Wall-mounted air conditioner indoor unit

Abstract

The application discloses a wall-mounted air conditioner indoor unit, which comprises a shell, a fresh air module, a fresh air volute and a fresh air impeller. The fresh air impeller comprises a hub, a reinforcing disc connected to the hub and coaxially arranged with the hub, a first surface and a second surface of the reinforcing disc along the axial direction of the fresh air impeller, a plurality of first blades connected to the first surface of the reinforcing disc and arranged at intervals along the circumferential direction of the fresh air impeller, a plurality of second blades connected to the second surface of the reinforcing disc and arranged at intervals along the circumferential direction of the fresh air impeller, and a driving motor connected to the hub to drive the fresh air impeller to rotate. The ratio of the diameter of the circle where the outer edge of the reinforcing disc is located to the diameter of the circle where the air outlet end of the plurality of first blades is located is 0.78-0.87. The scheme can enhance the structural strength of the fresh air impeller and improve the air outlet efficiency of the fresh air impeller.

Description

Technical Field

[0001] This application relates to the field of air conditioning equipment technology, and in particular to a wall-mounted air conditioning indoor unit. Background Technology

[0002] An air conditioner, also known as an air conditioner, is a device that uses artificial means to regulate and control parameters such as temperature, humidity, and airflow of the air inside a building or structure.

[0003] Currently, more and more people are choosing to install air conditioners indoors to regulate the temperature of the indoor air. Wall-mounted air conditioners are one type of air conditioner, and the fresh air module of the indoor unit can draw fresh outdoor air into the room through a fresh air impeller.

[0004] In the prior art, the centrifugal fan in the fresh air module of a wall-mounted air conditioner has a reinforcing disc between two sets of blades to enhance the overall structural strength of the centrifugal fan. However, the diameter of the reinforcing disc affects the airflow state between the blades, resulting in a reduction in the efficiency of the centrifugal fan. Utility Model Content

[0005] This application discloses a wall-mounted air conditioner indoor unit that can ensure the structural strength of the fresh air impeller and improve the air output efficiency of the fresh air impeller.

[0006] To achieve the above objectives, some embodiments of this application provide a wall-mounted air conditioner indoor unit, comprising: a casing; a fresh air module disposed within the casing, the fresh air module comprising: a housing, the housing having a fresh air inlet; a fresh air volute connected to the housing, the inlet of the fresh air volute communicating with the fresh air inlet; a fresh air impeller disposed within the fresh air volute, the fresh air impeller being used to draw in outdoor fresh air and blow the fresh air into the room through the outlet of the fresh air volute, the fresh air impeller comprising: a hub; a reinforcing disc connected to the hub and coaxially arranged with the hub, the reinforcing disc having a first surface and a second surface along the axial direction of the fresh air impeller; and multiple A plurality of first blades are connected to the first surface of the reinforcing disk and are spaced apart circumferentially along the fresh air impeller; a plurality of second blades are connected to the second surface of the reinforcing disk and are spaced apart circumferentially along the fresh air impeller, wherein the diameter R2 of the circumference where the air outlet end of the plurality of first blades is located is equal to the diameter of the circumference where the air outlet end of the plurality of second blades is located; a drive motor is connected to the hub to drive the fresh air impeller to rotate; wherein the ratio of the diameter R1 of the circumference where the outer edge of the reinforcing disk is located to the diameter R2 of the circumference where the air outlet end of the plurality of first blades is located is 0.78 to 0.87.

[0007] In related technologies, an inappropriate setting of the diameter R1 of the circumference of the reinforcing disc of the fresh air impeller leads to a decrease in the air outlet efficiency when the impeller rotates. When the ratio of the diameter R1 of the circumference of the reinforcing disc to the diameter R2 of the circumference of the air outlet ends of the multiple first blades is less than 0.78, it means that the length of the first blade occupied by the reinforcing disc is too small. Since the first blades are connected to the first surface of the reinforcing disc, a small diameter of the reinforcing disc results in less connection between the first and second blades and the reinforcing disc, thereby reducing the structural strength of the first and second blades when the fresh air impeller rotates. Furthermore, the reinforcing disc also guides the airflow between two adjacent first blades or two adjacent second blades. A small diameter of the reinforcing disc weakens the guiding effect of the airflow, causing mutual interference between the airflow between two adjacent first blades and between two adjacent second blades in the axial direction of the fresh air impeller. This leads to unstable airflow and reduces the air outlet efficiency of the fresh air impeller. When the ratio of the diameter R1 of the circumference where the outer edge of the reinforcing disc is located to the diameter R2 of the circumference where the air outlet ends of the multiple first blades are located is greater than 0.87, it means that the diameter of the reinforcing disc is too large relative to the length of the first blades. In other words, the diameter of the reinforcing disc is too large, and the contact path between the airflow and the reinforcing disc between two adjacent first blades and two adjacent second blades becomes longer. This leads to an increase in the friction force exerted by the reinforcing disc on the airflow during the flow process, resulting in a large flow loss of airflow, affecting the air volume. Furthermore, the long-term friction between the airflow and the reinforcing disc will generate noise, leading to an increase in the noise level within the fresh air module.

[0008] In this embodiment, the ratio of the diameter R1 of the circumference of the outer edge of the reinforcing disk to the diameter R2 of the circumference of the air outlet of the multiple first blades is set to 0.78 to 0.87. This means that the diameter of the reinforcing disk relative to the diameter of the circumference of the air outlet of the first blades is within a suitable range. This avoids insufficient connection strength between the first and second blades due to an excessively small diameter of the reinforcing disk, ensuring stable airflow between adjacent first and second blades. It also avoids reduced airflow due to an excessively large diameter of the reinforcing disk, thus reducing the noise level during the operation of the fresh air module. This ensures the structural strength of the fresh air impeller and improves its air outlet efficiency.

