Outdoor heat exchanger, outdoor unit and air conditioner

Abstract

This utility model provides an outdoor heat exchanger, an outdoor unit, and an air conditioner. The outdoor heat exchanger has a first flat plate area and includes an outer fin group and an inner fin group. The outer fin group includes multiple first fins distributed along a first straight line in the first flat plate area, and the inner fin group includes multiple second fins distributed along the first straight line in the first flat plate area. Within the first flat plate area, there is a first fin spacing between adjacent first fins and a second fin spacing between adjacent second fins. The first fin spacing is 1.5 to 3 times the second fin spacing. The outdoor unit is equipped with the above-mentioned outdoor heat exchanger, and the air conditioner includes the above-mentioned outdoor unit. The outdoor heat exchanger can extend the heating time, reduce the number of defrosting cycles, and reduce indoor temperature fluctuations during heating.

Description

Technical Field

[0001] This utility model relates to the field of air conditioning technology, specifically to an outdoor heat exchanger, an outdoor unit equipped with the outdoor heat exchanger, and an air conditioner equipped with the outdoor unit. Background Technology

[0002] Existing outdoor units typically have an outdoor heat exchanger consisting of an outer fin assembly (windward side) and an inner fin assembly (leeward side). Because the spacing between the first fins of the outer fin assembly is equal to the spacing between the second fins of the inner fin assembly, during winter heating operation, as the outdoor ambient temperature decreases and relative humidity increases, and the outdoor ambient temperature approaches 0°C, the outer fin assembly will accumulate significant frost. This frost hinders heat exchange between the fins and the air, reducing or even blocking the airflow of the outdoor heat exchanger. Conversely, there is no noticeable frost buildup on the inner fin assembly. This reduced or blocked airflow prevents the outdoor heat exchanger from being fully utilized, consequently reducing the air conditioner's heating capacity.

[0003] To maintain continuous heating, air conditioners must initiate a defrosting process once the outdoor heat exchanger has reached a certain level of frost buildup. This involves briefly switching from heating mode to cooling mode via a four-way valve to defrost the outdoor heat exchanger. Once defrosted, the four-way valve switches back to heating mode. However, frequent defrosting not only reduces the air conditioner's heating efficiency and causes indoor temperature fluctuations, but also increases energy consumption and shortens the lifespan of critical components such as the four-way valve and compressor. Summary of the Invention

[0004] The primary objective of this invention is to provide an outdoor heat exchanger that can extend heating time, reduce defrosting frequency, and decrease indoor temperature fluctuations during heating.

[0005] The second objective of this invention is to provide an outdoor unit that can extend heating time, reduce defrosting frequency, and reduce indoor temperature fluctuations during heating.

[0006] The third objective of this invention is to provide an air conditioner that can extend heating time, reduce the number of defrosting cycles, and reduce indoor temperature fluctuations during heating.

[0007] To achieve the first objective of this utility model, this utility model provides an outdoor heat exchanger having a first flat plate area. The outdoor heat exchanger includes an outer fin group and an inner fin group. The outer fin group includes multiple first fins distributed along a first straight line in the first flat plate area. The inner fin group includes multiple second fins distributed along the first straight line in the first flat plate area. In the first flat plate area, there is a first fin spacing between two adjacent first fins and a second fin spacing between two adjacent second fins. The first fin spacing is 1.5 to 3 times the second fin spacing.

[0008] As can be seen from the above, in heating mode, the outer fin assembly frosts quickly because it is located on the windward side. By increasing the fin spacing between the first fins, the time for frost bridges to form between the first fins is significantly extended, and the difficulty of frost bridge formation is increased. This allows the outer fin assembly to maintain ventilation for a longer period after frost formation, ensuring that sufficient humid air can continuously penetrate to the inner fin assembly on the leeward side before frost bridges form between the first fins, and condense and frost on the inner fin assembly, achieving two dehumidification and cooling processes and fully utilizing the function of the inner fin assembly. By designing the ratio between the first and second fin spacing, the frost formation process of the outer and inner fin assemblies is synchronized, minimizing the time for both fin assemblies to reach frost saturation. This effectively extends the heating time, increases the total heat exchange, and reduces the defrosting frequency, thereby reducing indoor temperature fluctuations, improving indoor temperature uniformity, and enhancing thermal comfort.

