Indoor unit of air conditioner

Abstract

The air conditioner indoor unit comprises a first heat exchanger and a second heat exchanger, wherein the first heat exchanger extends in the direction away from an air outlet in the height direction of a shell, and the second heat exchanger extends in the direction away from the air outlet. The fan volute comprises an upper volute and a lower volute; an extension plate is arranged at the end, close to the indoor heat exchanger, of the lower volute and extends in the direction close to the air outlet in the height direction of the shell. In a first section perpendicular to the thickness direction of the shell, the projection of the extension plate is a first straight line, the projection of the side, close to the indoor fan, of the first heat exchanger is a second straight line, and a first included angle beta is formed between the extension line of the first straight line and the second straight line and is larger than or equal to 90 degrees and smaller than or equal to 105 degrees. The extension plate is arranged, so that the airflow guided out of the air outlet of the volute can be accurately guided, impact loss and turbulence caused by the fact that the airflow directly impacts the windward side of the first heat exchanger are avoided, the heat exchange and dehumidification uniformity of the double heat exchangers is improved, and the use experience of a user is improved.

Description

Technical Field

[0001] This invention relates to the technical field of air conditioners, and particularly to an indoor unit of an air conditioner. Background Technology

[0002] The heat exchange performance of an air conditioner indoor unit is directly related to the airflow characteristics. As the core component of heat exchange, the layout of the heat exchanger and its relative position to the fan casing are key factors affecting airflow smoothness, heat exchange uniformity, and energy consumption. With increasing demands for heat exchange efficiency and functional diversity in air conditioning equipment, dual heat exchanger structures have become widely used in various air conditioner indoor units due to their ability to expand the effective heat exchange area and enhance heat exchange effects. Existing dual heat exchangers typically extend along the height of the casing and are located on the air outlet side of the fan casing. After being driven by the indoor fan, the airflow is drawn out from the air outlet of the casing and flows through the dual heat exchangers to complete heat exchange before finally being discharged from the air outlet of the casing. However, existing air conditioning indoor units using dual heat exchangers generally suffer from unreasonable airflow organization. There is a lack of effective airflow guidance structure between the air outlet of the fan casing and the dual heat exchangers. After the airflow is discharged from the air outlet of the casing, it is easy to directly impact the windward side of the first heat exchanger, resulting in uneven airflow velocity distribution and aggravated turbulence. This not only reduces the heat exchange uniformity of the dual heat exchangers, but also increases airflow impact loss and wind resistance. Ultimately, this leads to a decrease in the heat exchange efficiency of the air conditioning indoor unit, an increase in operating energy consumption, and the noise generated by turbulence and eddies also affects the user experience. In view of the above, this application is hereby submitted. Summary of the Invention

[0003] The present invention aims to at least partially solve the technical problems in the related art.

[0004] Therefore, according to embodiments of this disclosure, an air conditioning indoor unit is proposed, comprising: A housing, wherein an air duct is formed inside the housing, and an air inlet and an air outlet communicating with the air duct are provided on the housing. The thickness direction of the housing is defined from the front side to the rear side wall of the housing, and the height direction of the housing is defined from the top wall to the bottom wall of the housing. An indoor fan is installed inside the air duct and on the side closest to the air inlet; An indoor heat exchanger is disposed within the housing and on the side of the indoor fan away from the air inlet; the indoor heat exchanger includes: The first heat exchanger is arranged to extend away from the air outlet along the height direction of the shell. The second heat exchanger is disposed on the side of the first heat exchanger near the air outlet, and extends away from the air outlet along the height direction of the shell. Fan casing, wherein the indoor fan is disposed within the fan casing; comprising: The upper volute is located on the side of the indoor fan near the top of the housing; The lower volute is located on the side of the indoor fan near the bottom of the housing, and the upper volute and the lower volute form a volute outlet that communicates with the air outlet. An extension plate is provided at one end of the lower volute near the indoor heat exchanger, and the extension plate extends toward the air outlet along the height direction of the casing. The section perpendicular to the thickness direction of the shell is defined as the first section, the projection of the extension plate on the first section is the first straight line, the projection of the first heat exchanger on the side near the indoor fan is the second straight line, and there is a first included angle β between the extension of the first straight line and the second straight line, 90°≤β≤105°.

[0005] In the above technical solution, by setting an extension plate extending towards the air outlet at the end of the lower volute near the indoor heat exchanger, the airflow from the air outlet of the volute can be precisely guided. This avoids impact loss and turbulence caused by the airflow directly hitting the windward side of the first heat exchanger. Furthermore, by limiting the first angle between the first straight line projected by the extension plate and the second straight line projected by the first heat exchanger near the indoor fan to between 90° and 105°, the reasonable angle suppresses the separation of the airflow boundary layer, ensuring that the airflow flows uniformly and with low resistance through the first and second heat exchangers. This effectively improves the uniformity of heat exchange and dehumidification of the two heat exchangers, while reducing wind resistance loss and equipment operating energy consumption, reducing operating noise caused by airflow turbulence, and improving the user experience.

[0006] In some embodiments, the lower volute includes: A first enclosure panel, one end of which is connected to the extension panel; A second enclosure, one end of which is connected to the other end of the first enclosure, extends from one end near the top of the housing to one end near the bottom of the housing; The third enclosure has one end connected to the second enclosure and the other end connected to the upper volute. The indoor fan is at least partially located within the area enclosed by the first enclosure, the second enclosure, and the third enclosure. The projection of the second enclosure plate into the first section is defined as a third straight line, and there is a second included angle γ between the third straight line and the first straight line, where 47°≤γ≤57°.

[0007] In the above technical solution, by setting the included angle between the extension plate and the second enclosure plate between 47° and 57°, the enclosure structure of the lower volute and the extension plate form a smooth airflow guiding channel, further reducing the flow resistance of the airflow in the volute and preventing the formation of vortices inside the volute; at the same time, it can ensure that the airflow maintains a stable flow velocity and direction when it is discharged from the air outlet of the volute, providing a guarantee for the smooth flow through the heat exchanger, and further improving the overall heat exchange efficiency and operational stability of the equipment.

[0008] In some embodiments, the point closest to the first heat exchanger on the extension plate is defined as the first point, and the point furthest from the air outlet on the side of the first heat exchanger closest to the indoor fan is defined as the second point; the extension direction perpendicular to the thickness direction of the housing is defined as the first direction. The distance between the first point and the second point along the first direction is a first distance M, and the first distance M is not less than 50mm.

[0009] In the above technical solution, the first distance M is not less than 50mm, which provides sufficient buffer space for the airflow to flow from the extension plate to the first heat exchanger. This avoids excessive compression of the airflow and the formation of turbulence due to the small distance, and ensures that the airflow is fully diffused and has a uniform flow velocity before entering the first heat exchanger. This reduces the local pressure concentration of the airflow on the windward side of the heat exchanger, further reduces wind resistance loss, improves the contact efficiency between the airflow and the heat exchanger, and ensures heat exchange uniformity.