[0009] In some embodiments of this application, the ratio of the diameter R1 of the circumference of the outer edge of the reinforcing disc to the diameter R2 of the circumference of the air outlet end of the plurality of first blades is 0.825.

[0010] Thus, when the ratio of the diameter of the outer edge of the reinforcing disc to the diameter of the circumference of the outlet of the multiple first blades is 0.825, it not only enhances the structural strength of the first and second blades, preventing them from deforming and tearing, but also improves the guiding effect of the reinforcing disc on the airflow between two adjacent first blades and two adjacent second blades. This ensures the stability of the airflow between two adjacent first blades and two adjacent second blades, thereby improving the air volume and efficiency of the fresh air impeller.

[0011] In some embodiments of this application, along the axial direction of the fresh air impeller, the ratio of the minimum width L1 of the plurality of second blades to the minimum width L2 of the plurality of first blades is one-third to one.

[0012] Thus, by setting the ratio of the minimum width L1 of multiple second blades to the minimum width L2 of multiple first blades to one-third to one, the secondary flow phenomenon between multiple second blades when the fresh air impeller rotates is reduced, ensuring smooth airflow between multiple second blades, reducing the airflow impact force on the first blades, and reducing the difference in pressure pulsation amplitude between the first and second blades, the noise generated when the fresh air impeller rotates is also reduced.

[0013] In some embodiments of this application, there is a gap between two adjacent first blades, and the second blade corresponds to the gap along the axial direction of the fresh air impeller.

[0014] In related technologies, one of the multiple first blades corresponds axially to one of the multiple second blades of the fresh air impeller. This results in the airflow between two adjacent first blades and the airflow between two adjacent second blades reaching the inner wall of the fresh air volute at the same time when the fresh air impeller rotates. The noise from the two airflows is superimposed, leading to a high noise level during the operation of the fresh air module and affecting the user experience.

[0015] In this embodiment, by setting a second blade corresponding to the gap between two adjacent first blades, the first and second blades are offset axially in the fresh air impeller. This results in different arrival times for the airflow from between two adjacent first blades and between two adjacent second blades on the wall of the fresh air volute. Consequently, the frequencies of the noise generated by the two airflows impacting the wall of the fresh air volute are opposite at their peaks and troughs in the same phase. This causes the frequencies of the noise generated by the two airflows to cancel each other out, reducing the frequency of the noise and making it more even, thus reducing the noise of the fresh air module operation.

[0016] In some embodiments of this application, the number of the plurality of first blades is the same as the number of the plurality of second blades.

[0017] In this way, by setting the number of first blades and second blades to be the same, it is ensured that the airflow can be drawn in and discharged evenly from both sides when the fresh air impeller rotates, avoiding airflow deviation and asymmetry caused by the difference in the number of blades.

[0018] In some embodiments of this application, the plurality of first blades and the plurality of second blades are all forward-curved blades; or, the plurality of first blades and the plurality of second blades are all backward-curved blades; or, the plurality of first blades and the plurality of second blades are all radial blades.

[0019] Thus, the forward-curved blades bend in the same direction as the rotation of the fresh air impeller, allowing the blades to do work on the airflow during rotation, increasing the airflow's kinetic energy and pressure. When the fresh air impeller rotates, the forward-curved blades not only draw airflow in from the inlet but also, guided by the blades, cause a superposition of centrifugal and axial motions in the airflow. This motion results in high velocity and pressure energy in the airflow before it enters the fresh air volute, helping to overcome the pressure difference between indoors and outdoors and more forcefully blowing fresh air into the room. The backward-curved blades bend in the opposite direction to the rotation of the fresh air impeller, allowing the impeller to utilize the airflow's kinetic energy more effectively during rotation, improving the impeller's efficiency. The backward-curved blades also cause the airflow's velocity direction when leaving the blades to form a certain angle with the tangential direction of the fresh air impeller, converting part of the airflow's kinetic energy into pressure energy. The radial blades have a simpler shape, extending radially along the fresh air impeller, making their manufacturing and installation relatively easy. This structure reduces manufacturing costs and production cycle. Furthermore, the radial blade fresh air impeller has high symmetry and more uniform gravity distribution, which can reduce the amount of runout when the fresh air impeller rotates, making the rotation more stable.

[0020] In some embodiments of this application, the fresh air impeller further includes:

[0021] A connecting ring is attached to the side of the plurality of first blades away from the first surface at the air outlet end.

[0022] Thus, on the one hand, the connecting ring connects the outlet ends of multiple first blades together, forming an integral frame structure. This strengthens the mutual support and connection strength between the first blades, enabling them to better resist centrifugal force during high-speed rotation and reducing the risk of deformation and damage. On the other hand, the tight connection between the connecting ring and the outlet ends of the first blades effectively reduces airflow leakage at these outlets. Without the connecting ring, airflow might leak along the axial direction of the fresh air impeller through the gaps at the outlet ends of the first blades, reducing the efficiency of fresh air delivery. The presence of the connecting ring blocks leakage paths, allowing airflow to be delivered indoors more efficiently, thereby improving the efficiency of fresh air delivery.

[0023] In some embodiments of this application, a motor housing cavity is formed inside the hub, and at least a portion of the drive motor is located inside the motor housing cavity; the air inlet ends of the plurality of first blades are spaced apart from the hub along the radial direction of the fresh air impeller, and the air inlet ends of the plurality of second blades are spaced apart from the hub along the radial direction of the fresh air impeller; the reinforcing disk is provided with heat dissipation holes, which penetrate the reinforcing disk along the axial direction of the fresh air impeller and are located at the intervals.

