Air conditioner

Abstract

The air conditioner comprises a machine shell, a fan assembly and a heat exchanger, an air inlet and an air outlet are formed in the machine shell, the fan assembly is arranged in the machine shell and comprises a volute and a wind wheel, an air supply duct is formed in the volute and provided with an airflow inlet and an airflow outlet, and the wind wheel is rotatably arranged on the volute. The heat exchanger is located between the air inlet and the fan assembly, an extension part is formed at at least one end, in the circumferential direction of the wind wheel, of the heat exchanger, in the thickness direction of the heat exchanger, the extension part and the outer wall face of the volute are oppositely arranged in a spaced mode and jointly define an induced air duct, and the induced air duct extends to the airflow inlet and communicates with the air supply duct through the airflow inlet. According to the air conditioner provided by the embodiment of the utility model, the heat exchange area of the heat exchanger can be increased through the extension part, and the air flow subjected to heat exchange through the extension part can participate in the temperature regulation of indoor air by the air conditioner through the air inducing duct, so that the refrigeration or refrigeration efficiency of the air conditioner is improved.

Description

Technical Field

[0001] This utility model relates to the field of air conditioning equipment technology, and in particular to an air conditioner. Background Technology

[0002] As people's living standards improve, air conditioners have gradually entered thousands of households, becoming an important household appliance. Furthermore, with the continuous development of the air conditioning industry, users' demands for air conditioners are also increasing. Among these demands, the contact area between the evaporator and the incoming airflow directly affects the heat exchange performance of the air conditioner. In related technologies, the two ends of the evaporator only cover the air inlet of the fan casing, thus limiting the heat exchange area of ​​the evaporator due to the area covered by the air inlet. Therefore, improvements are needed. Utility Model Content

[0003] This utility model proposes an air conditioner that has the advantage of increasing the heat exchange area of ​​the heat exchanger to improve cooling or heating efficiency.

[0004] An air conditioner according to an embodiment of the present invention includes: a housing having an air inlet and an air outlet; a fan assembly disposed within the housing and including a volute and a fan impeller, wherein an air supply duct is formed within the volute, the air supply duct having an air inlet and an air outlet, and the fan impeller being rotatably disposed within the volute; and a heat exchanger located between the air inlet and the fan assembly, wherein the heat exchanger has an extension formed at least at one end of the fan impeller in the circumferential direction, and in the thickness direction of the heat exchanger, the extension is opposite to and spaced apart from the outer wall surface of the volute, the extension and the outer wall surface of the volute together defining an induced draft duct, the induced draft duct extending to the air inlet and communicating with the air supply duct through the air inlet.

[0005] According to the embodiment of the present invention, the air conditioner can increase the circumferential size of the heat exchanger in the impeller by providing an extension on the heat exchanger, thereby increasing the heat exchange area of ​​the heat exchanger. By providing an air duct between the extension and the volute, the airflow passing through the extension can smoothly enter the air supply duct and be discharged through the air outlet. That is, it is ensured that the airflow after heat exchange through the extension can participate in the air conditioner's temperature regulation of the indoor air, thereby improving the air conditioner's cooling or cooling efficiency.

[0006] According to some embodiments of the present invention, the dimension of the air duct in the thickness direction of the heat exchanger is increased in the direction of approaching the airflow inlet.

[0007] According to some embodiments of the present invention, the dimension of the end of the air duct away from the airflow inlet in the thickness direction of the heat exchanger is in the range of 3mm-15mm; and / or, the dimension of the end of the air duct adjacent to the airflow inlet in the thickness direction of the heat exchanger is in the range of 10mm-30mm.

[0008] According to some embodiments of the present invention, the length of the air duct in the circumferential direction of the wind turbine is not less than 30 mm.

[0009] According to some embodiments of the present invention, the volute includes a rear volute tongue, and the extension is formed at one end of the heat exchanger near the rear volute tongue. The extension is located outside the rear volute tongue and together with the outer wall surface of the rear volute tongue defines a portion of the air duct.