[0009] A further embodiment is that the outdoor heat exchanger also has an arc plate area, and in the first straight direction, one end of the first flat plate area is adjacent to one end of the arc plate area; the outer fin group also includes multiple first fins located in the arc plate area and distributed along the arc direction, and the inner fin group also includes multiple second fins located in the arc plate area and distributed along the arc direction; in the arc plate area, there is a first central angle between two adjacent first fins and a second central angle between two adjacent second fins, and the first central angle is 1.2 to 2 times the second central angle.

[0010] As can be seen from the above, the design of the arc plate area can make full use of the internal space of the outdoor unit to increase the heat exchange area of ​​the outdoor heat exchanger, thereby improving the heat exchange efficiency; the design of the ratio between the first central angle and the second central angle can also realize the synchronous frosting process of the outer fin group and the inner fin group, extend the heating time, reduce the defrosting frequency, and reduce the fluctuation range of indoor temperature.

[0011] A further embodiment includes an outdoor heat exchanger with a second flat plate area, and an arc plate area located between the second flat plate area and the first flat plate area. The outer fin assembly also includes multiple first fins located within the second flat plate area and distributed along a second straight line direction, and the inner fin assembly also includes multiple second fins located within the second flat plate area and distributed along a second straight line direction, with the first straight line direction intersecting the second straight line direction. Within the second flat plate area, there is a third fin spacing between two adjacent first fins and a fourth fin spacing between two adjacent second fins, with the third fin spacing being 1.5 to 3 times the fourth fin spacing.

[0012] As can be seen from the above, the second plate area can further utilize the internal space of the chassis to further increase the heat exchange area of ​​the outdoor heat exchanger; the proportional relationship between the third and fourth fin spacings ensures the synchronization of the frosting process between the inner and outer fin groups and the inner fin group in the second plate area.

[0013] A further proposed solution is to have a first layer spacing of 3 to 4 millimeters, a second layer spacing of 1.2 to 1.8 millimeters, a first central angle of 2° to 3°, a second central angle of 1° to 1.8°, a third layer spacing of 3 to 4 millimeters, and a fourth layer spacing of 1.2 to 1.8 millimeters.

[0014] As can be seen from the above, the design can effectively reduce airflow resistance and reduce the operating power consumption of the outdoor unit's fan module while ensuring that the outdoor radiator has sufficient heat exchange area.

[0015] A further proposed solution is to have a first and third piece spacing of 4 mm, a second and fourth piece spacing of 1.5 mm, a first central angle of 2°, and a second central angle of 1.5°.

[0016] As can be seen from the above, by optimizing the fin spacing, central angle parameters, etc., the outer fin group and the inner fin group can reach the frost layer saturation state at the same time.

[0017] A further proposed solution is that the width of both the first and second fins is between 18 and 22 millimeters.

[0018] As can be seen from the above, this design ensures that the heat exchange area of ​​the outdoor heat exchanger is large enough and the heat exchange time between the air and the outer and inner fin groups is long enough to guarantee the heat exchange effect between the outdoor heat exchanger and the air.

[0019] A further option is that the first fin is an aluminum fin, a copper fin, or a copper-aluminum composite fin, and the second fin is an aluminum fin, a copper fin, or a copper-aluminum composite fin; and / or both the first and second fins are coated with a hydrophobic layer.