[0024] Thus, the heat dissipation holes on the reinforcing plate extend along the axial direction of the fresh air impeller and are located at intervals, providing an effective channel for heat dissipation from the motor housing. As the fresh air impeller rotates, airflow can carry away the heat generated during the operation of the drive motor through the heat dissipation holes, reducing the drive motor's temperature and improving its heat dissipation efficiency. Good heat dissipation performance helps extend the service life of the drive motor. Operating the motor at a lower temperature reduces the rate of insulation aging in the motor windings, lowers the risk of motor failure, and ensures long-term stable operation of the fresh air module.

[0025] In some embodiments of this application, there are multiple heat dissipation holes, which are arranged at intervals around the motor housing cavity along the circumference of the hub.

[0026] In this way, multiple heat dissipation holes are arranged at intervals around the motor housing cavity along the circumference of the hub, significantly increasing the heat dissipation area. Compared to a single or fewer heat dissipation holes, this arrangement allows the heat generated by the motor during operation to dissipate through more paths.

[0027] In some embodiments of this application, along the axial direction of the fresh air impeller, the width of the plurality of first blades near the air outlet end of the first blade is greater than the width of the plurality of first blades near the air inlet end of the first blade, and the width of the plurality of second blades is uniform.

[0028] Thus, the variation in the width of the first blade allows for a more uniform distribution of airflow within the fresh air impeller. A wider outlet allows for more even diffusion of airflow throughout the entire outlet area of ​​the fresh air impeller, preventing excessive concentration or dispersion of airflow at the outlet. This helps improve the uniformity of indoor air quality, enabling fresh air to diffuse more evenly to every corner of the room. Meanwhile, the uniform width of the second blade provides continuous and stable guidance and acceleration of the airflow. The uniform width of the second blade ensures that the airflow experiences a uniform force as it passes through the blade channel, resulting in a more even distribution of airflow speed and pressure. Attached Figure Description

[0029] To more clearly illustrate the technical solutions in the embodiments of this application, the drawings used in the embodiments will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this application. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0030] Figure 1 This is a schematic diagram of the structure of the wall-mounted air conditioner indoor unit disclosed in an embodiment of this application from one perspective;

[0031] Figure 2 This is a schematic diagram of the structure of the fresh air module disclosed in the embodiments of this application;

[0032] Figure 3 This is a front view of the fresh air module disclosed in the embodiments of this application;

[0033] Figure 4 for Figure 3 Sectional view at point AA;

[0034] Figure 5 This is a schematic diagram of the structure of the fresh air impeller disclosed in an embodiment of this application from one perspective;

[0035] Figure 6 This is a schematic diagram of the structure of the fresh air impeller disclosed in an embodiment of this application from another perspective;

[0036] Figure 7 This is a side view of the fresh air impeller disclosed in an embodiment of this application;

[0037] Figure 8 for Figure 7 Sectional view at point BB;

[0038] Figure 9 This is a front view of the fresh air impeller disclosed in an embodiment of this application.

[0039] Explanation of reference numerals in the attached figures:

[0040] 100-Wall-mounted air conditioner indoor unit;

[0041] 1-Casing;

[0042] 2-Fresh air module; 21-Housing; 21a-Fresh air inlet; 22-Fresh air volute; 23-Fresh air impeller; 231-Hub; 231a-Motor housing cavity; 232-Reinforcing disc; 232a-Heat dissipation hole; 2321-First surface; 2322-Second surface; 233-First blade; 234-Second blade; 235-Connecting ring; 24-Drive motor. Detailed Implementation

[0043] The technical solutions of the embodiments of this application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this application, and not all embodiments. Based on the embodiments of this application, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this application.

[0044] In this application, the terms "upper," "lower," "left," "right," "front," "rear," "top," "bottom," "inner," "outer," "vertical," "horizontal," "lateral," and "longitudinal" indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. These terms are primarily for the purpose of better describing this application and its embodiments, and are not intended to limit the indicated device, element, or component to having a specific orientation, or to be constructed and operated in a specific orientation.

[0045] Furthermore, in addition to indicating location or positional relationship, some of the aforementioned terms may also have other meanings. For example, the term "above" may also be used in some cases to indicate a certain dependency or connection relationship. Those skilled in the art can understand the specific meaning of these terms in this application based on the specific circumstances.

[0046] Furthermore, the terms "installation," "setup," "equipped with," "connection," and "linked" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral structure; 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, or an internal connection between two devices, components, or parts. Those skilled in the art can understand the specific meaning of these terms in this application based on the specific circumstances.

[0047] Furthermore, the terms "first," "second," etc., are primarily used to distinguish different devices, elements, or components (which may be the same or different in specific type and construction), and are not intended to indicate or imply the relative importance or quantity of the indicated devices, elements, or components. Unless otherwise stated, "a plurality of" means two or more.

[0048] The field of home appliance technology encompasses a wide range of product categories, including but not limited to refrigerators, washing machines, air conditioners, microwave ovens, dishwashers, and vacuum cleaners. The technological development trends for these products primarily focus on intelligentization, energy conservation and environmental protection, optimized user experience, and the application of new materials. Optimized user experience is achieved through design innovation and functional enhancement to meet consumers' demands for health, convenience, and personalization.

[0049] As an important branch of home appliances, wall-mounted air conditioner indoor units can introduce fresh outdoor air into the room through the fresh air impeller, replenishing the living environment with fresh, filtered outdoor air in real time, so that people can breathe fresh, oxygen-rich, and high-quality air indoors.

[0050] In related technologies, the fresh air impeller of the fresh air module is reinforced by setting a reinforcing disc to strengthen the structural strength of the entire fresh air impeller. In order to ensure its structural strength, the diameter of the circumference of the outer edge of the reinforcing disc is larger than the diameter of the circumference of the air outlet end of the blade of the fresh air impeller. This causes the airflow between the blades to rub against the reinforcing disc, resulting in the airflow being subjected to additional frictional force from the reinforcing disc. Consequently, the airflow outlet efficiency of the fresh air impeller is poor, and the friction between the airflow and the reinforcing disc over a long period of time will also generate frictional noise.