[0010] In some embodiments, a straight line passing through the second point and extending along the first direction is defined as a fourth straight line; The intersection of the extension of the first line and the fourth line is defined as the third point; The distance between the first point and the third point along the first direction is the second distance N; The first distance M is not greater than the second distance N.

[0011] In the above technical solution, after the airflow inside the volute starts from the first point and flows along the first straight line, the intersection of its extended trajectory and the fourth straight line from the second point toward the air outlet is not less than the first distance of the initial section of the airflow in the first direction. This ensures that the airflow can cover the windward area of ​​the first heat exchanger during the process of being delivered to the air outlet, avoid local heat exchange blind spots caused by airflow deflection, improve airflow utilization, and enhance heat exchange and dehumidification effects.

[0012] In some embodiments, the side of the first heat exchanger closest to the second heat exchanger is defined as a first plane, and the side of the second heat exchanger closest to the first heat exchanger is defined as a second plane. A third angle δ is formed between the first plane and the second plane, where 1.5°≤δ≤2.5°.

[0013] In the above technical solution, by setting a certain angle between the two heat exchangers, the two heat exchangers form a slightly inclined relative layout, which not only avoids the airflow stagnation between the two heat exchangers caused by the parallel layout, but also prevents excessive airflow diffusion caused by an excessively large angle, reduces eddies and airflow losses between the two heat exchangers, and improves the overall heat exchange efficiency.

[0014] In some embodiments, the minimum distance between the first plane and the second plane is a third distance H1, where 12mm ≤ H1 ≤ 20mm.

[0015] The above technical solution ensures that there is sufficient airflow channel width between the two heat exchangers to avoid increased wind resistance caused by obstructed airflow, and also prevents waste of heat exchange area and airflow diffusion caused by excessive spacing, so that the airflow maintains a stable flow rate between the two heat exchangers and fully contacts the heat exchange surface.

[0016] In some embodiments, the point on the upper volute closest to the first heat exchanger is defined as the fourth point; the extending direction perpendicular to the thickness direction of the casing is defined as the first direction; The line that passes through the fourth point and extends along the first direction is defined as the fifth line; The fifth line and the second line form a fourth included angle α, where 41°≤α≤45°.

[0017] In the above technical solution, the airflow outlet direction of the upper volute is precisely matched with the windward side of the first heat exchanger. After the airflow is discharged from the upper side of the volute, it can flow to the first heat exchanger at a reasonable angle, avoiding the airflow on the upper side from colliding with the airflow guided by the lower extension plate. This design realizes the coordinated flow of airflow on the upper and lower sides, further improving the uniformity of the overall airflow in the duct, reducing local airflow impact and eddies, and reducing operating noise and energy consumption.

[0018] In some embodiments, the side of the second heat exchanger away from the first heat exchanger is defined as the sixth straight line projected into the first cross section; The projection of the bottom wall of the shell into the first cross section is defined as the seventh straight line; The sixth line and the seventh line form a fifth included angle ε, and the sum of the third included angle and the fourth included angle is equal to the fifth included angle.

[0019] In the above technical solution, the inclined layout of the dual heat exchangers, the airflow guidance angle of the upper volute, and the bottom of the shell can work together to achieve a synergistic effect. After the airflow is discharged from the volute, it flows through the dual heat exchangers along a preset trajectory through the extension plate and the upper airflow guide, reducing airflow boundary layer separation and flow loss. At the same time, it ensures that the installation layout of the heat exchangers and the duct structure are perfectly matched, improving the utilization rate of the internal space of the equipment.

[0020] In some embodiments, the indoor unit of the air conditioner further includes a water collection tray; The water receiving tray is located below the indoor heat exchanger. The lower ends of the first heat exchanger and the second heat exchanger are both in contact with the groove wall of the water receiving tray. The water receiving tray is used to receive the condensate generated by the indoor heat exchanger. Along the direction extending from the air inlet to the air outlet, the water receiving tray extends toward the top wall of the housing.

[0021] In the above technical solution, the inclined extension design of the water receiving tray is adapted to the layout of the heat exchanger. After the condensate drips from the heat exchanger surface onto the water receiving tray, it can quickly flow to the water collection area under the action of gravity and inclined guidance, avoiding the condensate from stagnating in the tank. At the same time, the inclined structure reduces the contact area between the airflow and the water surface of the water receiving tray, reduces the risk of the airflow tearing the water film, effectively prevents condensate splashing, and improves the user experience.

[0022] In some embodiments, the projection of the water receiving tray near the groove wall of the indoor heat exchanger in the first cross section is defined as the eighth straight line; The sixth included angle θ is formed between the eighth line and the seventh line, where 2°≤θ≤5°.

[0023] In the above technical solution, the sixth included angle is limited to between 2° and 5°, so that the tilt angle of the water receiving tray ensures smooth flow of condensate water, while avoiding waste of space in the tank or overflow of condensate water due to excessive angle, thus ensuring efficient collection of condensate water.

[0024] It should be understood that the above general description and the following detailed description are exemplary and explanatory only, and do not limit this application. Attached Figure Description

[0025] Figure 1 This is a schematic diagram of the structure of an air conditioner indoor unit according to an embodiment of this application; Figure 2 This is a schematic diagram of a portion of the structure of an air conditioner indoor unit according to an embodiment of this application; Figure 3 This is a schematic diagram of the main structure of an air conditioner indoor unit according to an embodiment of this application; Figure 4 yes Figure 3 A schematic diagram of the cross-sectional structure of AA in the diagram; Figure 5 This is a cross-sectional structural diagram of an air conditioner indoor unit according to an embodiment of this application; Figure 6 yes Figure 5 A magnified structural diagram of A in the middle; Figure 7This is a schematic diagram of airflow circulation inside an indoor heat exchanger according to an embodiment of this application; Figure 8 This is a schematic diagram of the airflow distribution at the outlet after rectification by the indoor heat exchanger according to an embodiment of this application; Figure 9 This is a schematic diagram of the wind speed distribution on the windward side of the first heat exchanger according to an embodiment of this application; Figure 10 This is a schematic diagram of the wind speed distribution on the windward side of the second heat exchanger according to an embodiment of this application.

[0026] The annotations in the attached figures are explained as follows: 100. Indoor unit; 1. Housing; 2. Air inlet; 3. Air outlet; 4. Indoor fan; 5. Indoor heat exchanger; 510. First heat exchanger; 520. Second heat exchanger; 6. Fan casing; 610. Upper casing; 611. First plate; 612. Second plate; 620. Lower volute; 621. First diaphragm; 622. Second diaphragm; 623. Third diaphragm; 630. Extension plate; 640. Volute air inlet; 650. Volute air outlet; 7. Water tray; 710. Water storage tank. Detailed Implementation

[0027] Typical embodiments embodying the features and advantages of the present invention will be described in detail in the following description. It should be understood that the present invention can have various variations in different embodiments without departing from the scope of the present invention, and the descriptions and illustrations herein are for illustrative purposes only and not intended to limit the present invention.

