the third section of the air inlet side profile 321c is inclined from top to bottom towards the direction close to the fan assembly 20. In some embodiments, the angle between the third section of the air inlet side profile 321c and the first direction is γ3. In some embodiments, γ3 = 45° to 60°. In some embodiments, the second section of the air inlet side profile 321b can be a straight line segment perpendicular to the first direction. That is, the second section of the air inlet side profile 321b extends along the height direction. In some embodiments, the air outlet side profile can be consistent with the extension direction of the air inlet side profile. In some embodiments, the first fin portion 32a of the upper part of the heat exchange fins 32 is V-shaped. In some embodiments, the second fin portion 32b in the middle of the heat exchange fins 32 extends along the height direction. In some embodiments, the third fin portion 32c at the lower part of the heat exchange fin 32 is inclined from top to bottom toward the direction of the fan assembly 20.

[0057] In some embodiments of this disclosure, the width of the heat exchange fin 32 is wider in the middle and narrower at the top and bottom. In some embodiments, since the upper part of the heat exchange fin 32 is V-shaped, the heat exchange area of ​​the upper part of the heat exchange fin 32 is increased, which can improve the heat exchange capacity of the upper part of the heat exchange fin 32. In some embodiments, the width of the third fin portion 32c is narrower, which reduces the heat exchange performance of the lower part of the heat exchange fin 32 and avoids wasting the heat exchange capacity of the lower part of the heat exchange fin 32. Therefore, some embodiments of this disclosure ensure the area of ​​the area with a large air volume on the heat exchange fin 32 and reduce the area of ​​the area with a small air volume, which is beneficial to improving the utilization rate of the heat exchange fin 32, enhancing the heat exchange performance, saving energy consumption, and reducing material waste in the area with a small air volume, which is beneficial to reducing material costs. In some embodiments, the first section of the air inlet side contour line 321a includes a V-shaped contour line segment one and a contour line segment two. In some embodiments, the contour line segment one is located below the contour line segment two. In some embodiments, the angle γ1 between the contour segment and the first direction is 15-30°. In some embodiments, within a certain height range, the smaller the V-angle, the larger the area of ​​the heat exchange fin 32. In some embodiments, within this value range, γ1 maximizes the heat exchange area while ensuring a reasonable pressure drop. In some embodiments, referring to Figures 18 and 19, the centerline of the heat exchange fin 32 parallel to the first direction is Lp3, and the distance from line Lp3 to the top of the heat exchange fin 32 is the same as the distance from line Lp3 to the bottom of the heat exchange fin 32. In some embodiments, the midpoint of the line segment ST where line Lp3 intersects the heat exchange fin 32 is O.

[0058] In some embodiments, the distance from point P on the windward side of the heat exchange fin 32 in the first direction to point O is R. In some embodiments, R is the vertical distance from the air outlet 21b of the fan assembly 20 to point O. In some embodiments, the distance from the endpoints of the first air inlet side profile 321a, the second air inlet side profile 321b, and the third air inlet side profile 321c to point P is Ri. In some embodiments, 0.8 ≤ Ri / R ≤ 1.2. In some embodiments, the top endpoint of the first air inlet side profile 321a is denoted as A. In some embodiments, the bottom endpoint of the first air inlet side profile 321a is denoted as B. In some embodiments, the top endpoint of the third air inlet side profile 321c is denoted as C. In some embodiments, the bottom endpoint of the third air inlet side profile 321c is denoted as D. In some embodiments, the length of the line connecting point P to point A is R1. In some embodiments, the length of the line connecting point P to point B is R2. In some embodiments, the length of the line connecting point P to point C is R3. In some embodiments, the length of the line connecting point P to point D is R4. In some embodiments, 0.8 ≤ R1 / R ≤ 1.2. In some embodiments, 0.8 ≤ R2 / R ≤ 1.2. In some embodiments, 0.8 ≤ R3 / R ≤ 1.2. In some embodiments, 0.8 ≤ R4 / R ≤ 1.2. In some embodiments, if 0.8 > Ri / R, then the position of Ri corresponding to the heat exchange fin 32 is too close to the air outlet 21b of the fan assembly 20. The airflow from the air outlet 21b will directly impact the heat exchange fin 32, resulting in uneven airflow distribution, increased system pressure drop, and poor local heat exchange effect on the heat exchange fin 32. In some embodiments, i = 1, 0.8 > R1 / R, then the top of the heat exchange fin 32 is too close to the air outlet 21b. In some embodiments, i = 4, then the bottom of the heat exchange fin 32 is too close to the air outlet 21b.

[0059] In some embodiments, 0.8 ≤ Ri / R ensures that the air inlet side of the heat exchange fin 32 is not too close to the air outlet 21b of the fan assembly 20, thereby improving the uniformity of airflow distribution on the heat exchange fin 32 and ensuring the heat exchange effect of each part of the heat exchange fin 32. In some embodiments, if Ri / R > 1.2, the air inlet side of the heat exchange fin 32 is too far from the air outlet 21b of the fan assembly 20, and the airflow from the air outlet 21b will attenuate before reaching the heat exchange fin 32, reducing the heat exchange efficiency. In some embodiments, 0.8 ≤ Ri / R ≤ 1.2, within this range, it can prevent the air inlet side of the heat exchange fin 32 from being too close or too far from the air outlet 21b of the fan assembly 20. In some embodiments, referring to FIG20, the angle between the inner extension lines of the first diffuser 212 and the second diffuser 213 is θ. In some embodiments, the angle between the first diffuser 212 and the first direction is β1. In some embodiments, the endpoint of the inner contour line of the first diffuser 212 at the air outlet 21b is E. In some embodiments, the endpoint of the inner contour line of the second diffuser 213 at the air outlet 21b is F. In some embodiments, the intersection point of the extension lines of the first diffuser 212 and the second diffuser 213 is J. In some embodiments, the foot of the perpendicular from point J to the air outlet 21b is point K. In some embodiments, the length of line segment JF is L2. In some embodiments, the length of line segment JK is L1. In some embodiments, the length of line segment KF is L. KF .