[0020] As can be seen from the above, the design gives the first and second fins high thermal conductivity and the advantages of geothermal groups, improving the heat exchange effect between the outdoor heat exchanger and the air. The hydrophobic coating on the first and second fins can reduce the condensate retention time, thereby extending the frost saturation time of the outdoor heat exchanger and reducing the defrosting frequency.

[0021] To achieve the second objective of this utility model, this utility model provides an outdoor unit, including a chassis and a fan module. The chassis has a return air inlet and an air outlet. The fan module is installed inside the chassis and is located between the return air inlet and the air outlet, supplying air to the air outlet. The outdoor unit also includes the aforementioned outdoor heat exchanger, which is installed inside the chassis and located between the return air inlet and the fan module. The outer fin assembly is located between the return air inlet and the inner fin assembly.

[0022] As can be seen from the above, by adopting the aforementioned outdoor heat exchanger, the outdoor unit can extend the heating time, reduce the number of defrosting cycles, thereby reducing indoor temperature fluctuations during heating, improving heat exchange and heating efficiency, and reducing energy consumption.

[0023] A further solution is to have a water collection tray at the bottom of the chassis, with a drainage channel below the outdoor heat exchanger on the water collection tray, and a drain outlet at the lowest point of the drainage channel.

[0024] As can be seen above, the condensate dripping from the outdoor heat exchanger into the drip tray can be quickly discharged from the drip tray through the drainage channel, avoiding the condensate from solidifying in the drip tray due to the low outdoor ambient temperature, which would affect the normal operation of the outdoor heat exchanger and fan module.

[0025] To achieve the third objective of this utility model, this utility model provides an air conditioner, including an indoor unit, which also includes the aforementioned outdoor unit, and the indoor unit and the outdoor unit are connected.

[0026] As can be seen from the above, air conditioners equipped with the aforementioned outdoor units have a long heating time and a low defrosting frequency, resulting in small fluctuations in indoor temperature during heating, as well as high heat exchange and heating efficiency and low energy consumption. Attached Figure Description

[0027] Figure 1 This is a structural diagram of an embodiment of the outdoor unit of this utility model.

[0028] Figure 2 This is a structural diagram of the outdoor heat exchanger from a first-view perspective of an embodiment of the outdoor unit of this utility model.

[0029] Figure 3 This is a structural diagram of the outdoor heat exchanger from a second perspective of an embodiment of the outdoor unit of this utility model.

[0030] Figure 4 yes Figure 3 Enlarged view of point F in the middle.

[0031] Figure 5 yes Figure 3 A magnified view of point G in the middle.

[0032] Figure 6 yes Figure 3 A magnified view of section H in the middle.

[0033] Figure 7 This is a structural diagram of the outdoor unit embodiment of this utility model with some components omitted.

[0034] Figure 8 This is a comparison table of relevant data between conventional outdoor heat exchangers and the outdoor heat exchanger of this utility model.

[0035] The present invention will be further described below with reference to the accompanying drawings and embodiments. Detailed Implementation

[0036] Outdoor unit example

[0037] Reference Figure 1 The outdoor unit 100 includes an outdoor heat exchanger 1, a casing 2, and a fan module 3. The casing 2 has a return air inlet and an air outlet 21. The outdoor heat exchanger 1 and the fan module 3 are both installed inside the casing 2. The outdoor heat exchanger 1 is located between the return air inlet and the air outlet 21, and the fan module 3 is located between the outdoor heat exchanger 1 and the air outlet 21. The fan module 3 is used to draw air from outside the casing 2 into the return air inlet, so that the air passes through the outdoor heat exchanger 1 and exchanges heat with the outdoor heat exchanger 1. Finally, the air is discharged from the casing 2 through the air outlet 21.

[0038] Combination Figure 2 and Figure 3 The outdoor heat exchanger 1 includes an outer fin assembly 1 and an inner fin assembly 12. The outer fin assembly 1 is located on the windward side of the outdoor heat exchanger 1, and the inner fin assembly 12 is located on the leeward side of the outdoor heat exchanger 1. That is, the outer fin assembly 1 is located between the return air inlet and the inner fin assembly 12, and the inner fin assembly 12 is located between the outer fin assembly 1 and the fan module 3.