[0010] According to some embodiments of this utility model, the wind turbine has multiple air dispersing channels arranged axially.

[0011] According to some embodiments of the present invention, the air diffuser structure is located at one end of the rear volute tongue near the airflow inlet.

[0012] According to some embodiments of this utility model, the distance between the air distribution structure and the airflow inlet is no more than 10mm.

[0013] According to some embodiments of the present invention, the air dissipation structure is spaced apart from the heat exchanger.

[0014] According to some embodiments of the present invention, the air dissipation structure includes multiple ribs extending along the axial direction of the impeller, and each rib has multiple air dissipation grooves arranged along the axial direction of the impeller on its side facing the heat exchanger. The multiple air dissipation grooves together constitute the air dissipation channel.

[0015] According to some embodiments of the present invention, the width of the end of the air duct adjacent to the airflow inlet in the thickness direction of the heat exchanger is L1, and the height of the air dispersing structure protruding from the outer wall of the rear volute tongue is L2. L1 and L2 satisfy: 1 / 3*L1≤L2≤2 / 3*L1.

[0016] According to some embodiments of the present invention, the air dispersing structure includes multiple ribs extending along the axial direction of the impeller, the air dispersing channel passes through the ribs along the extension direction of the air duct, the ribs are respectively a first side and a second side on opposite sides in the extension direction of the air duct, and the included angle between the first side and the second side and the outer wall surface of the rear volute tongue is in the range of 45°-135°.

[0017] According to some embodiments of this utility model, the air dissipation structure is integrally formed with the volute.

[0018] Additional aspects and advantages of this invention will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of the invention. Attached Figure Description

[0019] Figure 1 This is a schematic diagram of an air conditioner according to an embodiment of the present utility model;

[0020] Figure 2 This is a cross-sectional view of an air conditioner according to an embodiment of the present utility model;

[0021] Figure 3 yes Figure 2 Enlarged view of region A in the middle;

[0022] Figure 4 yes Figure 3 Enlarged view of region B in the middle;

[0023] Figure 5 This is a schematic diagram of the fan assembly of an air conditioner according to an embodiment of the present utility model;

[0024] Figure 6 yes Figure 5 Top view of the stroke unit components;

[0025] Figure 7 This is a schematic diagram of the volute and air distribution structure of an air conditioner according to Embodiment 1 of this utility model;

[0026] Figure 8 yes Figure 7 Enlarged view of region C in the middle;

[0027] Figure 9 This is a schematic diagram of the volute and air diffuser structure of an air conditioner according to Embodiment 2 of this utility model;

[0028] Figure 10 yes Figure 9 Enlarged view of region D in the middle;

[0029] Figure 11 This is a schematic diagram of the volute and air diffuser structure of an air conditioner according to Embodiment 3 of this utility model;

[0030] Figure 12 yes Figure 11 Enlarged view of region E in the middle;

[0031] Figure 13 This is a schematic diagram of the volute and air diffuser structure of an air conditioner according to Embodiment 4 of this utility model;

[0032] Figure 14 yes Figure 13 A magnified view of region F in the middle.

[0033] Figure label:

[0034] 100. Air conditioner;

[0035] 1. Housing; 11. Air inlet; 12. Air outlet;

[0036] 2. Fan assembly; 21. Volute; 211. Air supply duct; 212. Air inlet; 213. Air outlet; 214. Rear volute tongue; 22. Impeller; 23. Air diffusion structure; 231. Air diffusion channel; 232. Rib; 233. Air diffusion slot;

[0037] 3. Heat exchanger; 31. Extension section;

[0038] 4. Air intake duct; 5. Door opening and closing. Detailed Implementation

[0039] The following describes in detail embodiments of the present invention, examples of which are shown in the accompanying drawings, wherein the same or similar reference numerals throughout represent the same or similar elements or elements having the same or similar functions. The embodiments described below with reference to the accompanying drawings are exemplary and are intended to explain the present invention, and should not be construed as limiting the present invention.