[0051] Based on this, this application provides a wall-mounted air conditioner indoor unit that can ensure the structural strength of the fresh air impeller and improve the air output efficiency of the fresh air impeller.

[0052] The present technical solution will be further described below with reference to the embodiments and accompanying drawings.

[0053] Please see Figure 1 This application provides a wall-mounted air conditioner indoor unit 100, which includes a housing 1. The housing 1 houses various functional components of the wall-mounted air conditioner indoor unit 100, such as a fan and a heat exchanger. These components, in conjunction with the outdoor unit of the air conditioner, can improve the indoor air environment, including cooling, heating, and humidity control.

[0054] like Figure 2 and Figure 3 As shown, the wall-mounted air conditioner indoor unit 100 also includes a fresh air module 2, which is installed inside the casing 1 and is used to introduce fresh air from the outside into the room.

[0055] The fresh air module 2 includes a housing 21, which has a fresh air inlet 21a. The housing 21 is usually equipped with filters such as filters and HEPA filters so that the fresh air entering the housing 21 through the fresh air inlet 21a can be filtered.

[0056] The fresh air module 2 also includes a fresh air volute 22, which is connected to the housing 21, and the air inlet of the fresh air volute 22 is connected to the fresh air inlet 21a.

[0057] like Figure 4 As shown, the fresh air module 2 also includes a fresh air impeller 23, which is disposed inside the fresh air volute 22. The fresh air impeller 23 is used to draw in fresh air from the outside and blow the fresh air into the room through the air outlet of the fresh air volute 22.

[0058] like Figure 5 As shown, the fresh air impeller 23 includes a hub 231, which is the main structure of the fresh air impeller 23.

[0059] The fresh air impeller 23 also includes a reinforcing disc 232, which is connected to the hub 231 and is coaxially arranged with the hub 231. The reinforcing disc 232 has a first surface 2321 and a second surface 2322 along the axial direction of the fresh air impeller 23.

[0060] like Figure 5 As shown, the fresh air impeller 23 also includes a plurality of first blades 233, which are connected to the first surface 2321 of the reinforcing disk 232, and the plurality of first blades 233 are arranged at intervals along the circumference of the fresh air impeller 23.

[0061] like Figure 6 As shown, the fresh air impeller 23 also includes a plurality of second blades 234. The plurality of second blades 234 are connected to the second surface 2322 of the reinforcing disk 232, and the plurality of second blades 234 are arranged at intervals along the circumference of the fresh air impeller 23. The diameter of the circumference of the air outlet end of the plurality of first blades 233 is equal to the diameter of the circumference of the air outlet end of the plurality of second blades 234.

[0062] It should be noted that the air outlet end of the first blade 233 and the air outlet end of the second blade 234 refer to the ends of the first blade 233 and the second blade 234 that are far away from the hub 231 along the radial direction of the fresh air impeller 23, that is, the ends that are far away from the hub 231 along the length direction of the first blade 233 and the second blade 234.

[0063] like Figure 3 As shown, the fresh air module 2 also includes a drive motor 24, which is connected to the hub 231 of the fresh air impeller 23 to drive the fresh air impeller 23 to rotate.

[0064] Among them, such as Figure 8 As shown, the ratio of the diameter R1 of the circumference of the outer edge of the reinforcing disc 232 to the diameter R2 of the circumference of the air outlet of the plurality of first blades 233 is 0.78 to 0.87.

[0065] It should be noted that if the reinforcing disc 232 is circular, the diameter of the circumference of the outer edge of the reinforcing disc 232 is the diameter of the reinforcing disc 232. If the reinforcing disc 232 is not circular, the diameter of the circumference of the outer edge of the reinforcing disc 232 is the diameter of the circumference formed by connecting the outer edges of the reinforcing disc 232.

[0066] The ratio of the diameter R1 of the circumference of the outer edge of the reinforcing disc 232 to the diameter R2 of the circumference of the air outlet ends of the multiple first blades 233 indicates the length of the first blades 233 occupied by the reinforcing disc 232. The diameter of the circumference of the air outlet ends of the multiple first blades 233 is equal to the diameter of the circumference of the air outlet ends of the multiple second blades 234, meaning that the length of the first blades 233 is the same as the length of the second blades 234. In other words, the length of the first blade 233 occupied by the reinforcing disc 232 is the same as the length of the second blade 234 occupied by the reinforcing disc 232.

[0067] In related technologies, the diameter R1 of the circumference of the reinforcing disk 232 of the fresh air impeller 23 is not set properly, which leads to a decrease in the air output efficiency when the fresh air impeller 23 rotates. When the ratio of the diameter R1 of the circumference where the outer edge of the reinforcing disk 232 is located to the diameter R2 of the circumference where the air outlet ends of the multiple first blades 233 are located is less than 0.78, it means that the length of the first blade 233 occupied by the reinforcing disk 232 is too small. Since the first blade 233 is connected to the first surface of the reinforcing disk 232, the small diameter of the reinforcing disk 232 results in less connection between the first blade 233 and the second blade 234 and the reinforcing disk 232, thereby reducing the structural strength of the first blade 233 and the second blade 234 when the fresh air impeller 23 rotates. Furthermore, the reinforcing disk 232 also guides the airflow between two adjacent first blades 233 or two adjacent second blades 234. The small diameter of the reinforcing disk 232 weakens its guiding effect on the airflow, which causes the airflow between two adjacent first blades 233 and between two adjacent second blades 234 to interfere with each other in the axial direction of the fresh air impeller 23, resulting in unstable airflow and reduced air outlet efficiency of the fresh air impeller 23. When the ratio of the diameter R1 of the circumference where the outer edge of the reinforcing disk 232 is located to the diameter R2 of the circumference where the air outlet ends of the multiple first blades 233 are located is greater than 0.87, it means that the diameter of the reinforcing disk 232 is too large relative to the length of the first blades 233. In other words, the diameter of the reinforcing disk 232 is too large, and the contact path between the airflow and the reinforcing disk 232 between two adjacent first blades 233 and two adjacent second blades 234 becomes longer. This results in an increase in the frictional force of the airflow on the reinforcing disk 232 during the flow process, which in turn causes a large flow loss of airflow, affecting the air volume. Furthermore, the long-term friction between the airflow and the reinforcing disk 232 will generate noise, leading to an increase in the noise level in the fresh air module 2.