[0060] In some embodiments, 0.8 ≤ R / L KF ≤1.2. In some embodiments, if 0.8 > R / L KF The distance between the heat exchange fins 32 and the air outlet 21b of the fan assembly 20 is too short. The airflow from the outlet 21b does not have sufficient space to distribute evenly before reaching the heat exchange fins 32, resulting in uneven airflow distribution across the fins and poor heat exchange performance in localized areas. In some embodiments, 0.8 ≤ R / L KF This ensures that the distance between the heat exchange fins 32 and the air outlet 21b of the fan assembly 20 is not too close, and that the airflow from the air outlet 21b has sufficient space to be evenly distributed before reaching the heat exchanger 30, thus guaranteeing the heat exchange effect of each part of the heat exchange fins 32. In some embodiments, if R / L KF >1.2, the distance from the heat exchange fins 32 to the air outlet 21b of the fan assembly 20 is too far, resulting in severe attenuation of the airflow at the air outlet 21b, which will affect the heat exchange efficiency between the airflow and the heat exchange fins 32. In some embodiments, R / L KF≤1.2, the distance from the heat exchange fins 32 to the air outlet 21b of the fan assembly 20 will not be too far, and the airflow from the air outlet 21b can quickly reach the heat exchange fins 32, ensuring heat exchange efficiency. In some embodiments, the length h of the air outlet 21b of the fan assembly 20 in the height direction satisfies:

[0061] In some embodiments, the height dimension of the air outlet 21b of the fan assembly 20 is h. In some embodiments, the height dimension of the heat exchange fins 32 is H. In some embodiments, 0.4 ≤ h / H ≤ 0.6. In some embodiments, if 0.4 > h / H, then the ratio of the height dimension h of the air outlet 21b of the fan assembly 20 to the height dimension H of the heat exchange fins 32 is small. In some embodiments, under the condition that the height dimension h of the air outlet 21b of the fan assembly 20 is constant, the height dimension H of the heat exchange fins 32 is relatively large, and the overall heat exchange area of ​​the heat exchange fins 32 is relatively large, which can meet the unit's requirements for the heat exchange efficiency of the heat exchange fins 32. However, with a large height dimension H of the heat exchange fins 32, the airflow blown from the air outlet 21b needs a longer time to spread to the upper and lower ends of the heat exchange fins 32, resulting in the upper and lower ends of the heat exchange fins 32 not being fully utilized, leading to a waste of the heat exchange performance of the heat exchange fins 32. The large height dimension H of the heat exchange fins 32 will result in an increased size of the unit in the height direction. In installation situations with limited ceiling space, the unit will not be able to be installed and used, thus limiting its application. In addition, the larger size of the unit will also increase material costs.

[0062] In some embodiments, if 0.4 ≤ h / H, then the ratio of the height dimension h of the air outlet 21b of the fan assembly 20 to the height dimension H of the heat exchange fins 32 will not be too small. In some embodiments, given a fixed height dimension h of the air outlet 21b of the fan assembly 20, the height dimension H of the heat exchange fins 32 will not be too high. Therefore, the unit can be applied to a wider range of applications, and its structural dimensions are more compact, reducing costs. In some embodiments, if h / H > 0.6, then the ratio of the height dimension h of the air outlet 21b of the fan assembly 20 to the height dimension H of the heat exchange fins 32 is larger. In some embodiments, given a fixed height dimension h of the air outlet 21b of the fan assembly 20, a smaller height dimension H of the heat exchange fins 32 results in a smaller overall heat exchange area, leading to slower heat exchange efficiency and failing to meet users' needs for rapid cooling / heating. In some embodiments, h / H ≤ 0.6, so the ratio of the height dimension h of the air outlet 21b of the fan assembly 20 to the height dimension H of the heat exchange fins 32 will not be too large. In some embodiments, under the condition that the height dimension h of the air outlet 21b of the fan assembly 20 is constant, the height dimension H of the heat exchange fins 32 will not be too small, so that the heat exchange area of ​​the heat exchange fins 32 can meet the user's requirements for the cooling / heating rate. In some embodiments, 0.4 ≤ h / H ≤ 0.6, the ratio of the height dimension h of the air outlet 21b of the fan assembly 20 to the height dimension H of the heat exchange fins 32 is within this range. This allows the unit to have a relatively compact structure while meeting the unit's requirements for the heat exchange efficiency of the heat exchange fins 32. In some embodiments, the height dimension h of the air outlet 21b of the fan assembly 20 satisfies: 80mm ≤ h ≤ 100mm. In some embodiments, the height dimension H of the heat exchange fins 32 satisfies: 160mm ≤ H ≤ 180mm. In some embodiments, referring to FIG20, the minimum vertical distance Lm from the heat exchange fins 32 to the air outlet 21b satisfies:

[0063] In some embodiments, the closest point on the heat exchange fin 32 to the air outlet 21b is the bottom end of the heat exchange fin 32. In some embodiments, if the distance between the bottom end of the heat exchange fin 32 and the air outlet 21b is too close, the airflow from the air outlet 21b will not reach the bottom of the heat exchange fin 32, resulting in the bottom of the heat exchange fin 32 not being fully utilized. In some embodiments, if the distance between the bottom end of the heat exchange fin 32 and the air outlet 21b is too far, the tilt angle of the lower part of the heat exchange fin 32 relative to its height is relatively small, and the effect of reducing wind resistance will be weakened.

[0064] In some embodiments, referring to Figure 14, the minimum vertical distance Lm from the heat exchange fins 32 to the air outlet 21b satisfies:

[0065] In the above formula, Uave is the average wind speed of the airflow on the heat exchange fins 32, 15°≤θ≤20°. In some embodiments, the size of Lm greatly affects the heat exchange effect. In some embodiments, if Lm is too small, that is, the heat exchanger 30 is too close to the air outlet 21b of the fan assembly 20, the airflow at the air outlet 21b will pass through the heat exchanger 30 before it has a chance to spread upwards and downwards, resulting in insufficient heat exchange between the heat exchange fins 32 and the supply air, and problems such as excessive local wind speed, high wind resistance, and high noise. In some embodiments, if Lm is too large, that is, the heat exchanger 30 is too far from the air outlet 21b of the fan assembly 20, it will result in an excessively large unit size, material waste, and is not conducive to the installation and use of the unit in space-constrained situations. Therefore, some embodiments of this disclosure calculate Lm according to the above formula, so that Lm is within a reasonable size range, which can ensure sufficient heat exchange between the heat exchange fins 32 and the supply air, and can also avoid an excessively large unit size. In some embodiments, the minimum distance Lm from the air outlet 21b of the fan assembly 20 to the heat exchange fins 32 satisfies: 70mm ≤ Lm ≤ 110mm. In some embodiments, the minimum distance Lm from the air outlet 21b of the fan assembly 20 to the heat exchange fins 32 in the first direction is 0.7 ≤ h / Lm ≤ 1.4. In some embodiments, if 0.7 > h / Lm, then the ratio of the height h of the air outlet 21b of the fan assembly 20 to the minimum distance Lm from the air outlet 21b to the heat exchange fins 32 is small. In some embodiments, under the condition that the height h of the air outlet 21b of the fan assembly 20 is constant, if the minimum distance Lm from the air outlet 21b to the heat exchanger 30 is large, then the heat exchanger 30 is far from the air outlet 21b, which will result in a larger unit size in the first direction, an excessively large unit volume, and material waste. In some embodiments, if 0.7 ≤ h / Lm, then the ratio of the height h of the air outlet 21b of the fan assembly 20 to the minimum distance Lm from the air outlet 21b to the heat exchange fins 32 will not be too small. In some embodiments, under the condition that the height h of the air outlet 21b of the fan assembly 20 is constant, the minimum distance Lm from the air outlet 21b to the heat exchange fins 32 will not be too large, and the unit will be relatively compact in the first direction, reducing material costs. In some embodiments, if h / Lm > 1.4, the ratio of the height h of the air outlet 21b of the fan assembly 20 to the minimum distance Lm from the air outlet 21b to the heat exchange fins 32 will be relatively large. In some embodiments, under the condition that the height h of the air outlet 21b of the fan assembly 20 is fixed, the minimum distance Lm from the air outlet 21b to the heat exchange fins 32 is small. In this case, the heat exchange fins 32 are relatively close to the air outlet 21b, which will cause the airflow at the air outlet 21b to pass through the heat exchange fins 32 before it has a chance to spread to the upper and lower sides. This results in insufficient heat exchange between the heat exchange fins 32 and the air supply, as well as problems such as excessive local wind speed, high wind resistance, and high noise.In some embodiments, h / Lm ≤ 1.4, ensuring that the ratio of the height h of the air outlet 21b of the fan assembly 20 to the minimum distance Lm from the air outlet 21b to the heat exchanger 30 is not too large. In some embodiments, given a fixed height h of the air outlet 21b of the fan assembly 20, the minimum distance Lm from the air outlet 21b to the heat exchange fins 32 is not too small, allowing the airflow from the air outlet 21b to pass through all parts of the heat exchange fins 32, thereby fully utilizing the heat exchange fins 32, ensuring heat exchange efficiency at the heat exchange fins 32, and providing a relatively uniform airflow velocity after passing through the heat exchange fins 32, reducing wind resistance and noise. In some embodiments, 0.7 ≤ h / Lm ≤ 1.4, ensuring that the unit structure is relatively compact while allowing the heat exchange fins 32 to be fully utilized, guaranteeing heat exchange efficiency, and reducing wind resistance and noise.

[0066] <Arrangement of 325mm bore>

[0067] In some embodiments, referring to Figures 16, 17, and 21, the heat exchange fins 32 are provided with through holes 325 extending along the thickness direction (second direction) of the heat exchange fins 32 for the heat exchange tubes 31 to pass through. In some embodiments, referring to Figures 16 and 17, the widths W1 of the first fin portion 32a, W2 of the second fin portion 32b, and W3 of the third fin portion 32c decrease sequentially, i.e., W1 > W2 > W3. In some embodiments, the number of through holes 325 per unit area on the first fin portion 32a is greater than the number of through holes 325 per unit area on the second fin portion 32b. In some embodiments, the number of through holes 325 per unit area on the first fin portion 32a is greater than the number of through holes 325 per unit area on the third fin portion 32c. In some embodiments, the density of through holes 325 on the first fin portion 32a is greater than the density of through holes 325 on the second fin portion 32b. In some embodiments, the density of the tube holes 325 on the first fin portion 32a is greater than the density of the tube holes 325 on the third fin portion 32c. In some embodiments, a denser arrangement of the tube holes 325 indicates a denser arrangement of the heat exchange tubes 31 and a stronger heat exchange capacity. In some embodiments, a higher density of the tube holes 325 on the first fin portion 32a can increase the heat exchange capacity of that portion. In some embodiments, the airflow distribution of the incoming airflow field of the heat exchange fins 32 is "larger at the top and smaller at the bottom." Because the heat exchange tubes 31 on the first fin portion 32a are arranged more densely, the possibility and impact of excessive airflow at the top of the heat exchange fins 32 can be reduced, thereby improving the heat exchange efficiency of the heat exchange fins 32. In some embodiments, referring to FIG16, the number of tube holes 325 on the first fin portion 32a, the number of tube holes 325 on the second fin portion 32b, and the number of tube holes 325 on the third fin portion 32c decrease sequentially. In some embodiments, the number of tube holes 325 on the first fin portion 32a is greater than the number of tube holes 325 on the second fin portion 32b. In some embodiments, the number of tube holes 325 on the second fin portion 32b is greater than the number of tube holes 325 on the third fin portion 32c. In some embodiments, the number of tube holes 325 in the upper part of the heat exchange fin 32 is greater than the number of tube holes 325 in the middle part of the heat exchange fin 32. In some embodiments, the number of tube holes 325 in the middle part of the heat exchange fin 32 is greater than the number of tube holes 325 in the lower part of the heat exchange fin 32. In some embodiments, the number of tube holes 325 in the upper, middle, and lower parts of the heat exchange fin 32 is 11.5, 10.5, and 10, respectively. In some embodiments, the trend of more tube holes 325 at the top and fewer at the bottom on the heat exchange fin 32 matches the trend of higher wind speed at the top and lower wind speed at the bottom, which can fully utilize the heat exchange capacity of the heat exchanger 30 and avoid wasting heat exchange capacity.