[0028] In the description of this application, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are used only for the convenience of describing this application and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this application.

[0029] Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of the stated features. In the description of this application, "a plurality of" means two or more, unless otherwise explicitly specified.

[0030] In the description of this application, it should be noted that, unless otherwise expressly specified and limited, the terms "installation," "connection," and "linking" 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 application based on the specific circumstances.

[0031] In existing technologies, the heat exchanger structure design of the indoor unit of an air conditioner directly affects the overall performance of the unit. Current dual-heat exchanger layouts suffer from unreasonable placement. When airflow passes over the impeller, turbulence easily forms, leading to uneven airflow distribution, reduced heat exchange efficiency, and noise generation. In some designs, the distance between the two heat exchangers is too small, increasing ventilation resistance. These problems make it difficult for air conditioning equipment to simultaneously meet the requirements of high-efficiency heat exchange, low-noise operation, and adaptability to compact spaces.

[0032] To address these issues, the spatial layout of the dual heat exchangers needs to be optimized to balance airflow distribution and heat exchange efficiency. Analysis revealed that an excessively large angle between the two heat exchangers leads to turbulent airflow paths, while a completely parallel arrangement increases flow resistance. Therefore, it is necessary to find an angle range that guides smooth airflow while maintaining sufficient heat exchange area. Furthermore, the tilt angle of the heat exchangers must be coordinated with the fan position to avoid the formation of localized stagnation areas on the heat exchanger surface.

[0033] Therefore, this application proposes an indoor air conditioning unit, as detailed below with reference to the appendix. Figures 1-10 Describe the indoor unit of the air conditioner.

[0034] In this application, reference is made to Figure 1 The indoor unit 100 can be a component of an air conditioner. The air conditioner may also include an outdoor unit. (See reference...) Figure 1 The indoor unit 100 of the air conditioner can be a split wall-mounted air conditioner, and the air conditioner can be a cooling unit or a cooling and heating unit. In the description of this invention, the air conditioner is described as a cooling and heating unit.

[0035] In this application, the outdoor unit of an air conditioner may include an outdoor unit housing. The outdoor unit housing may contain an outdoor receiving space. The outdoor unit may include an outdoor heat exchanger. The outdoor heat exchanger may be located within the outdoor receiving space. The outdoor unit may also include an outdoor fan. The outdoor fan may be located within the outdoor receiving space.

[0036] In this application, the outdoor unit casing may be provided with an outdoor air inlet. The outdoor air inlet may communicate with the outdoor enclosure space. The outdoor air inlet can be used to introduce outdoor airflow into the outdoor enclosure space. The outdoor unit casing may be provided with an outdoor air outlet. The outdoor air outlet may communicate with the outdoor enclosure space. The outdoor air outlet can be used to lead the airflow from the outdoor enclosure space to the outside of the outdoor enclosure space. The rotation of the outdoor fan causes the outdoor airflow to enter the outdoor enclosure space through the outdoor air inlet and exchange heat with the outdoor heat exchanger. The heat-exchanged outdoor airflow flows out of the outdoor enclosure space through the outdoor air outlet.

[0037] In this application, the air conditioner may also include a compressor. The compressor may be located within an outdoor enclosure. The air conditioner may include a throttling device. The throttling device is used for flow control.

[0038] Reference Figures 1-10 This application proposes an indoor unit for an air conditioner. (Refer to...) Figure 2 The air conditioner indoor unit 100 includes a housing 1. The housing 1 is configured as the housing of the air conditioner indoor unit 100. The housing 1 may have a hollow cuboid structure. It should be noted that in other embodiments, the housing 1 may also adopt other shapes. The specific shape of the housing 1 can be adjusted as needed and is not limited here.

[0039] In this application, reference is made to Figure 1 The housing 1 may have a top and a bottom. The distance from the bottom wall of the housing 1 to the top wall of the housing 1 can be the height direction of the housing 1. The housing 1 may also have a length direction. The distance from the first side end of the housing 1 to the second side end of the housing 1 can be the length direction of the housing 1, as shown in the figure. Figure 1 and Figure 3 The left side of housing 1 is the first side end, and the right side of housing 1 is the second side end. Housing 1 may have a front side and a rear side that are arranged opposite to each other. The side of housing 1 facing the user can be the front side of housing 1. The distance from the front side to the rear side of housing 1 can be the thickness direction of housing 1.

[0040] In this application, references Figure 1 and Figure 3 The housing 1 serves as the installation base, and an air duct for airflow is formed inside it. The housing 1 is equipped with an air inlet 2 and an air outlet 3 connected to the air duct. The direction from the top wall to the bottom wall of the housing 1 is defined as the height direction of the housing, that is, this direction is consistent with the vertical direction, ensuring that the airflow flows along a reasonable path.

[0041] Reference Figure 2 An indoor fan 4 and an indoor heat exchanger 5 are installed inside the casing 1. The indoor fan 4 is located inside the air duct and near the air inlet 2, providing the power for airflow. The indoor fan 4 rotates inside the casing 1, drawing in air from outside the casing 1 through the air inlet 2. The airflow passes through the indoor heat exchanger 5 inside the casing 1 and is then discharged through the air outlet 3. The indoor heat exchanger 5, located inside the casing 1 and on the side of the indoor fan 4 furthest from the air inlet 2, is the core component for heat exchange and lays the foundation for improving heat exchange efficiency.

[0042] In this application, referring to Figure 4, the air inlet 2 serves as the entrance for airflow into the housing 1. The air inlet 2 can be located on the rear side of the housing 1. The air outlet 3 serves as the outlet for airflow out of the housing 1, and the opening direction of the air outlet 3 extends along the length direction of the housing 1. The air outlet 3 can be located on the side of the housing 1, or it can be located on the front side of the housing 1. The specific location of the air outlet 3 can be adjusted as needed and is not limited here. In this application, the air outlet 3 is located on the front side of the housing 1.

[0043] In this application, the indoor unit 100 of the air conditioner may also include an air guide plate, which is rotatably connected to the housing 1. The air guide plate rotates relative to the housing 1 to open or close the air outlet 3, thereby controlling the airflow direction of the indoor unit 100 of the air conditioner.

[0044] In this application, reference is made to Figure 3 and Figure 5 The indoor unit 100 of the air conditioner may also include an indoor fan 4, which is installed in the air duct and located on the side close to the air inlet 2. The indoor fan 4 can rotate to drive the airflow from the indoor air inlet 2 into the air duct to exchange heat with the indoor heat exchanger 5. The airflow after exchanging heat with the indoor heat exchanger 5 can flow into the user's room from the indoor air outlet 3.