[0039] In this embodiment, the outdoor heat exchanger 1 has a first flat plate area C, an arc plate area D, and a second flat plate area E, with the arc plate area D located between the first flat plate area C and the second flat plate area E. The arc plate area D and the second flat plate area E can be distributed according to the internal space of the casing 2 to fully utilize the internal space of the casing 2, increase the heat exchange area of ​​the outdoor heat exchanger 1, thereby improving the heat exchange efficiency of the outdoor heat exchanger 1 and enhancing the cooling or heating effect of the air conditioner equipped with this outdoor unit 100.

[0040] Combination Figure 4 The outer fin group 1 includes multiple first fins 111 in the first flat plate region C, and the multiple first fins 111 are distributed at equal intervals along the first straight line direction; the inner fin group 12 includes multiple second fins 121 in the first flat plate region C, and the multiple second fins 121 are also distributed at equal intervals along the first straight line direction; in the first straight line direction, one end of the first flat plate region C is adjacent to the first end of the arc plate region D.

[0041] Within the first plate area C, the distance between two adjacent first fins 111 is the first fin distance L1, and the distance between two adjacent second fins 121 is the second fin distance L2, with the first fin distance L1 being 1.5 to 3 times the second fin distance L2.

[0042] It is evident that the outdoor heat exchanger 1 has a composite fin spacing, with the fin spacing on the windward side being greater than that on the leeward side. Since the outer fin assembly 1 is located on the windward side, its frosting speed is faster than that of the inner fin assembly 12 in heating mode. By increasing the fin spacing of the first fin 111, the time for frost bridges to form between the first fins 111 can be significantly extended, increasing the difficulty of frost bridge formation. This results in the outer fin assembly 1 being faster than existing fin assembly 1 when the gaps between the first fins 111 are completely blocked by frost bridges from the start of frost formation. The outer fin assembly of the outdoor heat exchanger can maintain a longer ventilation time (the ventilation time of outer fin assembly 1 is more than twice that of a conventional outer fin assembly), thus ensuring a long period of ventilation effect after the outer fin assembly 1 begins to frost. This allows sufficient humid air to continuously penetrate the outer fin assembly 1 to the inner fin assembly 12 located on the leeward side before the outer fin assembly 1 is completely blocked by frost bridges, where it condenses and frosts, achieving two rounds of dehumidification and cooling, and fully utilizing the function of the inner fin assembly 12. Furthermore, by designing the proportional relationship between the first fin spacing L1 and the second fin spacing L2, the inner fin assembly 12 and the outer fin assembly 1 can reach frost saturation almost simultaneously, achieving a synchronous frosting process between them. This minimizes the time it takes for both fin assemblies to reach frost saturation, effectively extending the heating time, increasing the total heat exchange while reducing the defrosting frequency, thereby reducing indoor temperature fluctuations, improving indoor temperature uniformity, and enhancing thermal comfort.

[0043] Combination Figure 5 Within the arc plate region D, the outer fin group 1 includes multiple first fins 111, distributed at equal central angles along the arc direction; the inner fin group includes multiple second fins 121, also distributed at equal central angles along the arc direction. The first central angle α between two adjacent first fins 111 is 1.2 to 2 times that between two adjacent second fins 121, ensuring that the fin spacing between the first fins 111 within the arc plate region D is also greater than the fin spacing between the second fins 121. Similarly, through the design of the proportional relationship between the first central angle α and the second central angle β, the inner fin group 12 in the arc plate region D reaches frost saturation almost simultaneously with the outer fin group 1, achieving synchronous frosting processes between the inner fin group 12 and the outer fin group 1. This minimizes the time required for both fin groups to reach frost saturation, thereby extending the heating time, increasing the total heat exchange, and reducing the defrosting frequency.