[0068] In some embodiments, referring to FIG16, the first fin portion 32a has n rows of tube holes 325. In some embodiments, the second fin portion 32b has a mixture of n rows and n-1 rows of tube holes 325. In some embodiments, the third fin portion 32c has n-1 rows of tube holes 325. In some embodiments, the first fin portion 32a has a larger number of rows of tube holes 325, making the tube holes 325 of the first fin portion 32a more dense. In some embodiments, the third fin portion 32c has a smaller number of rows of tube holes 325, making the tube holes 325 of the third fin portion 32c more sparse. In some embodiments, the first fin portion 32a has three rows of tube holes 325. In some embodiments, the second fin portion 32b has a mixture of three rows and two rows of tube holes 325. In some embodiments, the third fin portion 32c has two rows of tube holes 325. In some embodiments, referring to FIG17, the heat exchange fin 32 is provided with multiple rows of tube holes 325 arranged along a first direction. In some embodiments, the heat exchange fins 32 are provided with two rows of pipe holes 325. In some embodiments, one row of pipe holes 325 can be translated in a first direction to coincide with the other row of pipe holes 325.

[0069] In some embodiments, referring to FIG17, on the first fin portion 32a, any two adjacent pipe holes 325 in the same row of pipe holes 325 constitute a pipe hole group, and there exists at least one pipe hole group in which the line connecting the centers of two pipe holes 325 makes an angle λ with the first section of air inlet side contour line 321a. In some embodiments, λ is not greater than 50°. In this way, the pipe holes 325 can be arranged more densely in the height direction, and the heat exchange between the heat exchange tubes 31 passing through adjacent pipe holes 325 does not affect each other.

[0070] In some embodiments, when the length of the connecting line between adjacent holes 325 in the same row is the same, the connecting line forms an angle λ with the first air inlet side profile 321a. This reduces the length of the two holes 325 in the extension direction of the first air inlet side profile 321a, thereby allowing more holes 325 to be arranged in the vertical direction and increasing the density of the hole arrangement. In some embodiments, as shown in FIG17, if the holes 325 are arranged along the extension direction (height direction) of the first air inlet side profile 321a on the first fin portion 32a, four holes 325 can be arranged under the same interval conditions. However, if holes ① and ③, holes ⑤ and ⑦, and holes ⑦ and ⑨ are arranged at an angle λ relative to the height direction, five holes 325 can be arranged.

[0071] In some embodiments, 20°≤λ≤50°. If λ is too small, it is impossible to achieve the vertical arrangement of multiple pipe holes 325 on the first fin portion 32a. In some embodiments, referring to FIG17, the changing trend of the center line connecting the same row of pipe holes 325 on the second fin portion 32b is generally the same as the changing trend of the second air inlet side profile line 321b. This can effectively avoid air mixing, disturbance, and local vortices perpendicular to the incoming flow direction, thereby reducing wind resistance and noise. In some embodiments, the center line connecting the same row of pipe holes 325 on the second fin portion 32b can be generally parallel to the second air inlet side profile line 321b.

[0072] In some embodiments, referring to FIG17, the changing trend of the center line connecting the same row of pipe holes 325 on the third fin portion 32c is substantially the same as the changing trend of the third section air inlet side profile line 321c. This can effectively avoid air mixing, disturbance, and local vortices perpendicular to the incoming flow direction, thereby reducing wind resistance and noise. In some embodiments, the center line connecting the same row of pipe holes 325 on the third fin portion 32c may be substantially parallel to the third section air inlet side profile line 321c. In some embodiments, referring to FIG17, taking any of the same row of pipe holes 325 as the target pipe hole, the reference line Lp4 is the line of the air inlet side profile line 321b translated along the first direction and close to the target pipe hole. In some embodiments, the center of the target pipe hole on the second fin portion 32b and the third fin portion 32c is located on the reference line Lp4. In some embodiments, the center of the target pipe hole on the second fin portion 32b and the third fin portion 32c is distributed near the reference line Lp4. In some embodiments, the distance from the center of the target hole on the second fin portion 32b and the third fin portion 32c to the reference line Lp4 is not greater than the radius of the hole 325. In some embodiments, the line connecting the centers of the same row of holes 325 on the second fin portion 32b is inclined from top to bottom towards the fan assembly 20, and the angle between the line connecting the centers and the height direction is δ2. In some embodiments, the line connecting the centers of the same row of holes 325 on the third fin portion 32c is inclined from top to bottom towards the fan assembly 20, and the angle between the line connecting the centers and the height direction is δ3. In some embodiments, δ3 > δ2. In some embodiments, the line connecting the centers of the same row of holes 325 on the second fin portion 32b is substantially parallel to its corresponding air inlet side profile, which can effectively avoid air mixing, disturbance, and local vortices perpendicular to the incoming flow direction, thereby reducing wind resistance and noise. In some embodiments, the line connecting the center of the same row of pipe holes 325 in the third fin portion 32c is substantially parallel to its corresponding air inlet side profile, which can effectively avoid air mixing, disturbance and local vortex perpendicular to the incoming flow direction, thereby reducing wind resistance and noise.

[0073] In some embodiments, referring to FIG21, the number of tube holes 325 on the first fin portion 32a is greater than the number of tube holes 325 on the third fin portion 32c. In some embodiments, the number of tube holes 325 on the first fin portion 32a is 12. In some embodiments, the number of tube holes 325 on the third fin portion 32c is 10. In some embodiments, a larger number of tube holes 325 on the first fin portion 32a can increase the heat exchange capacity of the first fin portion 32a. In some embodiments, referring to FIG21, on the second fin portion 32b, any two adjacent tube holes 325 in the same row of tube holes 325 constitute a tube hole group, and there exists at least one tube hole group in which the line connecting the centers of two tube holes 325 makes an angle λ with the second air inlet side contour line 321b (height direction). In some embodiments, λ is not greater than 50°. In this way, the tube holes 325 are arranged more densely in the height direction, and the heat exchange between adjacent heat exchange tubes 31 does not affect each other. In some embodiments, since the second fin portion 32b has a larger width, more tube holes 325 can be arranged on the second fin portion 32 to improve the heat exchange effect of the second fin portion 32.