[0068] In this embodiment, the ratio of the diameter R1 of the circumference of the outer edge of the reinforcing disk 232 to the diameter R2 of the circumference of the air outlet of the multiple first blades 233 is set to 0.78 to 0.87. This means that the diameter of the reinforcing disk 232 relative to the diameter of the circumference of the air outlet of the first blades 233 is within a suitable range. This avoids insufficient connection strength between the first blades 233 and the second blades 234 due to an excessively small diameter of the reinforcing disk 232, ensuring stable airflow between adjacent first blades 233 and adjacent second blades 234. It also avoids reduced airflow due to an excessively large diameter of the reinforcing disk 232, thus reducing the noise level of the fresh air module 2 during operation. This ensures the structural strength of the fresh air impeller 23 and improves its air outlet efficiency.

[0069] Specifically, the ratio of the diameter R1 of the circumference of the outer edge of the reinforcing disc 232 to the diameter R2 of the circumference of the air outlet of the plurality of first blades 233 can be 0.78, 0.8, 0.82, 0.84, 0.86 or 0.87.

[0070] In some embodiments, such as Figure 8 As shown, the ratio of the diameter R1 of the circumference of the outer edge of the reinforcing disk 232 to the diameter R2 of the circumference of the air outlet of the multiple first blades 233 is 0.825. When the ratio of the diameter R1 of the circumference of the outer edge of the reinforcing disk 232 to the diameter R2 of the circumference of the air outlet of the multiple first blades 233 is 0.825, it not only enhances the structural strength of the first blades 233 and the second blades 234, preventing the first blades 233 and the second blades 234 from deforming and tearing, but also makes the reinforcing disk 232 better guide the airflow between two adjacent first blades 233 and two adjacent second blades 234, ensuring the stability of the airflow between two adjacent first blades 233 and two adjacent second blades 234, and improving the air volume and air efficiency of the fresh air impeller 23.

[0071] In some embodiments, such as Figure 7 As shown, along the axial direction of the fresh air impeller 23, the ratio of the minimum width L1 of the plurality of second blades 234 to the minimum width L2 of the plurality of first blades 233 is one-third to one.

[0072] It should be noted that the width L2 of each first blade 233 is the same, and the width L1 of each second blade 234 is the same. The minimum width L2 of the first blade 233 and the minimum width L1 of the second blade 234 refer to the minimum value of the first blade 233 and the second blade 234 when the width of the first blade 233 or the second blade 234 is changing. When the width of the first blade 233 or the second blade 234 is constant, the minimum width of the first blade 233 and the second blade 234 is the width of the first blade 233 and the second blade 234.

[0073] In this embodiment, the width of the first blade 233 is variable, while the width of the second blade 234 is constant. Of course, the width of the first blade 233 can be constant, while the width of the second blade 234 can be variable, or both the width of the first blade 233 and the width of the second blade 234 can be variable or constant. This embodiment does not specifically limit this.

[0074] The axial position of the reinforcing disc 232 on the fresh air impeller 23 is determined by the ratio of the minimum width L1 of the second blade 234 to the minimum width L2 of the first blade 233.

[0075] If the ratio of the minimum width L1 of the multiple second blades 234 to the minimum width L2 of the multiple first blades 233 along the axial direction of the fresh air impeller 23 is less than one-third, it means that the ratio of the width of the second blades 234 on one side of the second surface 2322 of the reinforcing disk 232 to the total thickness of the fresh air impeller 23 is less than one-quarter. The thickness of the fresh air impeller 23 on one side of the second surface 2322 of the reinforcing disk 232 is too small. This will cause a secondary flow phenomenon between the second blades 234 when the fresh air impeller 23 rotates, resulting in airflow blockage between the multiple second blades 234. Consequently, the multiple second blades 234 cannot smoothly discharge air, reducing the overall air volume of the fresh air impeller 23.

[0076] If the ratio of the minimum width L1 of the multiple second blades 234 to the minimum width L2 of the multiple first blades 233 along the axial direction of the fresh air impeller 23 is greater than one, it means that the ratio of the width of the second blades 234 on one side of the second surface 2322 of the reinforcing disk 232 to the total thickness of the fresh air impeller 23 is greater than one-half. The thickness of the fresh air impeller 23 on one side of the second surface 2322 of the reinforcing disk 232 is too large, while the thickness of the fresh air impeller 23 on one side of the first surface 2321 of the reinforcing disk 232 is too small. This results in a large airflow impact force on the first blades 233 when the fresh air impeller 23 rotates, and the difference in the pressure pulsation amplitude between the first blades 233 and the second blades 234 will also increase, causing noise problems.

[0077] Therefore, in this embodiment, by setting the ratio of the minimum width L1 of the multiple second blades 234 to the minimum width L2 of the multiple first blades 233 to one-third, the secondary flow phenomenon between the multiple second blades 234 is reduced when the fresh air impeller 23 rotates, ensuring smooth airflow between the multiple second blades 234, reducing the airflow impact force on the first blades 233, and reducing the difference in the pressure pulsation amplitude between the first blades 233 and the second blades 234, the noise generated when the fresh air impeller 23 rotates is also reduced.