[0044] Combination Figure 6Within the second flat plate region E, the outer fin group 1 includes multiple first fins 111, which are evenly spaced along a second straight line direction; the inner fin group includes multiple second fins 121, which are also evenly spaced along the second straight line direction; wherein, the first straight line direction intersects the second pointing direction, and preferably, the first straight line direction is perpendicular to the second pointing direction. In the second straight line direction, one end of the second flat plate region E is adjacent to the second end of the arc plate region D.

[0045] Within the second plate region E, the spacing between two adjacent first fins 111 is the third fin spacing L3, and the spacing between two adjacent second fins 121 is the fourth fin spacing L4. The third fin spacing L3 is 1.5 to 3 times the fourth fin spacing L4. The design principles and achieved technical effects of the third fin spacing L3 and the fourth fin spacing L4 within the second plate region E are consistent with those of the first fin spacing L1 and the second fin spacing L2 within the first plate region C, and therefore will not be repeated here.

[0046] In some embodiments, the first fin spacing L1 is preferably between 3 mm and 4 mm, the second fin spacing L2 is preferably between 1.2 mm and 1.8 mm, the third fin spacing L3 is preferably between 3 mm and 4 mm, and the fourth fin spacing L4 is preferably between 1.2 mm and 1.8 mm; the first central angle α is preferably between 2° and 3°, and the second central angle b is preferably between 1° and 1.8°. This design can effectively reduce airflow resistance and reduce the operating power consumption of the fan module 3 of the outdoor unit 100 while ensuring that the outdoor radiator has sufficient heat exchange area.

[0047] Preferably, the third fin spacing L3 is equal to the first fin spacing L1, and the fourth fin spacing L4 is equal to the second fin spacing L2. For example, in this embodiment, the first fin spacing L1 and the third fin spacing L3 are both 4 mm, the second fin spacing L2 and the fourth fin spacing L4 are both 1.5 mm, the first central angle α is 2°, and the second central angle β is 1.5°. By optimizing the synergistic cooperation of fin spacing, central angle parameters, etc., the outer fin group 1 and the inner fin group 12 can reach the frost layer saturation state at almost the same time, while ensuring the heat exchange effect of the outdoor heat exchanger 1, and making the wind resistance of the outdoor heat exchanger 1 almost minimized, the heating time almost maximized, and the defrosting frequency almost minimized, so that the indoor temperature fluctuation is small during heating.

[0048] In some embodiments, the width W of the first fin 111 and the second fin 121 is preferably between 18 mm and 22 mm to ensure that the heat exchange area of ​​the outdoor heat exchanger 1 is large enough so that the heat exchange time between the air and the outer fin group 1 and the inner fin group 12 is long enough to ensure the heat exchange effect between the outdoor heat exchanger 1 and the air.

[0049] In this embodiment, both the first fin 111 and the second fin 121 are made of aluminum fins. Aluminum fins have advantages such as light weight, low cost, and good thermal conductivity. It is understood that in some embodiments, the first fin 111 and the second fin 121 may also be made of copper fins. Copper fins have the advantage of high thermal conductivity, which can improve the heat exchange effect and heat exchange efficiency of the outdoor heat exchanger 1. In some embodiments, the first fin 111 and the second fin 121 may also be made of copper-aluminum composite fins. Preferably, aluminum material is used as the substrate, and copper is coated on the aluminum substrate. The thickness of the copper layer is preferably about 0.03 mm. This design can optimize cost control and give the first fin 111 and the second fin 121 excellent thermal conductivity.

[0050] Furthermore, a hydrophobic layer is coated on the first fin 111 and the second fin 121 to reduce the residence time of condensate on the fins, better alleviate the frost formation of condensate on the fins, extend the frost saturation time of the outdoor heat exchanger 1, and thus further reduce the defrosting frequency.