[0045] In this application, reference is made to Figure 2 and Figure 4 The indoor unit 100 of the air conditioner may further include an indoor heat exchanger 5, which is disposed within the housing 1 and on the side of the indoor fan 4 away from the air inlet 2. (Refer to...) Figure 5 and Figure 7The indoor heat exchanger 5 includes a first heat exchanger 510 and a second heat exchanger 520. Along the height direction of the housing 1, the first heat exchanger 510 extends away from the air outlet 3. That is, from one end near the top of the housing 1 to one end near the bottom of the housing 1, the first heat exchanger 510 is gradually moved away from the air outlet 3. The second heat exchanger 520 is disposed on the side of the first heat exchanger 510 near the air outlet 3, and along the height direction of the housing 1, the second heat exchanger 520 extends away from the air outlet 3. That is, from one end near the top of the housing 1 to one end near the bottom of the housing 1, the second heat exchanger 520 is gradually moved away from the air outlet 3.

[0046] In this application, reference is made to Figure 2 , Figure 4 and Figure 5 The indoor unit 100 of the air conditioner also includes a fan volute 6, which houses the indoor fan 4; that is, the indoor fan 4 is housed within the fan volute 6. The fan volute 6 includes an upper volute 610 and a lower volute 620. The upper volute 610 is located on the side of the indoor fan 4 near the top of the housing 1; the lower volute 620 is located on the side of the indoor fan 4 near the bottom of the housing 1. A volute outlet 650, communicating with the air outlet 3, is formed between the upper volute 610 and the lower volute 620. This volute outlet 650 communicates with the air outlet 3 of the housing 1, ensuring that the airflow driven by the fan can be smoothly guided to the heat exchanger. In addition, a volute inlet 640, communicating with the air inlet 2, is also formed between the upper volute 610 and the lower volute 620. This volute inlet 640 is located on the left and right sides of the unit and communicates with the air inlet 2 of the housing 1, ensuring that the airflow driven by the fan can be smoothly guided to the heat exchanger.

[0047] In this application, when the indoor heat exchanger 5 is used as a condenser, the air conditioner is used as a heater in heating mode; when the indoor heat exchanger 5 is used as an evaporator, the air conditioner is used as a cooler in cooling mode.

[0048] For example, when the air conditioner is operating in heating mode, both heat exchangers in the indoor heat exchanger 5 function as condensers, releasing heat through the condensation of gaseous refrigerant, and the air conditioner acts as a heater in heating mode. The compressor compresses the low-temperature, low-pressure gaseous refrigerant into a high-temperature, high-pressure gaseous refrigerant, which is then delivered to the two sets of heat exchangers in the indoor unit 100. The first high-temperature, high-pressure gaseous refrigerant flows into the first heat exchanger 510; the refrigerant condenses in the coil, releasing a large amount of heat, which heats the indoor air flowing through the first heat exchanger 510. The condensed high-temperature, high-pressure liquid refrigerant flows out from the liquid outlet of the first heat exchanger 510 and returns to the condenser (or gas-liquid separator) of the outdoor unit.

[0049] The second stream of high-temperature, high-pressure gaseous refrigerant flows simultaneously into the second heat exchanger 520. Within the second heat exchanger 520, the refrigerant fully condenses and releases heat, continuously heating the indoor air. The condensed liquid refrigerant flows out from the liquid outlet of the second heat exchanger 520, merging with the first stream of refrigerant and returning to the outdoor unit. The merged refrigerant then evaporates and absorbs heat (from the outdoor air) in the outdoor unit, becoming gaseous again. It is then drawn into the compressor and compressed, entering the next heating cycle. Through the coordinated heat release of the dual condensers, the indoor temperature rise rate and heating stability are improved.

[0050] When the air conditioner is operating in cooling mode, the two heat exchangers in the indoor heat exchanger 5 act as evaporators. Liquid refrigerant evaporates evenly within the indoor heat exchanger 5, absorbing heat, and the air conditioner functions as a cooler in cooling mode. The compressor compresses the low-temperature, low-pressure gaseous refrigerant into a high-temperature, high-pressure gaseous refrigerant, which is then delivered to the condenser of the outdoor unit. In the condenser, the refrigerant exchanges heat with the outdoor air, condensing into a high-temperature, high-pressure liquid refrigerant, which is then distributed through the outdoor unit's refrigerant supply pipeline to two independent throttling devices. The first path of liquid refrigerant, after being throttled by the throttling device, becomes a low-temperature, low-pressure gas-liquid mixture, entering the first heat exchanger 510 from its liquid port. The refrigerant evaporates evenly within the first heat exchanger 510, absorbing heat from the indoor air flowing through it, thus achieving cooling. The evaporated low-temperature, low-pressure gaseous refrigerant then flows out from the gas port of the first heat exchanger 510 and returns to the outdoor unit. The second stream of liquid refrigerant, after being simultaneously throttled by another set of throttling devices, forms a low-temperature, low-pressure gas-liquid mixture. This mixture enters the second heat exchanger 520 through its liquid inlet. Within the second heat exchanger 520, the refrigerant fully evaporates and absorbs heat, further cooling the indoor air. The evaporated gaseous refrigerant then flows out of the second heat exchanger 520 through its gas inlet and returns to the outdoor unit. Both streams of refrigerant then return to the compressor, where they are compressed again and enter the next refrigeration cycle. Through the coordinated heat absorption by the dual evaporators, the indoor cooling efficiency and temperature uniformity are improved.

[0051] Furthermore, the air conditioner of this application may also have a non-cooling dehumidification mode, wherein the first heat exchanger 510 is connected to the outdoor unit 2 of the air conditioner by setting a first throttling component; and the second heat exchanger 520 is connected to the outdoor unit 2 of the air conditioner by setting a second throttling component. The first and second throttling components refer to components that regulate the refrigerant flow rate, such as electronic expansion valves, used to control the refrigerant flow rate entering different heat exchangers.

[0052] Specifically, when the non-cooling dehumidification mode is activated, the controller opens the first throttling component, allowing the refrigerant to enter the first heat exchanger 510 for cooling. Within the first heat exchanger 510, the refrigerant absorbs heat from the air to complete cooling and dehumidification. After heat exchange, the refrigerant returns from the first heat exchanger 510 to the compressor's first gas pipe interface. Simultaneously, the controller controls the refrigerant output from the compressor's second gas pipe interface to enter the second heat exchanger 520 for heating. After heat exchange, the refrigerant passes through the second throttling component and directly enters the first heat exchanger 510. The two refrigerant streams merge at the first throttling component, forming a closed loop, thus maintaining a stable air temperature after dehumidification. By adjusting the operating pressure difference between the two heat exchangers, a dynamic balance between cooling and heating capacity can be achieved. This process avoids flow rate conflicts of the refrigerant in a single loop by separating the cooling and heating paths.