[0074] In some embodiments, referring to FIG21, the centers of the target tube holes on the first fin portion 32a and the third fin portion 32c are located on reference line Lp4. In some embodiments, the centers of the target tube holes on the first fin portion 32a and the third fin portion 32c are distributed near reference line Lp4. In some embodiments, the distance from the center of the target tube hole on the first fin portion 32a and the third fin portion 32c to reference line Lp4 is not greater than the radius of the tube hole 325. In some embodiments, referring to FIG17, the center distance between adjacent tube holes 325 in the same row is b, and the center distance between tube holes 325 in different rows in the first direction is a. In some embodiments, a > b. In some embodiments, b ≥ 13 mm. In some embodiments, a ≥ 15 mm. This avoids heat exchange interference between adjacent heat exchange tubes 31. In some embodiments, b ≤ 20 mm. In some embodiments, a ≤ 22 mm. This allows more tube holes 325 to be arranged within a certain space. In some embodiments, a = 18-20 mm. In some embodiments, b = 13-15 mm. This ensures that the arrangement of the tube holes 325 is relatively dense and avoids heat exchange interference between adjacent heat exchange tubes 31.

[0075] <Heat Exchange Enhancement Section 326>

[0076] In some embodiments, referring to Figures 16, 17, 19, 21, and 22, the heat exchange fins 32 are provided with a plurality of heat exchange reinforcement portions 326. In some embodiments, the heat exchange reinforcement portions 326 can improve the heat transfer coefficient and enhance the heat transfer capacity of the heat exchange fins 32. In some embodiments, the heat exchange fins 32 are provided with openings. In some embodiments, the heat exchange reinforcement portions 326 are correspondingly connected to the openings of the heat exchange fins 32. In some embodiments, the heat exchange reinforcement portions 326 include two bent sidewalls 3261 that bend from the edges of the openings toward the thickness direction of the heat exchange fins 32. In some embodiments, the two bent sidewalls 3261 are disposed opposite to each other.

[0077] In some embodiments, the heat exchange reinforcement 326 includes a connecting wall 3262 bridging the two bent sidewalls 3261, such that the heat exchange reinforcement 326 resembles a bridge on the heat exchange fins 32. In some embodiments, the connecting wall 3262 connects to the ends of the two bent sidewalls 3262 that are away from the heat exchange fins 32. In some embodiments, referring to Figures 16, 17, and 21, the heat exchange reinforcement 326 may be disposed between two adjacent tube holes 325 in the same row. In some embodiments, the longitudinal direction of the heat exchange reinforcement 326 is substantially parallel to the line connecting the centers of its two adjacent tube holes 325. In some embodiments, the longitudinal direction of the heat exchange reinforcement 326 is the arrangement direction of the two bent sidewalls 3261. In some embodiments, the heat exchange reinforcement 326 may be disposed below the bottommost tube hole 325 on the heat exchange fins 32.

[0078] In some embodiments, Pipe and A heat exchange reinforcement section 326 is provided on the lower side of the pipe hole. In some embodiments, the length direction of the heat exchange reinforcement section 326 at the lowermost end of the heat exchange fin 32 is substantially parallel to the air outlet side profile line 322 corresponding to the first direction. In some embodiments, the heat exchange reinforcement section 326 is not provided at the bottom of the heat exchange fin 32. In some embodiments, Pipe and The lower side of the pipe hole is not provided with a heat exchange reinforcement section 326. In some embodiments, since the bottom of the heat exchanger 30 is in the lowest wind speed zone, this part does not require strong heat exchange capacity, therefore, the heat exchange reinforcement section 326 may not be provided in this part. In addition, in some embodiments, the absence of a heat exchange reinforcement section 326 at the bottom can improve the drainage capacity of the heat exchanger 30 and avoid the heat exchange reinforcement section 326 obstructing the downward flow of condensate on the heat exchanger 30. In some embodiments, the connection line between the heat exchange reinforcement section 326 and the heat exchange fin 32 is an arc. In some embodiments, the center of the arc coincides with the center of the adjacent pipe hole 325. In some embodiments, the connection line between the upper end of the heat exchange reinforcement section 326 and the heat exchange fin 32 is a first arc. In some embodiments, the center of the first arc coincides with the center of the adjacent upper pipe hole 325. In some embodiments, the connection line between the lower end of the heat exchange reinforcement section 326 and the heat exchange fin 32 is a second arc. In some embodiments, the center of the second arc coincides with the center of the adjacent lower tube hole 325. In some embodiments, the minimum distance between the edge of the heat exchange reinforcement 326 and the edge of the tube hole 325 is not less than 0.3 mm, which can prevent the heat exchange reinforcement 326 from being too close to the tube hole 325 and thus increasing local wind resistance. In some embodiments, the radius of the first arc and / or the radius of the second arc are controlled to be greater than 4 mm. In some embodiments, taking any tube hole 325 as a reference target, the heat exchange reinforcement 326 located below and adjacent to the tube hole 325 constitutes a heat exchange reinforcement group. In some embodiments, each heat exchange reinforcement group may include multiple heat exchange reinforcement 326. In some embodiments, the multiple heat exchange reinforcement 326 are arranged along the width direction of the heat exchange reinforcement 326. In some embodiments, the width direction of the heat exchange reinforcement 326 is perpendicular to its length direction. In some embodiments, in the same heat exchange reinforcement group, the connecting wall 3262 of two adjacent heat exchange reinforcement 326 are respectively located on both sides of the heat exchange fin 32. In some embodiments, the bending directions of the bent sidewalls 3261 of two adjacent heat exchange reinforcement sections 326 are opposite. This allows for sufficient contact with air, enhancing local airflow disturbance near the heat exchange tube 31 and thus increasing heat exchange capacity. In some embodiments, the number of heat exchange reinforcement sections 326 in the first fin portion 32a is greater than the number of heat exchange reinforcement sections 326 in the third fin portion 32c. This improves the heat exchange capacity of the first fin portion 32a through the heat exchange reinforcement sections 326, avoiding waste of airflow in the upper part of the heat exchanger 30. Simultaneously, the degree to which the heat exchange reinforcement sections 326 enhance the heat exchange capacity of the third fin portion 32c is less than the degree to which they enhance the heat exchange capacity of the first fin portion 32a, thus avoiding waste of heat exchange capacity in the third fin portion 32c.