[0040] The following disclosure provides numerous different embodiments or examples for implementing various structures of the present invention. To simplify the disclosure, specific examples of components and arrangements are described below. These are merely examples and are not intended to limit the scope of the invention. Furthermore, reference numerals and / or letters may be repeated in different examples. Such repetition is for simplification and clarity and does not in itself indicate a relationship between the various embodiments and / or arrangements discussed. In addition, examples of various specific processes and materials are provided in this invention; however, those skilled in the art will recognize the applicability of other processes and / or the use of other materials.

[0041] The air conditioner 100 according to an embodiment of the present invention is described below with reference to the accompanying drawings.

[0042] like Figures 1 to 4As shown, the air conditioner 100 according to an embodiment of the present invention includes: a housing 1, a fan assembly 2, and a heat exchanger 3. The housing 1 has an air inlet 11 and an air outlet 12. The fan assembly 2 is disposed inside the housing 1 and includes a volute 21 and a fan wheel 22. An air supply duct 211 is formed inside the volute 21. The air supply duct 211 has an air inlet 212 and an air outlet 213. The fan wheel 22 is rotatably disposed on the volute 21. The heat exchanger 3 is located between the air inlet 11 and the fan assembly 2. The heat exchanger 3 has an extension 31 formed at least one end of the fan wheel 22 in the circumferential direction. In the thickness direction of the heat exchanger 3, the extension 31 is opposite to and spaced apart from the outer wall surface of the volute 21. The extension 31 and the outer wall surface of the volute 21 together define an air duct 4. The air duct 4 extends to the air inlet 212 and communicates with the air supply duct 211 through the air inlet 212.

[0043] In other words, the air inlet 11 is connected to the air outlet 12 through the air supply duct 211. By rotating the impeller 22, external airflow can be driven to enter the casing 1 through the air inlet 11. After exchanging heat with the heat exchanger 3, the airflow passes through the air supply duct 211 and is finally discharged through the air outlet 12, thereby achieving forced air circulation to cool or heat the indoor space. Specifically, driven by the impeller 22, after the external air enters the casing 1 through the air inlet 11, part of it can directly pass through the part of the heat exchanger 3 except for the extension 31 and enter the air supply duct 211 through the air inlet 212. Part of it can pass through the extension 31 of the heat exchanger 3 and enter the induced draft duct 4, and then enter the air supply duct 211 through the air inlet 212. The airflow entering the air supply duct 211 flows to the air outlet 12 through the air outlet 213 and is finally discharged into the indoor space through the air outlet 12.

[0044] Therefore, by providing an extension 31 on the heat exchanger 3, the circumferential dimension of the heat exchanger 3 in the impeller 22 can be increased, thereby increasing the heat exchange area of ​​the heat exchanger 3. By providing an air duct 4 located between the extension 31 and the volute 21, the airflow passing through the extension 31 can smoothly enter the air supply duct 211 and be discharged through the air outlet 12. That is, it is ensured that the airflow after heat exchange through the extension 31 can participate in the temperature regulation of indoor air by the air conditioner 100, thereby improving the cooling or cooling efficiency of the air conditioner 100.

[0045] According to the embodiment of the present utility model, the air conditioner 100 can increase the circumferential dimension of the heat exchanger 3 in the impeller 22 by providing an extension 31 on the heat exchanger 3, thereby increasing the heat exchange area of ​​the heat exchanger 3. By providing an air duct 4 located between the extension 31 and the volute 21, the airflow passing through the extension 31 can smoothly enter the air supply duct 211 and be discharged through the air outlet 12. That is, it is ensured that the airflow after heat exchange through the extension 31 can participate in the temperature regulation of indoor air by the air conditioner 100, thereby improving the cooling or cooling efficiency of the air conditioner 100.

[0046] In a specific example, the heat exchanger 3 is U-shaped, opening towards the impeller 22. Air inlets 11 are formed on the rear, left, and right side walls of the casing 1, which effectively increases the air intake position and heat exchange effect of the air conditioner 100, thereby improving the heating or cooling efficiency of the air conditioner 100. Furthermore, the air outlet 12 is equipped with a door 5 for opening or closing the air outlet 12.