[0053] When executing the first dehumidification mode, the controller uses an independent loop to make the first heat exchanger 510 act as an evaporator (cooling and dehumidifying) and the second heat exchanger 520 act as a condenser (releasing and replenishing heat), forming a synergistic cycle of dehumidification and heat replenishment. The first heat exchanger 510 condenses the moisture in the air to complete the dehumidification, and the heat released by the second heat exchanger 520 just offsets the cooling generated during the dehumidification process, preventing the indoor temperature from being too low. At the same time, the precise switching and confluence design of the refrigerant circuit ensures the energy balance between dehumidification and heat replenishment, ensuring both dehumidification efficiency and maintaining a stable room temperature, achieving the core requirement of "dehumidifying only without cooling", improving user comfort, and the independent loop control allows for more precise matching of refrigerant flow and heat exchange intensity.

[0054] In this application, reference is made to Figure 4 , Figure 5 and Figure 6 An extension plate 630 is provided at one end of the lower volute 620 near the indoor heat exchanger 5. The extension plate 630 extends along the height direction of the shell 1 towards the air outlet 3 to form an airflow guiding structure.

[0055] Reference Figure 4 , Figure 5 and Figure 6 The section perpendicular to the thickness direction of shell 1 is defined as the first section, that is... Figure 3 Within the vertical section of AA, the projection of the extension plate 630 onto the first section is a first straight line, and the projection of the first heat exchanger 510 on the side closer to the indoor fan 4 is a second straight line. An angle β exists between the extension of the first straight line and the second straight line, where 90°≤β≤105°. The extension plate 630 guides the airflow discharged from the volute outlet 650 towards the first heat exchanger 510. When β is between 90° and 105°, refer to... Figure 7After being guided by the extension plate 630, the airflow can impact the windward surface of the first heat exchanger 510 in a forward direction, avoiding the problem of increased turbulence caused by direct airflow impact. This significantly reduces the turbulence intensity of the airflow on the heat exchanger surface, reduces energy loss caused by turbulence, and results in smoother airflow with significantly reduced eddies and turbulence, thus lowering operating noise. At the same time, this angle works in conjunction with the overall airflow guiding structure of the lower volute 620 to prevent the formation of dead zones or backflow in the area between the volute and the heat exchanger. The reduction in wind resistance can reduce the operating load of the indoor fan 4, thereby reducing the overall energy consumption of the air conditioning system.

[0056] When β < 90°, the airflow impact intensifies and the turbulence loss surges. At this time, the guiding direction of the extension plate 630 causes the airflow to impact the windward side of the first heat exchanger 510 at an acute angle. The airflow will form a strong turbulence zone at the impact point, which will significantly increase energy loss and wind resistance by 20%-30%, resulting in a significant increase in fan energy consumption. The increase in turbulence intensity and the impact of local high-speed airflow will increase the noise of air conditioning operation and even produce obvious airflow whistling sound, which seriously affects the user experience.

[0057] When β > 105°, the guiding angle of the extension plate 630 is too large. After passing through the extension plate 630, the airflow will deviate from the windward side of the first heat exchanger 510. Some airflow may even form a backflow between the volute and the heat exchanger. Not only will it fail to effectively flow through the heat exchanger to complete heat exchange, but it will also interfere with the mainstream airflow, further aggravating turbulence. The deviated airflow can only cover a part of the first heat exchanger 510, and the core heat exchange area cannot be fully contacted by the airflow. The heat exchange advantage of the dual heat exchangers cannot be utilized, and the cooling / heating capacity of the air conditioner will decrease.

[0058] In this application, reference is made to Figure 4 , Figure 5 and Figure 6 The lower volute 620 includes a first enclosure 621, a second enclosure 622, and a third enclosure 623 connected in sequence. One end of the first enclosure 621 is connected to the extension plate 630, forming a transition section for airflow guidance. The first enclosure 621 is a smooth arc-shaped plate with an overall concave curved structure, that is, it is concave towards the indoor fan 4 and away from the first heat exchanger 510. The end connected to the second enclosure 622 is a tangential butt joint end, with its end face smoothly tangent to the side of the second enclosure 622, without steps or sharp edges, ensuring a continuous airflow trajectory from the second enclosure 622 to the first enclosure 621; the end connected to the extension plate 630 can also be smoothly tangential, smoothly transmitting the arc-guided airflow to the extension plate 630.

[0059] One end of the second enclosure 622 is connected to the other end of the first enclosure 621. The second enclosure 622 extends from the end near the top of the housing 1 to the end near the bottom of the housing 1. It can be understood that the second enclosure 622 is a straight segment, and the whole structure can be obliquely extended. The main body is a straight plate, extending obliquely from the end near the top of the housing 1 to the end near the bottom of the housing 1, in a direction away from the air outlet 3. Of course, it can also be set parallel to the height direction of the housing 1.

[0060] One end of the third enclosure 623 is connected to the second enclosure 622, and the other end of the third enclosure 623 is connected to the upper volute 610. The indoor fan 4 is at least partially located within the area enclosed by the first enclosure 621, the second enclosure 622, and the third enclosure 623. Together, they form a complete lower volute 620 cavity, ensuring the stable operation of the indoor fan 4 and guiding the airflow to be discharged smoothly. The third enclosure 623 is an arc-shaped plate that fits the outer contour of the indoor fan 4. It has an overall convex curved structure with the bending direction facing away from the indoor fan 4. It is used to wrap the lower area of ​​the indoor fan 4, wrapping about 1 / 3 to 1 / 2 of the lower circumference of the indoor fan 4, forming a semi-enclosed structure. This ensures the fan installation space and effectively guides the airflow to rotate and be discharged along the arc surface, guiding the airflow generated by the fan rotation towards the second enclosure 622. The end where the third enclosure plate 623 connects to the second enclosure plate 622 is a smooth transition end, with its arc-shaped surface tangentially aligned with the side of the second enclosure plate 622. Airflow can flow directly from the arc-shaped surface of the third enclosure plate 623 to the second enclosure plate 622 without any turning loss. The end connecting to the upper volute 610 can be a stepped connection end, with the end face machined into a stepped shape. It is fixedly connected to the lower end face of the upper volute 610 by bolts. Simultaneously, the stepped structure serves as a seal, preventing airflow leakage from the connection point between the upper and lower volutes 620.

[0061] Refer to Figure 5 The projection of the second enclosure plate 622 into the first cross-section is defined as a third straight line, and a second included angle γ exists between the third straight line and the first straight line, where 47°≤γ≤57°. By setting the included angle between the extension plate 630 and the second enclosure plate 622 between 47° and 57°, the enclosure structure of the lower volute 620 and the extension plate 630 form a smooth airflow guiding channel, further reducing the flow resistance of the airflow within the volute and preventing the formation of vortices inside the volute. At the same time, it ensures that the airflow maintains a stable velocity and direction when exiting from the volute outlet 650, providing a guarantee for the smooth flow through the heat exchanger and further improving the overall heat exchange efficiency and operational stability of the equipment.