[0079] In some embodiments, the number of heat exchange reinforcement sections 326 in the first fin portion 32a, the second fin portion 32b, and the third fin portion 32c decreases sequentially. This results in a progressively decreasing degree of improvement in the heat exchange capacity of the heat exchange reinforcement sections 326 on the first fin portion 32a, the second fin portion 32b, and the third fin portion 32c, matching the wind speed flow field with a larger upper section and a smaller lower section, thus improving the heat exchange capacity of the heat exchange fins 32 while avoiding waste of heat exchange capacity. In some embodiments, each heat exchange reinforcement group on the first fin portion 32a has m1 heat exchange reinforcement sections 326. In some embodiments, each heat exchange reinforcement group on the second fin portion 32b has m2 heat exchange reinforcement sections 326. In some embodiments, each heat exchange reinforcement group on the third fin portion 32c has m3 heat exchange reinforcement sections 326. In some embodiments, m1 > m2 > m3. In some embodiments, m1 = 4. In some embodiments, m2 = 3. In some embodiments, m3 = 2. In some embodiments, the area near the junction of the first fin portion 32a and the second fin portion 32b is a bend region. In some embodiments, the area near the junction of the second fin portion 32b and the third fin portion 32c is a bend region. In some embodiments, the bottom of the third fin portion 32c is a bottom region. In some embodiments, the areas on the heat exchange fin 32 other than the bend region and the bottom region are the main body region. In some embodiments, the number of heat exchange reinforcement portions 326 in the heat exchange reinforcement group in the bend region is less than the number of heat exchange reinforcement portions 326 in the heat exchange reinforcement group in the main body region. In some embodiments, when the dividing line (first dividing line F1 and / or second dividing line F2) passes through the tube hole 325, the number of heat exchange reinforcement portions 326 adjacent to the lower side of the dividing line is less than the number of heat exchange reinforcement portions 326 in the heat exchange reinforcement group in the main body region. In some embodiments, referring to FIG17, the first dividing line F1 passes through Pipe and Pipe hole. In some embodiments, Pipe and Two heat exchange reinforcement sections 326 are provided between the tube holes. In some embodiments, Pipe and The heat exchange reinforcement group between the pipe holes has two heat exchange reinforcement sections 326. In some embodiments, the heat exchange reinforcement group in the main body region has four heat exchange reinforcement sections 326. In some embodiments, when the dividing line passes through the heat exchange reinforcement group, the number of heat exchange reinforcement sections 326 in the heat exchange reinforcement group adjacent to the lower side of the dividing line is less than the number of heat exchange reinforcement sections 326 in the heat exchange reinforcement group in the main body region. In some embodiments, referring to FIG17, the second dividing line F2 passes through... Pipe and The heat exchange enhancement group between the tube holes, and after Pipe and Enhanced heat exchange assembly between the tube holes. In some embodiments, Pipe and The heat exchange reinforcement assembly between the tube holes has two heat exchange reinforcement sections 326. In some embodiments, Pipe and The heat exchange reinforcement group between the tube holes has two heat exchange reinforcement sections 326. In some embodiments, the heat exchange reinforcement group in the main body region has four heat exchange reinforcement sections 326.

[0080] In some embodiments, when the dividing line passes through a heat exchange reinforcement group, the number of heat exchange reinforcement sections 326 within the heat exchange reinforcement group through which the dividing line passes is less than the number of heat exchange reinforcement sections 326 within the heat exchange reinforcement group of the main body region. In some embodiments, referring to FIG21, the first dividing line F1 passes through... Pipe and The heat exchange enhancement group between the tube holes, and after Pipe and Enhanced heat exchange assembly between the tube holes. In some embodiments, Pipe and The heat exchange reinforcement assembly between the tube holes has two heat exchange reinforcement sections 326. In some embodiments, Pipe and The heat exchange reinforcement assembly between the tube holes has two heat exchange reinforcement sections 326. In some embodiments, the second dividing line F2 passes through... Pipe and The heat exchange enhancement group between the tube holes, and after Pipe and Enhanced heat exchange assembly between the tube holes. In some embodiments, Pipe and The heat exchange reinforcement assembly between the tube holes has two heat exchange reinforcement sections 326. In some embodiments, Pipe and The heat exchange reinforcement group between the tube holes has two heat exchange reinforcement sections 326. In some embodiments, the positions near the connection between the first fin portion 32a and the second fin portion 32b, or near the connection between the second fin portion 32b and the third fin portion 32c, generally correspond to the bends of the air inlet side profile line 321 in the first direction. In some embodiments, since the local wind resistance at the bends of the air inlet side profile line 321 is relatively large and the heat exchange effect is poor, reducing the number of heat exchange reinforcement sections 326 at these positions can reduce the pressure drop of the airflow passing through the heat exchange fins 32 and reduce noise. In some embodiments, the number of heat exchange reinforcement sections 326 in the heat exchange reinforcement group in the bottom region of the heat exchange fins 32 is less than the number of heat exchange reinforcement sections 326 in the heat exchange reinforcement group in the main body region. In some embodiments, the number of heat exchange reinforcement sections 326 in the heat exchange reinforcement groups on both sides of the tube hole 325 at the bottom end of the heat exchange fins 32 is less than the number of heat exchange reinforcement sections 326 in the heat exchange reinforcement group in the main body region. In some embodiments, refer to FIG17. The heat exchange reinforcement assemblies on the upper and lower sides of the tube hole have two heat exchange reinforcement sections 326. In some embodiments, The heat exchange reinforcement assemblies on the upper and lower sides of the tube hole have two heat exchange reinforcement sections 326. In some embodiments, referring to FIG21, The heat exchange reinforcement assemblies on the upper and lower sides of the tube hole have two heat exchange reinforcement sections 326. In some embodiments, The heat exchange reinforcement assemblies on the upper and lower sides of the tube hole have two heat exchange reinforcement sections 326. In some embodiments, the air volume at the bottom of the heat exchange fins 32 is relatively small and does not require a large heat exchange capacity. Reducing the number of heat exchange reinforcement sections 326 at this location can reduce the pressure drop of the airflow passing through the heat exchange fins 32 and reduce noise.