[0047] According to some embodiments of this utility model, the dimension of the induced draft duct 4 in the thickness direction of the heat exchanger 3 is increased in the direction toward the airflow inlet 212. That is, in the direction toward the airflow inlet 212, the distance between the extension 31 and the outer wall surface of the volute 21 in the thickness direction of the extension 31 is increased. It can be understood that as the width of the induced draft duct 4 increases, the flow area of ​​the induced draft duct 4 increases, the resistance to airflow decreases, and the gas velocity can be reduced. Therefore, the resistance of the airflow entering the induced draft duct 4 through the extension 31 and flowing toward the airflow inlet 212 can be reduced, thereby reducing airflow loss. At the same time, the velocity of the airflow flowing from the induced draft duct 4 to the airflow inlet 212 can be reduced, thereby mitigating the impact between the airflow entering the airflow inlet 212 and the rotating airflow of the impeller 22, i.e., the airflow that directly passes through the part other than the extension 31 at the heat exchanger 3 and flows toward the airflow inlet 212, thus avoiding cavity noise caused by airflow impact.

[0048] According to some embodiments of this utility model, the dimension of the end of the exhaust duct 4 away from the airflow inlet 212 in the thickness direction of the heat exchanger 3 (e.g.) Figure 3The range of L3 shown is 3mm-15mm. That is, the distance between the end of the extension 31, i.e. the end of the extension 31 away from the airflow inlet 212, and the outer wall surface of the volute 21 in the thickness direction of the heat exchanger 3 is controlled within the range of 3mm to 15mm. It can be understood that the greater the distance between the end of the extension 31 and the outer wall of the volute 21, the larger the space occupied by the extension 31 and the volute 21 in the thickness direction of the heat exchanger 3. However, the larger the anti-interference space that can be reserved for production tolerances between the extension 31 and the heat exchanger 3, the larger the size of the induced draft duct 4 in the thickness direction of the heat exchanger 3, and the smaller the resistance to airflow along the induced draft duct 4. Conversely, the closer the distance between the end of the extension 31 and the outer wall of the volute 21, the smaller the space occupied by the extension 31 and the volute 21 in the thickness direction of the heat exchanger 3. However, the smaller the anti-interference space that can be reserved for production tolerances between the extension 31 and the heat exchanger 3, and the smaller the size of the induced draft duct 4 in the thickness direction of the heat exchanger 3, the greater the resistance to airflow along the induced draft duct 4.

[0049] Therefore, by controlling the distance between the end of the extension 31 and the outer wall of the volute 21 in the thickness direction of the heat exchanger 3 within the range of 3mm to 15mm, it is possible to avoid increasing the size of the air conditioner 100 due to an excessively large distance, while avoiding increasing the airflow resistance along the air duct 4 and the risk of interference between the extension 31 and the volute 21 during installation due to an excessively small distance. The distance between the end of the extension 31 and the outer wall of the volute 21 in the thickness direction of the heat exchanger 3 can be 3mm, 4mm, 5mm, 7mm, 9mm, 11mm, 13mm, 15mm, etc., and no specific limitation is made here.

[0050] According to some embodiments of this utility model, the dimension of one end of the induced draft duct 4 adjacent to the airflow inlet 212 in the thickness direction of the heat exchanger 3 (e.g.) Figure 4 The range of L1 shown is 10mm-30mm. That is, the distance between the fixed end of the extension 31 (the end of the extension 31 near the airflow inlet 212) and the outer wall of the volute 21 in the thickness direction of the heat exchanger 3 is controlled within the range of 10mm to 30mm. It can be understood that the greater the distance between the fixed end of the extension 31 and the outer wall of the volute 21, the larger the space occupied by the extension 31 and the volute 21 in the thickness direction of the heat exchanger 3, the larger the size of the end of the induced draft duct 4 near the airflow inlet 212 in the thickness direction of the heat exchanger 3, and the smaller the resistance to airflow along the induced draft duct 4; conversely, the closer the distance between the fixed end of the extension 31 and the outer wall of the volute 21, the smaller the space occupied by the extension 31 and the volute 21 in the thickness direction of the heat exchanger 3, the smaller the size of the end of the induced draft duct 4 near the airflow inlet 212 in the thickness direction of the heat exchanger 3, and the greater the resistance to airflow along the induced draft duct 4.