[0062] In this application, reference is made to Figure 4 and Figure 5The first point is defined as the point on the extension plate 630 closest to the first heat exchanger 510, and the second point is defined as the point on the side of the first heat exchanger 510 closest to the indoor fan 4 furthest from the air outlet 3; the first direction is defined as the extension direction perpendicular to the thickness direction of the shell 1, that is... Figure 4 The X-axis direction in the first direction; the distance between the first point and the second point along the first direction is the first distance M, and the first distance M is not less than 50mm.

[0063] Reference Figures 8-10 Setting the first distance M to be no less than 50mm allows sufficient buffer space for the airflow to flow from the extension plate 630 to the first heat exchanger 510, avoiding excessive compression of the airflow and the formation of turbulence due to the small distance. This ensures that the airflow is fully diffused and has a uniform flow velocity before entering the first heat exchanger 510, reduces local pressure concentration of the airflow on the windward side of the heat exchanger, further reduces wind resistance loss, improves the contact efficiency between the airflow and the heat exchanger, and ensures heat exchange uniformity.

[0064] In this application, reference is made to Figure 4 and Figure 5 The straight line passing through the second point and extending along the first direction is defined as the fourth straight line, that is, the extension line from the second point towards the air outlet 3 is the fourth straight line; the intersection of the extension of the first straight line and the fourth straight line is defined as the third point; the distance between the first point and the third point along the first direction is the second distance N; the first distance M is not greater than the second distance N. It can be understood that the lower end of the first heat exchanger 510 should always be located on the side of the third point closer to the indoor fan 4. When the airflow inside the fan casing 6 starts from the first point and flows along the first straight line, its extension trajectory can intersect with the fourth straight line from the second point towards the air outlet 3. The horizontal distance between the intersection point and the first point is not less than the first distance of the initial section of the airflow. This ensures that during the process of airflow being delivered to the air outlet 3, the guiding direction of the extension plate 630 can effectively cover the windward side of the first heat exchanger 510. During the diffusion process, the airflow is always within the guiding range of the extension plate 630, avoiding excessive airflow diffusion due to excessive M, which deviates from the effective heat exchange area of ​​the first heat exchanger 510. When M does not exceed the distance between the second and third points, the airflow can flow precisely to the windward side of the first heat exchanger 510, which not only ensures the uniformity of the airflow, but also avoids energy loss caused by ineffective diffusion, so that the indoor unit 100 of the air conditioner can maintain stable heat exchange performance and low energy consumption under different operating conditions.

[0065] In this application, reference is made to Figure 4 and Figure 5The side of the first heat exchanger 510 closest to the second heat exchanger 520 is defined as the first plane, and the side of the second heat exchanger 520 closest to the first heat exchanger 510 is defined as the second plane. A third angle δ is formed between the first and second planes, where 1.5°≤δ≤2.5°. In other words, the two heat exchangers are arranged in a front-to-back relationship along the airflow path. Specifically, their positions can be fixed using independent mounting brackets to form a phased heat exchange area. Both the first heat exchanger 510 and the second heat exchanger 520 are positioned from the end closest to the air outlet 3 towards the end closest to the indoor fan 4, gradually moving away from the air outlet 3. That is, the heat exchanger bodies are arranged at an angle along the airflow direction, which prolongs the contact time between the airflow and the heat exchanger.

[0066] Specifically, when the airflow enters the duct from the air inlet 2, it is first accelerated by the indoor fan 4, and then flows sequentially through the first heat exchanger 510 and the second heat exchanger 520. Since both heat exchangers are inclined away from the air outlet 3, the airflow increases the contact area as it flows over the surfaces of the first heat exchanger 510 and the second heat exchanger 520. An angle of 1.5° to 2.5° is set between the planes of the two heat exchangers to create a laminar flow within the channel between them, avoiding flow obstruction caused by an excessively small angle or an excessively wide flow channel caused by an excessively large angle. This angle range ensures that the airflow maintains an appropriate velocity while fully contacting the surface areas of the two heat exchangers, achieving efficient heat exchange.

[0067] In existing technologies, traditional dual heat exchangers often employ parallel arrangement or a large-angle cross layout. Parallel arrangement results in narrow airflow channels and a significant increase in flow resistance; large-angle cross layout leads to excessive spacing between the two heat exchangers, causing some airflow to escape through the gap without sufficient heat exchange. This solution precisely controls the angle between the planes of the two heat exchangers to between 1.5° and 2.5°, avoiding both the resistance problem of parallel arrangement and the heat exchange area loss caused by large angles. Simultaneously, the tilt direction of the two heat exchangers aligns with the airflow diffusion direction, effectively reducing local turbulence intensity.

[0068] Thus, both the first heat exchanger 510 and the second heat exchanger 520 adopt an inclined design that gradually moves away from the air outlet 3 towards the indoor fan 4, conforming to the airflow trajectory. This avoids airflow stagnation between the two heat exchangers caused by a parallel layout, reduces the impact and turbulence of airflow as it passes through the heat exchangers, and prevents the generation of turbulence. The inclined layout increases the contact area between the heat exchanger and the airflow. Combined with a reasonable angle, this makes the air velocity distribution on the heat exchanger surface more uniform, avoiding insufficient local heat exchange and preventing excessive airflow diffusion caused by an excessively large angle. It also reduces eddies between the two heat exchangers. Airflow loss is reduced, improving overall heat exchange efficiency. The angle between the two heat exchangers is between 1.5° and 2.5°, precisely matching the airflow distribution and forming a smooth airflow channel between the two heat exchangers. This avoids boundary layer separation, reduces wind resistance loss, and improves air supply efficiency. The precise control of the heat exchanger spacing and position parameters reduces the space occupied by the two heat exchangers in the shell 11. It effectively optimizes the airflow channel to reduce turbulence, improves heat exchange efficiency, and reduces operating noise. It has the advantages of optimizing the heat exchanger structure layout to improve heat exchange efficiency, reduce operating noise, and improve space adaptability.

[0069] In this application, reference is made to Figure 4 and Figure 5 The minimum distance between the first plane and the second plane is the third distance H1, where 12mm ≤ H1 ≤ 20mm.

[0070] Specifically, the first plane refers to the reference plane formed by the side of the first heat exchanger 510 near the second heat exchanger 520, and the second plane refers to the reference plane formed by the side of the second heat exchanger 520 near the first heat exchanger 510. This second plane can be defined by the surface of the heat exchanger shell 1 or an extended plane of the internal support structure, and is used to establish a spatial constraint relationship with the first plane. The minimum distance between adjacent sides of the two heat exchangers is controlled within the range of 12-20mm. This distance range can be achieved by limiting the installation position and angle of the heat exchangers. When the airflow flows from the indoor fan 4 to the air outlet 3, a gradually expanding channel is formed between the two planes. The minimum distance area serves as an airflow acceleration zone, guiding the airflow to diffuse evenly along the heat exchanger surface. This distance range avoids airflow obstruction due to excessive distance and also prevents airflow separation and the formation of vortex zones due to excessive distance.