[0051] Combination Figure 7 The bottom of the casing 2 is equipped with a water collection tray 22, and the water collection tray 22 is provided with a drainage channel 221 below the outdoor heat exchanger 1. The drainage channel 221 has a drainage slope, and a drain outlet 222 is provided at the lowest point of the drainage slope. The water collection tray 22 is used to collect the condensate dripping from the outdoor heat exchanger 1, and guides the condensate to the drain outlet 222 through the drainage channel 221 to discharge the condensate from the water collection tray 22. This prevents the condensate from solidifying in the water collection tray 22 due to the low outdoor ambient temperature, and ensures the normal operation of the outdoor heat exchanger 1 and the fan module 3.

[0052] The following combination Figure 8 The conventional outdoor heat exchanger and the outdoor heat exchanger 1 of this utility model are compared and described under the conditions of 0℃ temperature and 90% humidity.

[0053] For conventional outdoor heat exchangers:

[0054] The fin spacing of the outer fin group is 1.5 mm, and the fin spacing of the inner fin group is 1.5 mm.

[0055] In heating mode, after the air conditioner has been running for 20 minutes, there is obvious frost on the outer fin assembly, while there is almost no frost on the inner fin assembly. After the air conditioner has been running for 60 minutes, the outer fin assembly is completely covered with frost (reaching frost saturation), but there is almost no frost on the inner fins [the reason is that the frost completely blocks the gaps (ventilation channels) between the fins of the outer fin assembly]. At this time, the air conditioner enters defrosting mode.

[0056] For the outdoor heat exchanger 1 of this utility model, taking the first plate spacing L1 and the third plate spacing L3 of the outdoor heat exchanger 1 as examples, both being 4 mm, the second plate spacing L2 and the fourth plate spacing L4 being 1.5 mm, the first central angle α being 2°, and the second central angle b being 1.5°:

[0057] In heating mode, after the air conditioner has been running for 20 minutes, frost begins to form on the first fin 111 of the outer fin group 1 and the second fin 121 of the inner fin group 12. After the air conditioner has been running for 60 minutes, there is significant frost on both the first fin 111 of the outer fin group 1 and the second fin 121 of the inner fin group 12. At this point, due to the spacing design between the first fins 111, there is still a gap (ventilation channel) between the first fins 111, allowing air to still penetrate the outer fin group 1 and reach the inner fin group 12, thus maintaining a higher heating capacity. After the air conditioner has been running for 120 minutes, the first fin 111 of the outer fin group 1 is completely covered with frost (reaching frost saturation), and the second fin 121 of the inner fin group 12 is also completely covered with frost (reaching frost saturation). At this point, the air conditioner enters defrosting mode.

[0058] It can be seen that for an air conditioner using a conventional outdoor heat exchanger 1, when the running time is about 120 minutes, a defrosting process is required after about 60 minutes of running time, and the defrosting time is about 10 minutes; while for an air conditioner using the outdoor heat exchanger 1 provided by this utility model, when the running time is about 240 minutes, a defrosting process is required after about 150 minutes of running time, and the defrosting time is about 10 minutes.

[0059] In summary, the design of the outdoor heat exchanger 1 enables the air conditioner equipped with the outdoor unit 100 to extend the heating time, reduce the number of defrosting cycles, thereby reducing indoor temperature fluctuations during heating, improving heat exchange and heating efficiency, and reducing energy consumption.

[0060] Air Conditioner Example

[0061] The air conditioner includes an indoor unit and an outdoor unit as described in the above-described outdoor unit embodiment, with the indoor unit connected to the outdoor unit. By employing the aforementioned outdoor unit, the air conditioner achieves a longer heating time, a lower defrosting frequency, smaller fluctuations in indoor temperature during heating, higher heat exchange and heating efficiency, and lower energy consumption.