[0051] Therefore, by controlling the distance between the fixed end of the extension 31 and the outer wall of the volute 21 in the thickness direction of the heat exchanger 3 within the range of 10mm to 30mm, it is possible to avoid increasing the size of the air conditioner 100 due to an excessively large distance, while avoiding increasing the resistance to airflow along the duct 4 due to an excessively small distance. The distance between the fixed end of the extension 31 and the outer wall of the volute 21 in the thickness direction of the heat exchanger 3 can be 10mm, 13mm, 15mm, 18mm, 21mm, 25mm, 28mm, 30mm, etc., and no specific limitation is made here.

[0052] According to some embodiments of this utility model, in the circumferential direction of the impeller 22, the length of the air duct 4 (e.g.) Figure 3 The length of L4 shown is not less than 30mm. It can be understood that the circumferential length of the extension 31's impeller 22 is not less than the circumferential length of the induced draft duct 4 of the impeller 22. The longer the circumferential length of the induced draft duct 4 of the impeller 22, the longer the circumferential length of the extension 31 of the impeller 22, and the more airflow passes through the extension 31 for heat exchange and enters the supply air duct 211 through the induced draft duct 4. Therefore, by controlling the length of the induced draft duct 4 to be not less than 30mm, the extension length of the extension 31 of the impeller 22 in the circumferential direction can be guaranteed, thereby increasing the heat exchange area of ​​the heat exchanger 3. The circumferential length of the induced draft duct 4 of the impeller 22 can be 30mm, 32mm, 34mm, 35mm, 37mm, 39mm, 43mm, 46mm, 50mm, etc., without specific limitations.

[0053] According to some embodiments of this utility model, the volute 21 includes a rear volute tongue 214, and an extension 31 is formed at one end of the heat exchanger 3 near the rear volute tongue 214. The extension 31 is located on the outer side of the rear volute tongue 214 and together with the outer wall surface of the rear volute tongue 214 defines a portion of the air intake duct 4. That is, the airflow entering the air intake duct 4 will flow along the outer wall surface of the rear volute tongue 214 toward the airflow inlet 212, and will be deflected at the position of the rear volute tongue 214 before entering the airflow inlet 212. The outer side of the rear volute tongue 214 can provide more space for arrangement, thereby reducing the difficulty of arranging the extension 31. At the same time, it can reduce the deflection angle of the airflow in the air intake duct 4 during the process of entering the airflow inlet 212, thereby reducing the impact of the airflow in the air intake duct 4 on the rotating airflow of the impeller 22 when entering the airflow inlet 212, and avoiding cavity noise caused by airflow impact.

[0054] According to some embodiments of this utility model, such as Figure 5 and Figure 6As shown, a diffuser structure 23 is formed on the outer wall of the rear volute tongue 214. The diffuser structure 23 is located inside the air intake duct 4 and forms multiple diffuser channels 231 arranged along the axial direction of the impeller 22. Therefore, when the airflow entering the air intake duct 4 flows towards the airflow inlet 212 and passes through the diffuser structure 23, the multiple diffuser channels 231 can disperse the airflow into multiple small airflows, thereby better dispersing the airflow distribution entering the airflow inlet 212. This reduces the impact between the airflow in the air intake duct 4 and the rotating airflow of the impeller 22 when the airflow enters the airflow inlet 212, and avoids cavity noise caused by airflow impact.