[0078] In some embodiments, combined with Figure 8 and Figure 9 There is a gap M between two adjacent first blades 233, and the second blade 234 corresponds to the gap M along the axial direction of the fresh air impeller 23. That is to say, the multiple first blades 233 and multiple second blades 234 are arranged alternately along the circumference of the fresh air impeller 23, and one second blade 234 corresponds to the gap M between two adjacent first blades 233.

[0079] In related technologies, one of the multiple first blades 233 corresponds axially to one of the multiple second blades 234 of the fresh air impeller 23. This results in the airflow between two adjacent first blades 233 and between two adjacent second blades 234 reaching the inner wall of the fresh air volute 22 at the same time when the fresh air impeller 23 rotates. The noise from the two airflows is superimposed, leading to a high noise level during the operation of the fresh air module 2, which affects the user experience.

[0080] In this embodiment, by setting a second blade 234 corresponding to the gap M between two adjacent first blades 233, the first blades 233 and the second blades 234 are offset in the axial direction of the fresh air impeller 23. Thus, the airflow blowing from between two adjacent first blades 233 and the airflow blowing from between two adjacent second blades 234 reaches the wall of the fresh air volute 22 at different times. This causes the frequencies of the noise generated by the two airflows impacting the wall of the fresh air volute 22 to have opposite peaks and troughs in the same phase. Consequently, the frequencies of the noise generated by the two airflows cancel each other out, reducing the frequency of the noise and making it more even, thereby reducing the operating noise of the fresh air module 2.

[0081] In some embodiments, the number of the plurality of first blades 233 is the same as the number of the plurality of second blades 234. If the number of the plurality of first blades 233 is different from the number of the plurality of second blades 234, for example, if the number of first blades 233 is greater than the number of second blades 234, it will result in an uneven guiding and compression effect of the blades on both sides of the reinforcing disk 232 on the airflow. The first blades and second blades cannot be matched, and the corresponding amount of airflow cannot be effectively guided and accelerated. This will result in uneven distribution of airflow inside the fresh air impeller 23, affecting the uniformity of fresh air delivery.

[0082] Furthermore, the first blade 233 and the second blade 234 cause the airflow speed and direction inside the fresh air impeller 23 to be uncoordinated on both sides, which easily generates more airflow turbulence and eddy phenomena inside the fresh air impeller 23. This not only increases airflow resistance and reduces the energy utilization rate of the airflow, but also intensifies the collision and friction of the airflow inside the fresh air impeller 23, generating more noise.

[0083] In this embodiment, the number of multiple first blades 233 and multiple second blades 234 are the same, which ensures that the airflow can be evenly drawn in and discharged from both sides when the fresh air impeller 23 rotates, avoiding airflow deviation and asymmetry caused by the difference in the number of blades.

[0084] For example, when the fresh air impeller 23 rotates, the first blade 233 and the second blade 234 guide the airflow from both sides, causing the airflow to converge evenly in the central region of the impeller, forming a symmetrical airflow field. The symmetrical airflow distribution improves the stability of the airflow, making the airflow inside the fresh air impeller 23 smoother, reducing airflow fluctuations and turbulence, and helping to improve the uniformity and efficiency of fresh air delivery.

[0085] Furthermore, the equal number of first blades 233 and second blades 234 can uniformly compress and accelerate the airflow. When the fresh air impeller 23 rotates, the first blades 233 and second blades 234 compress and accelerate the airflow on both sides respectively, improving the energy utilization rate of the airflow and enabling more outdoor fresh air to be effectively delivered indoors.

[0086] In some embodiments, such as Figure 6 As shown, the multiple first blades 233 and the multiple second blades 234 are all forward-curved blades.

[0087] The forward-curved blades bend in the same direction as the rotation of the fresh air impeller 23, enabling the blades to perform work on the airflow during rotation, increasing the airflow's kinetic energy and pressure. When the fresh air impeller 23 rotates, the forward-curved blades not only draw airflow in from the inlet but also, guided by the blades, cause the airflow to undergo a superposition of centrifugal and axial motion. This motion mode gives the airflow high velocity and pressure energy before entering the fresh air volute 22, helping to overcome the pressure difference between indoors and outdoors and more powerfully blowing fresh air into the room.

[0088] In some embodiments, the plurality of first blades 233 and the plurality of second blades 234 are all backward-curved blades.

[0089] The backward-curved blades are curved in the opposite direction to the rotation of the fresh air impeller 23, which allows the fresh air impeller 23 to utilize the kinetic energy of the airflow more effectively during rotation, thus improving the efficiency of the fresh air impeller 23. The backward-curved blades cause the velocity direction of the airflow when it leaves the blades to form a certain angle with the tangential direction of the fresh air impeller 23, so that part of the kinetic energy of the airflow is converted into pressure energy.

[0090] In some embodiments, the plurality of first blades 233 and the plurality of second blades 234 are radial blades.

[0091] The radial blades have a relatively simple shape, extending radially along the fresh air impeller 23, making their manufacturing and installation relatively easy. This structure reduces manufacturing costs and production cycle. Furthermore, the radial blades of the fresh air impeller 23 have high symmetry and more uniform gravity distribution, which reduces the amount of runout during rotation, resulting in smoother rotation.

[0092] It should be noted that, in addition to the first blade 233 and the second blade 234 being the same type of blade as described in the above embodiments, the first blade 233 and the second blade 234 can also be configured as blades of different types, that is, the first blade 233 is a forward-curved blade and the second blade 234 is a radial blade or a backward-curved blade; or, the first blade 233 is a backward-curved blade and the second blade 234 is a forward-curved blade or a radial blade; or, the first blade 233 is a radial blade and the second blade 234 is a forward-curved blade or a backward-curved blade. This embodiment does not specifically limit this.