[0071] Limiting the minimum distance H1 between the first and second planes to 12-20mm provides a smooth flow channel for airflow between the two heat exchangers, avoiding increased wind resistance and airflow congestion caused by excessively narrow spacing, ensuring uniform airflow to improve heat exchange efficiency, and preventing excessively wide spacing from wasting internal space of the casing 1. This adapts to the miniaturized design requirements of the indoor unit 100, effectively improving the uniformity of airflow distribution between the two heat exchangers, reducing energy loss and noise generation during airflow, and preventing condensation and stagnation caused by excessively small spacing, thereby improving heat exchange efficiency and equipment operational stability.

[0072] In this application, reference is made to Figure 4 and Figure 5 The fourth point is defined as the point on the upper volute 610 closest to the first heat exchanger 510; the first direction is defined as the extension direction perpendicular to the thickness direction of the shell 1; and the fifth line is defined as the straight line passing through the fourth point and extending along the first direction. It can be understood that the fifth line is the extension line from the fourth point toward the air outlet 3, and the fifth line forms a fourth included angle α with the second line, where 41°≤α≤45°. The upper volute 610 may include a first plate 611 and a second plate 612. One end of the first plate 611 can be connected and fixed to the lower volute 620 by bolts, and the other end of the first plate 611 is connected to the second plate 612. The first plate 611 and the second plate 612 are integrally formed or sealed together to form an arc-shaped cavity structure. The two plates work together to form a semi-enclosed space adapted to the upper part of the indoor fan 4, which, together with the lower volute 620, constitutes a complete fan housing cavity. The first plate 611 can be a smoothly tapered arc plate, curving away from the indoor fan 4 and protruding outwards from the volute cavity, covering the upper 1 / 3-1 / 2 of the circumferential area of ​​the indoor fan 4. One end of the second plate 612 is sealed to the first plate 611, and the other end extends to the upper edge of the air outlet 3 of the fan volute 6, simultaneously serving the function of sealing and fixing with the housing 1, taking into account both airflow guidance and structural stability. The second plate 612 extends from the end connected to the first plate 611 towards the air outlet 650 of the volute. The second plate 612 can be inclined away from the top side plate of the housing 1, or it can be parallel to the horizontal direction, as long as it is ensured that the airflow, after being guided by the second plate 612, can reach the windward side of the first heat exchanger 510. It can be understood that the fourth point is located at the end of the second plate 612 near the first heat exchanger 510.

[0073] Thus, referring to Figure 8 , Figure 9 and Figure 10 This design ensures that the airflow outlet direction of the upper volute 610 is precisely matched with the windward side of the first heat exchanger 510. After the airflow is discharged from the upper side of the volute, it can flow to the first heat exchanger 510 at a reasonable angle, avoiding the airflow on the upper side from colliding with the airflow guided by the lower extension plate 630. The first included angle β corresponding to the lower volute 620 extension plate 630 works in conjunction to form a symmetrical airflow guiding structure, so that the airflow discharged from the upper and lower areas of the volute outlet 650 can flow to the first heat exchanger 510 at a reasonable angle, further improving the uniformity of the overall airflow in the duct, reducing local airflow impact and eddies, and reducing operating noise and energy consumption.

[0074] In this application, reference is made to Figure 4 and Figure 5The projection of the side of the second heat exchanger 520 away from the first heat exchanger 510 in the first section is defined as the sixth straight line; the projection of the bottom wall of the shell 1 in the first section is defined as the seventh straight line; the sixth straight line and the seventh straight line form a fifth included angle ε, and the sum of the third included angle and the fourth included angle is equal to the fifth included angle.

[0075] The side of the second heat exchanger 520 furthest from the first heat exchanger 510, i.e., the leeward side of the second heat exchanger 520, projects as a continuous inclined straight line in the first cross-section parallel to the height of the shell 1. This straight line extends upward from the lower end of the second heat exchanger 520 (where it abuts against the water receiving tray 7) to the upper end (near the top of the shell 1), exhibiting an overall inclined posture with the lower end closer to the air inlet 2 and the upper end farther from the air inlet 2, perfectly consistent with the actual inclination direction of the second heat exchanger 520. The projection of the bottom wall of the shell 1 in the first cross-section is also a straight line.

[0076] Reference Figure 9 and Figure 10 The sixth and seventh straight lines form a fifth included angle ε, which enables the inclined layout of the dual heat exchangers, the airflow guiding angle of the upper volute 610, and the bottom of the shell 1 to work together. After the airflow is discharged from the volute, it flows through the dual heat exchangers along a preset trajectory through the extension plate 630 and the upper airflow guide, reducing airflow boundary layer separation and flow loss. At the same time, it ensures that the installation layout of the heat exchangers and the duct structure are perfectly matched, improving the utilization rate of the internal space of the equipment.

[0077] If ε < δ + α, the tilt angle of the second heat exchanger 520 is too small, the leeward surface is too gentle, and the airflow will form a "backflow vortex" after passing through the second heat exchanger 520, which will increase wind resistance and reduce heat exchange efficiency. If ε > δ + α, the tilt angle of the second heat exchanger 520 is too large, the leeward surface is too steep, which will interfere with the top of the shell 1. At the same time, the airflow is prone to boundary layer separation on the leeward surface, which will aggravate turbulence loss and increase noise.

[0078] In this application, reference is made to Figure 4 and Figure 5 The indoor unit 100 of the air conditioner also includes a drip tray 7. When the air conditioner is cooling, water vapor in the air condenses into water droplets on the evaporator. The drip tray 7 can collect these water droplets and prevent them from dripping directly. The drip tray 7 is located below the indoor heat exchanger 5. The lower ends of the first heat exchanger 510 and the second heat exchanger 520 abut against the groove wall of the drip tray 7. The drip tray 7 is used to collect the condensate produced by the indoor heat exchanger 5. Along the direction extending from the air inlet 2 to the air outlet 3, the drip tray 7 extends towards the top wall of the casing 1. This ensures effective collection of condensate while avoiding obstruction of airflow.

[0079] The drip tray 7 can be configured as a U-shaped trough structure, located directly below the indoor heat exchanger 5, with the trough opening facing upwards and the trough wall height of 30-100mm to ensure sufficient condensate storage capacity. The drip tray 7 can be fixed to the bottom wall of the housing 1 by bolts or clips, and the top of the trough wall on the side of the drip tray 7 near the air outlet 3 should not exceed the bottom of the air outlet 3, meaning that the drip tray 7 is located in the area below the air outlet 3.

[0080] The inclined extension design of the water tray 7 is adapted to the layout of the heat exchanger. After the condensate drips from the heat exchanger surface onto the water tray 7, it can quickly flow to the water collection area under the action of gravity and inclined guidance, avoiding the condensate from stagnating in the tank. At the same time, the inclined structure reduces the contact area between the airflow and the water surface of the water tray 7, reduces the risk of the airflow tearing the water film, effectively prevents condensate from splashing, and improves the user experience.