[0055] According to some embodiments of this utility model, the air diffuser structure 23 is located at the end of the rear volute tongue 214 near the airflow inlet 212. Therefore, the distance between the air diffuser structure 23 and the airflow inlet 212 can be shortened, thereby shortening the distance the airflow dispersed by the air diffuser structure 23 travels to the airflow inlet 212. This prevents the airflow in the air duct 4 from being dispersed by the air diffuser structure 23 and not flowing to the airflow inlet 212 before converging again. In other words, it allows the airflow dispersed by the air diffuser structure 23 to enter the airflow inlet 212 as quickly as possible, thus ensuring the dispersing effect of the air diffuser structure 23 on the airflow entering the airflow inlet 212.

[0056] According to some embodiments of this utility model, the distance between the air diffuser structure 23 and the airflow inlet 212 (e.g.) Figure 4 The distance L5 shown is no greater than 10mm. That is, the distance between the air diffuser structure 23 and the airflow inlet 212 in the circumferential direction of the impeller 22 is controlled within 10mm or less. It can be understood that the greater the distance between the air diffuser structure 23 and the airflow inlet 212, the higher the probability that the multiple small airflows dispersed by the air diffuser structure 23 will reconverge. Therefore, by controlling the distance between the air diffuser structure 23 and the airflow inlet 212 to no greater than 10mm, the dispersing effect of the air diffuser structure 23 on the airflow entering the airflow inlet 212 can be improved, thereby reducing the impact of the airflow in the duct 4 on the rotating airflow of the impeller 22 when it enters the airflow inlet 212. The distance between the air diffuser structure 23 and the airflow inlet 212 can be 10mm, 9.5mm, 9mm, 8.5mm, 8mm, 7.5mm, 7mm, 6.5mm, 6mm, etc., without specific limitations. It should be noted that the distance between the air diffuser structure 23 and the airflow inlet 212 is the distance between the position of the air diffuser structure 23 closest to the airflow inlet 212 and the airflow inlet 212. For example, if the air diffuser structure 23 includes multiple arc-shaped ribs 232, and the ribs 232 are bent towards the direction close to the airflow inlet 212, then the distance between the air diffuser structure 23 and the airflow inlet 212 is the distance between the apex of the arc of the rib 232 and the airflow inlet 212.

[0057] According to some embodiments of this utility model, the air diffuser structure 23 and the heat exchanger 3 are spaced apart. That is, the air diffuser structure 23 and the heat exchanger 3 are arranged at intervals along the thickness direction of the heat exchanger 3. Therefore, the air diffuser structure 23 can avoid interfering with the installation of the heat exchanger 3, thereby providing a certain margin for the installation of the heat exchanger 3. Furthermore, the air diffuser structure 23 can avoid generating excessive airflow resistance to the flowing air, so as to ensure the air volume entering the air supply duct 211 from the exhaust duct 4.

[0058] According to some embodiments of the present invention, the air dissipation structure 23 includes multiple ribs 232 extending along the axial direction of the impeller 22. Each rib 232 has multiple air dissipation grooves 233 arranged along the axial direction of the impeller 22 on its side facing the heat exchanger 3. The multiple air dissipation grooves 233 together constitute the air dissipation channel 231.

[0059] In some embodiments, such as Figure 7 and Figure 8 As shown, the raised ribs 232 are parallel to the axial direction of the wind turbine 22, and multiple raised ribs 232 are connected end to end and arranged in a straight line along the axial direction of the wind turbine 22; in some embodiments, such as Figure 9 and Figure 10 As shown, the rib 232 has an included angle with the axial direction of the impeller 22; in some embodiments, such as Figure 11 and Figure 12 As shown, multiple ribs 232 are connected end to end and arranged in a serrated pattern along the axial direction of the impeller 22; in some embodiments, such as Figure 13 and Figure 14 As shown, the rib 232 is an arc-shaped protrusion that bends toward the airflow inlet 212. It should be noted that this is only an example of the shape of some of the ribs 232, and is not a limitation on the shape of the ribs 232. Any shape of the ribs 232 that meets the requirement of dispersing the airflow is within the scope of protection of this application.