[0093] In some embodiments, such as Figure 5 As shown, the fresh air impeller 23 also includes a connecting ring 235, which is connected to the side of the first surface 2321 of the plurality of first blades 233 away from the air outlet end of the first blades 233.

[0094] On the one hand, the connecting ring 235 connects the outlet ends of multiple first blades 233 together, forming an integral frame structure. This strengthens the mutual support and connection strength between the first blades 233, enabling them to better resist centrifugal force during high-speed rotation and reducing the risk of deformation and damage. On the other hand, the tight connection between the connecting ring 235 and the outlet ends of the first blades 233 effectively reduces airflow leakage at these outlet ends. Without the connecting ring, airflow might leak along the axial direction of the fresh air impeller 23 from the gaps at the outlet ends of the first blades 233, reducing the fresh air delivery efficiency. The presence of the connecting ring 235 blocks the leakage path, allowing airflow to be delivered to the room more efficiently, thereby improving the fresh air delivery efficiency.

[0095] It should be noted that the connecting ring 235 can be a circular structure coaxial with the fresh air impeller 23. Its inner diameter is larger than the outer edge diameter R1 of the reinforcing disc, and its outer diameter is basically equal to or slightly smaller than the diameter R2 of the circumference of the air outlet end of the multiple first blades 233, so that the connecting ring 235 can be connected to the top of all the first blades 233 in a close fit.

[0096] The radial cross-sectional shape of the connecting ring 235 can be varied, such as rectangular, circular, elliptical, or aerodynamically optimized airfoil cross-sections. For example, Figure 8 As shown, the cross-section of the connecting ring 235 is circular to provide sufficient structural strength and facilitate manufacturing.

[0097] It should be noted that a connecting ring 235 can also be provided on the side of the air outlet end of the multiple second blades 234 away from the second surface 2322 of the reinforcing disk 232. This is similar to the function of the connecting ring 235 connecting the air outlet end of the first blade 233 to the side of the first surface 2321 away from the reinforcing disk 232. This embodiment will not be described in detail here.

[0098] In some embodiments, such as Figure 6 As shown, a motor receiving cavity 231a is formed inside the hub 231, and at least a portion of the drive motor 24 is located inside the motor receiving cavity 231a.

[0099] It should be noted that at least a portion of the drive motor 24 is located within the motor housing cavity 231a. This can be either a partial or complete installation of the drive motor 24 within the motor housing cavity 231a. Utilizing the space around the hub 231 to form the motor housing cavity 231a to accommodate the drive motor 24 saves space in the fresh air module 2, thus facilitating the miniaturization of the fresh air module 2.

[0100] like Figure 8As shown, the air inlet ends of multiple first blades 233 and hub 231 are spaced N apart along the radial direction of fresh air impeller 23, and the air inlet ends of multiple second blades 234 and hub 231 are spaced N apart along the radial direction of fresh air impeller 23.

[0101] The reinforcing disc 232 has heat dissipation holes 232a, which penetrate the reinforcing disc 232 along the axial direction of the fresh air impeller 23 and are located at interval N.

[0102] It should be noted that the air inlet ends of the first blade 233 and the second blade 234 are both the ends of the first blade 233 and the second blade 234 that are closer to the hub 231.

[0103] The heat dissipation holes 232a on the reinforcing plate 232 extend through the reinforcing plate 232 along the axial direction of the fresh air impeller 23 and are located at intervals N, providing an effective channel for heat dissipation within the motor housing 231a. When the fresh air impeller 23 rotates, airflow can carry away the heat generated during the operation of the drive motor 24 through the heat dissipation holes 232a, reducing the temperature of the drive motor 24 and improving its heat dissipation efficiency. Good heat dissipation performance helps extend the service life of the drive motor 24. Operating the motor at a lower temperature reduces the rate of insulation aging in the motor windings, lowers the risk of motor failure, and ensures the long-term stable operation of the fresh air module 2.

[0104] In some embodiments, such as Figure 9 As shown, there are multiple heat dissipation holes 232a on the reinforcing disc 232, and the multiple heat dissipation holes 232a are arranged at intervals around the motor housing cavity 231a along the circumference of the hub 231.

[0105] Multiple heat dissipation holes 232a are arranged at intervals around the motor housing cavity 231a along the circumference of the hub 231, significantly increasing the heat dissipation area. Compared to a single or fewer heat dissipation holes, this arrangement allows the heat generated during motor operation to dissipate through more paths. For example, when the drive motor 24 is running at high speed, internal components such as windings generate a large amount of heat. Multiple heat dissipation holes 232a allow this heat to be transferred to the surrounding environment more evenly, improving heat dissipation efficiency by approximately 30%-40% compared to having only one heat dissipation hole 232a.

[0106] Furthermore, the circumferentially arranged heat dissipation holes 232a can guide airflow to form an annular heat dissipation channel. When the fresh air impeller 23 rotates, the airflow enters from one end of the heat dissipation hole 232a, evenly carrying away and expelling the heat in the motor housing cavity 231a, ensuring that the overall temperature of the drive motor 24 drops evenly.

[0107] Furthermore, the spaced arrangement of multiple heat dissipation holes 232a makes the temperature field around the drive motor 24 more uniform. When the drive motor 24 is running, heat is dissipated from the motor housing cavity 231a to the surroundings. The multiple heat dissipation holes 232a are evenly distributed around the hub 231, making the heat dissipation conditions of the drive motor 24 consistent in all directions and avoiding local overheating of the motor due to uneven heat dissipation.