[0062] Finally, it should be emphasized that the above description is only a preferred embodiment of the present utility model and is not intended to limit the present utility model. For those skilled in the art, the present utility model can have various changes and modifications. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present utility model should be included within the protection scope of the present utility model.

Claims

1. An outdoor heat exchanger, the outdoor heat exchanger having a first flat plate area, the outdoor heat exchanger comprising an outer fin group and an inner fin group, the outer fin group comprising a plurality of first fins distributed along a first straight line direction in the first flat plate area, the inner fin group comprising a plurality of second fins distributed along the first straight line direction in the first flat plate area, characterized in that: Within the first plate area, there is a first fin spacing between two adjacent first fins and a second fin spacing between two adjacent second fins. The first fin spacing is 1.5 to 3 times the second fin spacing.

2. The outdoor heat exchanger according to claim 1, characterized in that: The outdoor heat exchanger also has an arc plate area, and in the first straight direction, one end of the first flat plate area is adjacent to one end of the arc plate area. The outer fin group further includes multiple first fins located within the arc plate area and distributed along the arc direction, and the inner fin group further includes multiple second fins located within the arc plate area and distributed along the arc direction. Within the arc plate area, there is a first central angle between two adjacent first fins and a second central angle between two adjacent second fins, wherein the first central angle is 1.2 to 2 times the second central angle.

3. The outdoor heat exchanger according to claim 2, characterized in that: The outdoor heat exchanger also has a second plate area, and the arc plate area is located between the second plate area and the first plate area; The outer fin group further includes multiple first fins located within the second flat plate area and distributed along the second straight line direction, and the inner fin group further includes multiple second fins located within the second flat plate area and distributed along the second straight line direction, wherein the first straight line direction intersects with the second straight line direction. Within the second plate region, there is a third fin spacing between two adjacent first fins and a fourth fin spacing between two adjacent second fins, wherein the third fin spacing is 1.5 to 3 times the fourth fin spacing.

4. The outdoor heat exchanger according to claim 3, characterized in that: The first interlayer spacing is between 3 mm and 4 mm, and the second interlayer spacing is between 1.2 mm and 1.8 mm; The first central angle is between 2° and 3°, and the second central angle is between 1° and 1.8°; The third piece spacing is between 3 mm and 4 mm, and the fourth piece spacing is between 1.2 mm and 1.8 mm.

5. The outdoor heat exchanger according to claim 4, characterized in that: The first and third sheet spacings are both 4 mm, the second and fourth sheet spacings are both 1.5 mm, the first central angle is 2°, and the second central angle is 1.5°.

6. The outdoor heat exchanger according to any one of claims 1 to 5, characterized in that: The width of both the first fin and the second fin is between 18 mm and 22 mm.

7. The outdoor heat exchanger according to claim 6, characterized in that: The first fin is an aluminum fin, a copper fin, or a copper-aluminum composite fin; the second fin is an aluminum fin, a copper fin, or a copper-aluminum composite fin; and / or Both the first fin and the second fin are coated with a hydrophobic layer.

8. Outdoor unit, including: The chassis has a return air vent and an exhaust air vent; A fan module is installed inside the casing, and the fan module is located between the return air inlet and the air outlet and supplies air to the air outlet; Its features are: The outdoor unit further includes an outdoor heat exchanger as described in any one of claims 1 to 7, wherein the outdoor heat exchanger is installed inside the casing and located between the return air inlet and the fan module, and the outer fin assembly is located between the return air inlet and the inner fin assembly.

9. The outdoor unit according to claim 8, characterized in that: The bottom of the casing is provided with a water receiving tray, and the water receiving tray is provided with a drainage channel below the outdoor heat exchanger. The lowest point of the drainage channel is provided with a drain outlet.

10. An air conditioner comprising an indoor unit, characterized by comprising: It also includes an outdoor unit as described in claim 8 or 9, wherein the indoor unit is connected to the outdoor unit.

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