[0081] Furthermore, refer to Figure 4 and Figure 5 A water storage tank 710 is also provided at one end of the water receiving pan 7 near the first heat exchanger 510. The water storage tank 710 is located between the first heat exchanger 510 and the second heat exchanger 520. The water storage tank 710 is used to collect the condensate in the water receiving pan 7, so as to facilitate the recycling and treatment of the condensate.

[0082] In this application, reference is made to Figure 4 and Figure 5 The projection of the water receiving tray 7 near the tank wall of the indoor heat exchanger 5 in the first cross section is defined as the eighth straight line; the eighth straight line and the seventh straight line form a sixth included angle θ, where 2°≤θ≤5°. In this embodiment, the sixth included angle can be 3°, that is, the included angle between the second heat exchanger 520 and the water receiving tray 7 can be the difference between the fifth included angle ε and the sixth included angle θ.

[0083] Limiting the sixth included angle to between 2° and 5° ensures that the tilt angle of the water collection tray 7 guarantees smooth flow of condensate while avoiding excessive space wastage or overflow due to excessively rapid condensate flow, thus ensuring efficient condensate collection. If θ < 2°, the bottom of the tank is tilted too gently, resulting in insufficient condensate flow velocity and potential stagnation within the tank, which could lead to overflow over time. If θ > 5°, the tank wall is tilted too steeply, causing excessively rapid condensate flow that may impact the tank wall and cause splashing. This also increases the longitudinal space occupied by the water collection tray 7, resulting in wasted internal space within the casing 1.

[0084] Although the invention has been described with reference to several typical embodiments, it should be understood that the terminology used is illustrative and exemplary, and not restrictive. Since the invention can be embodied in many forms without departing from the spirit or essence of the invention, it should be understood that the above embodiments are not limited to any of the foregoing details, but should be interpreted broadly within the spirit and scope defined by the appended claims. Therefore, all variations and modifications falling within the scope of the claims or their equivalents should be covered by the appended claims.

Claims

1. An indoor unit for an air conditioner, characterized in that, include: A housing, wherein an air duct is formed inside the housing, and an air inlet and an air outlet communicating with the air duct are provided on the housing. The thickness direction of the housing is defined from the front side to the rear side of the housing, and the height direction of the housing is defined from the top wall to the bottom wall of the housing. An indoor fan is installed inside the air duct and on the side closest to the air inlet; An indoor heat exchanger is disposed within the housing and on the side of the indoor fan away from the air inlet; the indoor heat exchanger includes: The first heat exchanger is arranged to extend away from the air outlet along the height direction of the shell. The second heat exchanger is disposed on the side of the first heat exchanger near the air outlet, and extends away from the air outlet along the height direction of the shell. Fan casing, wherein the indoor fan is disposed within the fan casing; comprising: The upper volute is located on the side of the indoor fan near the top of the housing; The lower volute is located on the side of the indoor fan near the bottom of the housing, and the upper volute and the lower volute form a volute outlet that communicates with the air outlet. An extension plate is provided at one end of the lower volute near the indoor heat exchanger, and the extension plate extends toward the air outlet along the height direction of the casing. The section perpendicular to the thickness direction of the shell is defined as the first section, the projection of the extension plate onto the first section is defined as the first straight line, the projection of the first heat exchanger on the side closer to the indoor fan is defined as the second straight line, and there is a first included angle β between the extension of the first straight line and the second straight line, where 90°≤β≤105°.

2. The indoor unit of the air conditioner according to claim 1, characterized in that, The lower volute includes: A first enclosure panel, one end of which is connected to the extension panel; A second enclosure, one end of which is connected to the other end of the first enclosure, extends from one end near the top of the housing to one end near the bottom of the housing; The third enclosure has one end connected to the second enclosure and the other end connected to the upper volute. The indoor fan is at least partially located within the area enclosed by the first enclosure, the second enclosure, and the third enclosure. The projection of the second enclosure plate into the first section is defined as a third straight line, and there is a second included angle γ between the third straight line and the first straight line, where 47°≤γ≤57°.

3. The indoor unit of the air conditioner according to claim 1, characterized in that, The point closest to the first heat exchanger on the extension plate is defined as the first point, and the point furthest from the air outlet on the side of the first heat exchanger closest to the indoor fan is defined as the second point. The extension direction perpendicular to the thickness direction of the shell is defined as the first direction; The distance between the first point and the second point along the first direction is a first distance M, and the first distance M is not less than 50mm.

4. The indoor unit of the air conditioner according to claim 3, characterized in that, The line that passes through the second point and extends along the first direction is defined as the fourth line; The intersection of the extension of the first line and the fourth line is defined as the third point; The distance between the first point and the third point along the first direction is the second distance N; The first distance M is not greater than the second distance N.

5. The indoor unit of the air conditioner according to claim 1, characterized in that, The side of the first heat exchanger closest to the second heat exchanger is defined as the first plane, and the side of the second heat exchanger closest to the first heat exchanger is defined as the second plane. The first plane and the second plane form a third included angle δ, where 1.5°≤δ≤2.5°.

6. The indoor unit of the air conditioner according to claim 5, characterized in that, The minimum distance between the first plane and the second plane is the third distance H1. .

7. The indoor unit of the air conditioner according to claim 5, characterized in that, The point closest to the first heat exchanger on the upper volute is defined as the fourth point; the extension direction perpendicular to the thickness direction of the shell is defined as the first direction; The line that passes through the fourth point and extends along the first direction is defined as the fifth line; The fifth line and the second line form a fourth included angle α, where 41°≤α≤45°.

8. The indoor unit of the air conditioner according to claim 7, characterized in that, The side of the second heat exchanger furthest from the first heat exchanger is defined as the sixth straight line in the first cross section. The projection of the bottom wall of the shell into the first cross section is defined as the seventh straight line; The sixth line and the seventh line form a fifth included angle ε, and the sum of the third included angle and the fourth included angle is equal to the fifth included angle.

9. The indoor unit of the air conditioner according to claim 8, characterized in that, The indoor unit of the air conditioner also includes a water drip tray; The water receiving tray is located below the indoor heat exchanger. The lower ends of the first heat exchanger and the second heat exchanger are both in contact with the groove wall of the water receiving tray. The water receiving tray is used to receive the condensate generated by the indoor heat exchanger. Along the direction extending from the air inlet to the air outlet, the water receiving tray extends toward the top wall of the housing.

10. The indoor unit of the air conditioner according to claim 9, characterized in that, The projection of the water receiving tray near the indoor heat exchanger's groove wall into the first cross section is defined as the eighth straight line; The sixth included angle θ is formed between the eighth line and the seventh line, where 2°≤θ≤5°.

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