[0081] In some embodiments, referring to Figures 22 and 23, the length n of the heat exchange reinforcement portion 326 is (4.5–8) mm. In some embodiments, the width n3 of the heat exchange reinforcement portion 326 is (1.1–1.3) mm. In some embodiments, the heat exchange reinforcement group includes four heat exchange reinforcement portions 326. In some embodiments, the length n1 of the long side of the heat exchange reinforcement portion 326 is (6–8) mm. In some embodiments, the length n2 of the short side of the heat exchange reinforcement portion 326 is (4.5–6.5) mm. In some embodiments, in the second direction, the distance t from the connecting wall 3262 of the heat exchange reinforcement portion 326 to the heat exchange fin 32 is (0.5–0.65) mm. That is, the heat exchange reinforcement portion 326 protrudes from the heat exchange fin 32 by a distance t. In some embodiments, the distance t1 by which the heat exchange reinforcement portion 326 protrudes from the heat exchange fin 32 on the first fin portion 32a, the distance t2 by which the heat exchange reinforcement portion 326 protrudes from the heat exchange fin 32 on the second fin portion 32b, and the distance t3 by which the heat exchange reinforcement portion 326 protrudes from the heat exchange fin 32 on the third fin portion 32c decreases sequentially. In some embodiments, t1 > t2 > t3. In some embodiments, the greater the wind speed, the greater the distance by which the heat exchange reinforcement portion 326 protrudes from the heat exchange fin 32, which can maximize the heat exchange capacity of the heat exchange fin 32 while maintaining a reasonable pressure drop. Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of some embodiments of this disclosure, and are not intended to limit them; although some embodiments of this disclosure have been described in detail with reference to the foregoing embodiments, those skilled in the art should understand that modifications can still be made to the technical solutions described in the foregoing embodiments, or equivalent substitutions can be made to some or all of the technical features; and these modifications or substitutions do not cause the essence of the corresponding technical solutions to deviate from the scope of the technical solutions of some embodiments of this disclosure.

[0082] For ease of explanation, the above description has been provided in conjunction with specific embodiments. However, the above exemplary discussion is not intended to be exhaustive or to limit the embodiments to the specific forms disclosed above. Various modifications and variations can be obtained based on the above teachings. The selection and description of the above embodiments are for the purpose of better explaining the principles and practical applications, thereby enabling those skilled in the art to better utilize the described embodiments and various different variations of embodiments suitable for specific use considerations.

Claims

1. A ducted air conditioner, wherein, include: A fan assembly, configured to drive an airflow, includes: impeller; A volute is provided to cover the impeller, and the volute has an air outlet; A heat exchanger, arranged along a first direction perpendicular to the height direction, is provided with the fan assembly. The heat exchanger includes: The heat exchange tubes are configured to allow refrigerant to circulate. Heat exchange fins are inserted into heat exchange tubes, and a plurality of heat exchange fins are arranged along a second direction, which is perpendicular to the first direction and perpendicular to the height direction; projected onto a plane perpendicular to the second direction, the outline of the heat exchange fins includes: The air inlet side profile line can be divided into a first air inlet side profile line, a second air inlet side profile line, and a third air inlet side profile line connected sequentially from top to bottom; the first air inlet side profile line has an angle γ1 with the first direction, the second air inlet side profile line has an angle γ2 with the first direction, and the third air inlet side profile line has an angle γ3 with the first direction, where γ1 > γ2 > γ3. Wherein, the dimension of the air inlet side profile in the height direction is H, A is any point on the air inlet side profile, and the vertical distance from A to the top of the air inlet side profile is H0; the dimension of the air outlet in the height direction is h, a is a point on the air outlet, and the vertical distance from a to the top of the air outlet is h0; H0 / H=h0 / h; the line connecting point A and point a is line Aa, and the angle α between the normal of the air inlet side profile at point A and line Aa is ≤30°.

2. The duct air handling unit according to claim 1, wherein, γ1=70°~90°, γ2=50°~80°, γ3=30°~50°.

3. The duct air handling unit according to claim 1, wherein, The first and third air inlet side contour lines are straight lines, while the second air inlet side contour line is either an arc or a straight line.

4. The duct air handling unit according to claim 1, wherein, The outline of the heat exchange fins includes the outline of the air outlet side; After the air inlet side contour line is translated along the first direction, it can coincide with the air outlet side contour line, and the degree of coincidence is greater than 90%.

5. The duct air handling unit according to claim 1, wherein, The heat exchange fins include a first fin portion, a second fin portion, and a third fin portion connected sequentially along a height decreasing direction; the first air inlet side profile is located on the first fin portion, the second air inlet side profile is located on the second fin portion, and the third air inlet side profile is located on the third fin portion; the widths of the first fin portion, the second fin portion, and the third fin portion decrease sequentially.

6. The duct air handling unit according to claim 5, wherein, When the fan assembly is running, the wind speed at the connection between the first fin and the second fin is (1.2~1.4) Uave, and the wind speed at the connection between the second fin and the third fin is (0.6~0.8) Uave; where Uave is the average wind speed of the airflow at the heat exchange fins. The width of the first fin portion is 10% to 30% greater than the average width of the heat exchange fins, and the width of the third fin portion is 10% to 30% less than the average width of the heat exchange fins.

7. The duct air handling unit according to claim 5, wherein, The heat exchange fins are provided with tube holes, which are configured to allow the heat exchange tubes to pass through. The density of the tube holes in the first fin portion is greater than the density of the tube holes in the third fin portion.

8. The duct air handling unit according to claim 5, wherein, The heat exchange fins are provided with tube holes, which are configured to allow the heat exchange tubes to pass through. A heat exchange reinforcement section is provided between two adjacent tube holes, and the number of heat exchange reinforcement sections in the first fin section is greater than the number of heat exchange reinforcement sections in the third fin section.