[0060] According to some embodiments of this utility model, the width of one end of the air duct 4 adjacent to the airflow inlet 212 in the thickness direction of the heat exchanger 3 is L1, and the height of the outer wall of the volute tongue 214 protruding from the air diffuser structure 23 is L2. L1 and L2 satisfy: 1 / 3*L1≤L2≤2 / 3*L1. That is, the height of the air diffuser structure 23 is controlled within the range of 1 / 3 to 2 / 3 of the width of one end of the air duct 4 adjacent to the airflow inlet 212. It can be understood that, with the relative position between the extension 31 and the volute 21 remaining fixed, the higher the height of the air diffuser structure 23, the larger the contact area between the air diffuser structure 23 and the airflow in the air intake duct 4, resulting in a better dispersion effect on the airflow in the air intake duct 4. However, it also obstructs the airflow in the air intake duct 4 more, leading to a greater airflow loss. Conversely, the lower the height of the air diffuser structure 23, the less obstruction it causes to the airflow in the air intake duct 4, resulting in a smaller airflow loss. However, the smaller the contact area between the air diffuser structure 23 and the airflow in the air intake duct 4, resulting in a worse dispersion effect on the airflow in the air intake duct 4.

[0061] Therefore, by controlling the height of the air diffuser structure 23 within the range of 1 / 3 to 2 / 3 of the width of the end of the air intake duct 4 adjacent to the airflow inlet 212, excessive airflow loss due to an excessively high height of the air diffuser structure 23 can be avoided. Simultaneously, an excessively low height of the air diffuser structure 23 can be avoided to prevent weakening the dispersing effect on the flowing air. This ensures both the airflow delivered from the air intake duct 4 to the supply air duct 211 and the effective dispersing of the airflow. The ratio of L2 to L1 can be 1 / 3, 9 / 24, 5 / 12, 11 / 24, 1 / 2, 13 / 24, 7 / 12, 15 / 24, 2, etc., without specific limitations.

[0062] According to some embodiments of the present invention, the air distribution structure 23 includes multiple ribs 232 extending axially along the impeller 22. The air distribution channel 231 passes through the ribs 232 along the extending direction of the air intake duct 4. The two opposite sides of the ribs 232 in the extending direction of the air intake duct 4 are respectively the first side and the second side. The included angle between the first side and the second side and the outer wall surface of the rear volute tongue 214 (e.g., Figure 6In the diagram, α (where the three angle markings refer to optional angles of α) ranges from 45° to 135°. The angle between the first and second sides and the outer wall of the rear volute 214 represents the angle between the rib 232 and the outer wall of the rear volute 214 in the direction extending away from the outer wall of the rear volute 214. It can be understood that if the angle between the rib 232 and the outer wall of the rear volute 214 is too large or too small, and the angle between the rib 232 and the direction of airflow towards the air inlet 212 within the air duct 4 is smaller, the contact area between the rib 232 and the airflow within the air duct 4 will be too small, affecting the air dispersion effect. Therefore, by controlling the angles between the first and second sides and the outer wall of the rear volute 214 within the range of 45° to 135°, the dispersion effect of the air dispersion structure 23 on the airflow within the air duct 4 can be better guaranteed. The angle between the first and second sides and the outer wall of the rear volute tongue 214 can be 45°, 55°, 65°, 75°, 85°, 90°, 105°, 115°, 125°, 135°, etc., without specific limitations. Specifically, the first and second sides are parallel.

[0063] According to some embodiments of this utility model, the air diffuser structure 23 and the volute 21 are integrally formed. This integrally formed structure not only ensures the structural and performance stability of the air diffuser structure 23 and the volute 21, but also facilitates molding and simplifies manufacturing. Furthermore, it eliminates the need for fittings and connection processes used to connect the air diffuser structure 23 and the volute 21, resulting in lower production costs and significantly improved assembly efficiency. This ensures reliable connection between the air diffuser structure 23 and the volute 21. Moreover, the integrally formed structure exhibits higher overall strength and stability, and a longer service life.

[0064] In this utility model, unless otherwise explicitly specified and limited, the terms "installation," "connection," "joining," and "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components. For those skilled in the art, the specific meaning of the above terms in this utility model can be understood according to the specific circumstances.