[0108] It should be noted that the multiple heat dissipation holes 232a can be four, five, six, or more; this embodiment does not specifically limit this. For example, as shown... Figure 9 As shown, there are 30 heat dissipation holes 232a.

[0109] In some embodiments, combined with Figure 5 and Figure 6 Along the axial direction of the fresh air impeller 23, the width of the multiple first blades 233 near their outlet ends is greater than the width of the multiple first blades 233 near their inlet ends, while the width of the multiple second blades 234 is uniform. The variation in the width of the first blades 233 allows for smoother airflow, reducing airflow rotation and eddy current generation. The uniform width of the second blades 234 also contributes to stable airflow and reduces energy loss.

[0110] The wider outlet width of the first blade 233 allows for more effective compression and acceleration of the airflow. As the airflow enters the fresh air impeller 23, the gradually widening width of the first blade 233 better guides the airflow, gradually increasing its speed and pressure as it passes through the channel between two adjacent first blades 233. This helps to draw in more outdoor fresh air and deliver it indoors through the fresh air impeller 23, thereby improving the fresh air delivery efficiency.

[0111] Furthermore, the varying width of the first blade 233 ensures a more uniform distribution of airflow within the fresh air impeller 23. A wider outlet allows for more even diffusion of airflow across the entire outlet area of ​​the fresh air impeller 23, preventing excessive concentration or dispersion of airflow at the outlet. This contributes to improved indoor air quality uniformity, enabling fresh air to diffuse more evenly to all corners of the room. The uniform width of the second blade 234 provides continuous and stable guidance and acceleration of the airflow. The uniform width of the second blade 234 ensures that the airflow experiences a uniform force as it passes through the blade channel, resulting in a more even distribution of airflow velocity and pressure.

[0112] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of this application, and are not intended to limit them. Although this application has been described in detail with reference to the foregoing embodiments, those skilled in the art should understand that modifications can still be made to the technical solutions described in the foregoing embodiments, or equivalent substitutions can be made to some or all of the technical features therein. Such modifications or substitutions do not cause the essence of the corresponding technical solutions to deviate from the scope of the technical solutions of the embodiments of this application.

Claims

1. A wall-mounted air conditioner indoor unit, characterized in that, include: chassis; A fresh air module is disposed within the housing, and the fresh air module includes: The housing is provided with a fresh air inlet; A fresh air volute is connected to the housing, and the air inlet of the fresh air volute is connected to the fresh air inlet. A fresh air impeller, disposed within the fresh air volute, is used to draw in outdoor fresh air and blow it into the room through the air outlet of the fresh air volute. The fresh air impeller includes: Wheel hub; A reinforcing disc is connected to the hub and is coaxially arranged with the hub. The reinforcing disc has a first surface and a second surface along the axial direction of the fresh air impeller. A plurality of first blades are connected to the first surface of the reinforcing disk, and the plurality of first blades are arranged at circumferential intervals along the fresh air impeller; Multiple second blades are connected to the second surface of the reinforcing disk, and the multiple second blades are spaced apart circumferentially along the fresh air impeller. The diameter R2 of the circumference where the air outlet end of the multiple first blades is located is equal to the diameter of the circumference where the air outlet end of the multiple second blades is located. A drive motor is connected to the hub to drive the fresh air impeller to rotate; The ratio of the diameter R1 of the outer edge of the reinforcing disc to the diameter R2 of the air outlet end of the plurality of first blades is 0.78 to 0.

87.

2. The wall-mounted air conditioner indoor unit according to claim 1, characterized in that, The ratio of the diameter R1 of the outer edge of the reinforcing disc to the diameter R2 of the air outlet of the plurality of first blades is 0.

825.

3. The wall-mounted air conditioner indoor unit according to claim 2, characterized in that, Along the axial direction of the fresh air impeller, the ratio of the minimum width L1 of the plurality of second blades to the minimum width L2 of the plurality of first blades is one-third to one.

4. The wall-mounted air conditioner indoor unit according to claim 1, characterized in that, There is a gap between two adjacent first blades, and the second blade corresponds to the gap along the axial direction of the fresh air impeller.

5. The wall-mounted air conditioner indoor unit according to claim 4, characterized in that, The number of the plurality of first blades is the same as the number of the plurality of second blades.

6. The wall-mounted air conditioner indoor unit according to claim 1, characterized in that, The plurality of first blades and the plurality of second blades are all forward-curved blades; Alternatively, both the plurality of first blades and the plurality of second blades may be backward-curved blades; Alternatively, both the plurality of first blades and the plurality of second blades may be radial blades.

7. The wall-mounted air conditioner indoor unit according to claim 1, characterized in that, The fresh air impeller also includes: A connecting ring is attached to the side of the plurality of first blades away from the first surface at the air outlet end.

8. The wall-mounted air conditioner indoor unit according to claim 1, characterized in that, A motor housing cavity is formed inside the wheel hub, and at least a portion of the drive motor is located inside the motor housing cavity; The air inlet ends of the plurality of first blades are spaced apart from the hub along the radial direction of the fresh air impeller, and the air inlet ends of the plurality of second blades are spaced apart from the hub along the radial direction of the fresh air impeller; The reinforcing disc has heat dissipation holes that extend through the reinforcing disc along the axial direction of the fresh air impeller and are located at the interval.

9. The wall-mounted air conditioner indoor unit according to claim 8, characterized in that, The heat dissipation holes are multiple, and the multiple heat dissipation holes are arranged at intervals around the motor housing cavity along the circumference of the hub.

10. The wall-mounted air conditioner indoor unit according to claim 1, characterized in that, Along the axial direction of the fresh air impeller, the width of the plurality of first blades near the air outlet end of the first blade is greater than the width of the plurality of first blades near the air inlet end of the first blade, and the width of the plurality of second blades is uniform.

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