9. A ducted air conditioner, wherein, include: A fan assembly, configured to drive an airflow, includes: impeller; A volute is provided to cover the impeller, and the volute has an air outlet; A heat exchanger, arranged along a first direction perpendicular to the height direction, is provided with the fan assembly. The heat exchanger includes: The heat exchange tubes are configured to allow refrigerant to circulate. Heat exchange fins are inserted into heat exchange tubes, and a plurality of heat exchange fins are arranged along a second direction, which is perpendicular to the first direction and perpendicular to the height direction; projected onto a plane perpendicular to the second direction, the outline of the heat exchange fins includes: The air intake side profile line gradually moves closer to the direction of the volute as the height decreases, and the angle between it and the first direction gradually decreases. Wherein, the dimension of the air inlet side profile in the height direction is H, A is any point on the air inlet side profile, and the vertical distance from A to the top of the air inlet side profile is H0; the dimension of the air outlet in the height direction is h, a is a point on the air outlet, and the vertical distance from a to the top of the air outlet is h0; H0 / H=h0 / h; the line connecting point A and point a is line Aa, and the angle α between the normal of the air inlet side profile at point A and line Aa is ≤30°.

10. The duct air handling unit according to claim 9, wherein, As the height decreases, the width of the heat exchange fins gradually becomes smaller.

11. An indoor unit for an air conditioner, wherein, include: A fan assembly, configured to drive an airflow, includes: impeller; A volute is installed over the impeller; A heat exchanger, arranged along a first direction perpendicular to the height direction, wherein the upper middle part of the heat exchanger is opposite the air outlet of the volute in the first direction, the heat exchanger comprising: The heat exchange tubes are configured to allow refrigerant to circulate. Heat exchange fins are inserted into heat exchange tubes. Multiple heat exchange fins are arranged along a second direction, which is perpendicular to the height direction and perpendicular to the first direction. The projection on a plane perpendicular to the second direction is described. The heat exchange fins include an inlet side profile line and an outlet side profile line with the same extension direction. The air inlet side contour line can be divided into sections connected sequentially from top to bottom: The first section of the air inlet side profile extends along the height direction or slopes from top to bottom toward the direction of the fan assembly, and the first section of the air inlet side profile makes an angle γ1 with the first direction. The second section of the air inlet side profile line is inclined from top to bottom towards the direction of the fan assembly, and the angle γ2 between the second section of the air inlet side profile line and the first direction is γ2. The third air inlet side profile line is inclined from top to bottom towards the direction of the fan assembly, and the angle γ3 between the third air inlet side profile line and the first direction is γ1>γ2>γ3.

12. The indoor unit of the air conditioner according to claim 11, wherein, When the fan assembly is running, the wind speed at the junction of the first air inlet side profile and the second air inlet side profile is (1.2~1.4)Uave, and the wind speed at the junction of the second air inlet side profile and the third air inlet side profile is (0.6~0.8)Uave; where Uave is the average wind speed of the airflow towards the heat exchange fins.

13. The indoor unit of the air conditioner according to claim 11 or 12, wherein, γ1=70°~90°, γ2=50°~80°, γ3=30°~60°.

14. The indoor unit of the air conditioner according to claim 12, wherein, When the rate of change of wind speed on the second air intake side profile is Rv > 0.1, the second air intake side profile is an arc; when Rv ≤ 0.1, the second air intake side profile is a straight line. in, V1 is the wind speed at the upper end of the second air inlet side profile, V2 is the wind speed at the lower end of the second air inlet side profile, and △Z is the length of the second air inlet side profile in the height direction.

15. The indoor unit of the air conditioner according to claim 11, wherein, The volute includes a first diffuser and a second diffuser that are positioned opposite each other. The angle between the first diffuser and the first direction is β1, the angle between the first diffuser and the second diffuser is θ, the length of the air outlet of the volute in the height direction is h, the length of the heat exchange fins in the height direction is H, and the minimum vertical distance from the heat exchange fins to the air outlet of the volute is Lm. Uave is the average airflow velocity towards the heat exchange fins when the fan assembly is operating under standard conditions.

16. The indoor unit of the air conditioner according to claim 15, wherein, 15°≤θ≤20°, 0°≤β1≤5°.

17. The indoor unit of the air conditioner according to claim 11, wherein, The minimum vertical distance Lm from the heat exchange fins to the air outlet of the volute and the length h of the air outlet of the volute in the height direction satisfy: 0.7≤h / Lm≤1.

4.

18. The indoor unit of the air conditioner according to claim 11, wherein, The length of the air outlet of the volute in the vertical direction is h, and the length of the heat exchange fins in the vertical direction is H, where 0.4≤h / H≤0.

6.

19. The indoor unit of the air conditioner according to claim 11, wherein, The heat exchange fins can be divided into a first fin section, a second fin section, and a third fin section connected sequentially from top to bottom. The first section of the air inlet side profile is the air inlet side profile of the first fin section, the second section of the air inlet side profile is the air inlet side profile of the second fin section, and the third section of the air inlet side profile is the air inlet side profile of the third fin section. The heat exchange fins are provided with multiple tube holes, which are configured to pass through the heat exchange tubes; the density of tube holes on the first fin portion is greater than the density of tube holes on the third fin portion.

20. An indoor unit for an air conditioner, wherein, include: A fan assembly, configured to drive an airflow, includes: impeller; A volute is installed over the impeller; A heat exchanger, arranged along a first direction perpendicular to the height direction, wherein the upper middle part of the heat exchanger is opposite the air outlet of the volute in the first direction, the heat exchanger comprising: The heat exchange tubes are configured to allow refrigerant to circulate. Heat exchange fins are inserted into heat exchange tubes. Multiple heat exchange fins are arranged along a second direction, which is perpendicular to the height direction and perpendicular to the first direction. The projection on a plane perpendicular to the second direction is described. The heat exchange fins include an air inlet side profile line and an air outlet side profile line. The air inlet side profile line can be superimposed on the air outlet side profile line after translation along the first direction, and the degree of superposition is greater than 90%. The air inlet side contour line can be divided into sections connected sequentially from top to bottom: The first section of the air inlet side profile extends along the height direction or slopes from top to bottom toward the direction of the fan assembly, and the first section of the air inlet side profile makes an angle γ1 with the first direction. The second section of the air inlet side profile line is inclined from top to bottom towards the direction of the fan assembly, and the angle γ2 between the second section of the air inlet side profile line and the first direction is γ2. The third air inlet side profile line is inclined from top to bottom towards the direction of the fan assembly, and the angle γ3 between the third air inlet side profile line and the first direction is γ1>γ2>γ3.

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