[0065] In the description of this specification, the description with reference to the terms "one embodiment", "some embodiments", "example", "specific example", or "some examples" means that the specific features, structures, materials or characteristics described in conjunction with the embodiment or example are included in at least one embodiment or example of the present invention. In this specification, the schematic representations of the above terms do not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials or characteristics described can be combined in any one or more embodiments or examples in a suitable manner. In addition, those skilled in the art can combine and combine different embodiments or examples described in this specification and features of different embodiments or examples without contradiction.

[0066] Although embodiments of the present invention have been shown and described, those skilled in the art will understand that various changes, modifications, substitutions and alterations can be made to these embodiments without departing from the principles and spirit of the present invention, the scope of which is defined by the claims and their equivalents.

Claims

1. An air conditioner, characterized in that, include: The casing has an air inlet and an air outlet. A fan assembly is disposed within the housing and includes a volute and a fan wheel. An air supply duct is formed within the volute, and the air supply duct has an air inlet and an air outlet. The fan wheel is rotatably disposed within the volute. A heat exchanger is located between the air inlet and the fan assembly. The heat exchanger has an extension at at least one end of the impeller in the circumferential direction. In the thickness direction of the heat exchanger, the extension is opposite to and spaced apart from the outer wall of the volute. The extension and the outer wall of the volute together define an air duct. The air duct extends to the air inlet and communicates with the air supply duct through the air inlet.

2. The air conditioner according to claim 1, characterized in that, The dimension of the induced draft duct in the thickness direction of the heat exchanger increases in the direction of approaching the airflow inlet.

3. The air conditioner according to claim 1, characterized in that, The dimension of the end of the exhaust duct away from the airflow inlet in the thickness direction of the heat exchanger ranges from 3mm to 15mm; and / or, the dimension of the end of the exhaust duct adjacent to the airflow inlet in the thickness direction of the heat exchanger ranges from 10mm to 30mm.

4. The air conditioner according to claim 1, characterized in that, In the circumferential direction of the wind turbine, the length of the air duct is not less than 30 mm.

5. The air conditioner according to claim 1, characterized in that, The volute includes a rear volute tongue, and the extension is formed at one end of the heat exchanger near the rear volute tongue. The extension is located outside the rear volute tongue and together with the outer wall surface of the rear volute tongue defines a portion of the air intake duct.

6. The air conditioner according to claim 5, characterized in that, An air-dispersing structure is formed on the outer wall surface of the rear volute tongue. The air-dispersing structure is located in the air-inducing duct and forms multiple air-dispersing channels arranged along the axial direction of the impeller.

7. The air conditioner according to claim 6, characterized in that, The air diffuser structure is located at the end of the rear volute tongue near the airflow inlet.

8. The air conditioner according to claim 7, characterized in that, The distance between the air diffuser structure and the airflow inlet is no more than 10 mm.

9. The air conditioner according to claim 6, characterized in that, The air distribution structure is spaced apart from the heat exchanger.

10. The air conditioner according to claim 9, characterized in that, The air dissipation structure includes multiple ribs extending along the axial direction of the impeller. Each rib has multiple air dissipation grooves arranged along the axial direction of the impeller on its side facing the heat exchanger. The multiple air dissipation grooves together constitute the air dissipation channel.

11. The air conditioner according to claim 6, characterized in that, The width of the end of the air duct adjacent to the airflow inlet in the thickness direction of the heat exchanger is L1, and the height of the air dispersing structure protruding from the outer wall of the rear volute tongue is L2. L1 and L2 satisfy: 1 / 3*L1≤L2≤2 / 3*L1.

12. The air conditioner according to claim 6, characterized in that, The air dispersing structure includes multiple ribs extending along the axial direction of the impeller. The air dispersing channel passes through the ribs along the extension direction of the air duct. The two sides of the ribs in the extension direction of the air duct are respectively the first side and the second side. The angle between the first side and the second side and the outer wall of the rear volute tongue is in the range of 45°-135°.

13. The air conditioner according to claim 6, characterized in that, The air distribution structure is integrally formed with the volute.

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